WO2011003444A1 - Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur - Google Patents

Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur Download PDF

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Publication number
WO2011003444A1
WO2011003444A1 PCT/EP2009/058632 EP2009058632W WO2011003444A1 WO 2011003444 A1 WO2011003444 A1 WO 2011003444A1 EP 2009058632 W EP2009058632 W EP 2009058632W WO 2011003444 A1 WO2011003444 A1 WO 2011003444A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat
heat exchange
transport
exchange system
Prior art date
Application number
PCT/EP2009/058632
Other languages
German (de)
English (en)
Inventor
Holger König
Franz Summerer.
Original Assignee
A-Heat Allied Heat Exchange Technology 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 A-Heat Allied Heat Exchange Technology Ag filed Critical A-Heat Allied Heat Exchange Technology Ag
Priority to CN2009801603516A priority Critical patent/CN102472602A/zh
Priority to PCT/EP2009/058632 priority patent/WO2011003444A1/fr
Priority to EP09780284A priority patent/EP2452148A1/fr
Priority to JP2012518760A priority patent/JP2012532306A/ja
Priority to RU2012104027/06A priority patent/RU2012104027A/ru
Priority to AU2009349362A priority patent/AU2009349362A1/en
Priority to US13/382,635 priority patent/US20120199310A1/en
Priority to MX2012000210A priority patent/MX2012000210A/es
Priority to CA2767378A priority patent/CA2767378A1/fr
Publication of WO2011003444A1 publication Critical patent/WO2011003444A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G15/00—Details
    • F28G15/003—Control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • 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
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B11/00—Controlling arrangements with features specially adapted for condensers
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2200/00—Prediction; Simulation; Testing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • Heat exchange system and a method for operating a
  • the invention relates to a heat exchange system and a method for operating and determining a degree of soiling of a
  • Heat exchangers are used in refrigerators, e.g. in ordinary
  • Heat exchangers " which may also be referred to as” tube heat exchangers ", and on the other hand to” Minnichannel ",
  • the laminated tube heat exchangers serve, like all types of heat exchangers, to transfer heat between two media, eg, but not only, to transfer from a cooling medium to air or vice versa, as is known, for example, from a classic household refrigerator in which over the
  • Refrigerator is given off heat to the ambient air.
  • the ambient medium outside of the heat exchanger eg water, oil or often simply the ambient air, for example, absorbs the heat or is transferred from the heat to the heat exchanger is either cooled or heated accordingly.
  • the second medium may be, for example, a liquid refrigerant or heat transfer medium or an evaporating or condensing heat medium.
  • heat means is to be understood as meaning any fluid which can be advantageously used in a heat exchanger.
  • heating means thus encompasses both the conventional refrigerants known in the art and any other suitable heating means or refrigerants .
  • the heat exchanger is a simple radiator, for example a radiator in an internal combustion engine, then the heating means may be in the Special, of course, simply be water or oil, which circulates as a coolant through the heat exchanger.
  • the surrounding medium e.g. the air
  • the second medium e.g. the coolant that circulates in the heat exchanger system. This is due to very different heat transfer surfaces for the two media
  • FIG. 2 shows a heat exchange system according to the invention with a laminated tubular heat exchanger known per se.
  • the hillsau seh system is formed by a variety of such elements.
  • the slat distance is for
  • thermodynamically it should be as small as possible, but not so small that the air-side pressure drop is too large.
  • An economic optimum is about 2 mm, which is a typical value for condenser and recooler.
  • the efficiency is essentially determined by the fact that the heat that is transferred between the fin surface and the air, must be transmitted through heat conduction through the fins to the pipe. This heat transfer is all the more effective, the higher the conductivity or the thickness of the lamella, but also the smaller the distance between the tubes. This is called the lamella efficiency.
  • a lamellar material is therefore nowadays predominantly aluminum used, which has a high thermal conductivity (about 220 W / mK) to economic conditions.
  • the pipe pitch should be as small as possible, but this leads to the problem that you need many pipes.
  • Many pipes mean high costs because the pipes (usually made of copper) are considerably more expensive than the thin aluminum fins. This material could be reduced by reducing the tube diameter and wall thickness, i.
  • Microchannel heat exchangers have been developed that are manufactured using a completely different process, almost laminating the ideal image
  • Tubular heat exchanger correspond: many small tubes with small distances.
  • FIG. 1 Embodiment of FIG. 1 used and shown schematically.
  • a heat exchanger depending on the required heat output, already with a single extruded profile as the central
  • Such profiles can e.g. be made easily and in a variety of forms from a variety of materials in suitable extrusion. But also other manufacturing processes for the production of
  • Mini-channel heat exchangers are known, such as e.g. the assembly of suitably shaped profile sheets or other suitable methods.
  • Minnichannel heat exchanger flows, and the air, for example, heat should be issued, similar to the laminated tubular heat exchange also often used fins.
  • louvers are usually roof-shaped
  • Heat exchange can be further increased.
  • This measure has long been known, the specific geometric design of the Louver depending on the application can be very different. In the simplest case, a Louver simply a slot, so an elongated narrow recess or opening in the lamella.
  • Microchannel heat exchangers create a heat exchanger with a very high fin efficiency and a very small filling volume
  • Minichannel heat exchangers were previously limited in size to be eligible. Many small modules would have to be connected consuming.
  • the use of aluminum in the extruded profiles is relatively high, so that hardly a cost advantage was expected from the use of materials.
  • a problem with all previously known heat exchange systems is the pollution of the system components of the system tau seh, in particular the heat exchanger itself, that is, especially the fins of the heat exchanger, which in principle not in the operating condition
  • Air-applied heat exchangers such as e.g. Condensers or recoolers often work in contaminated environments. Contamination of the air may be natural (pollen, insects, dust, leaves, etc.) or industrial (grinding dust, tire wear, flour dust, cardboard dust, etc.). Many impurities remain on the airborne
  • Heat exchangers hang and add to it over time.
  • the heat exchangers where, for example, the cooling air is guided past with the aid of appropriate fan can be polluted by such and other contaminants of all kinds that are contained in the cooling air with time more and more, which may for example lead to the heat transfer coefficient of the surface of the heat exchanger is lowered, so that the heat transfer performance is significantly reduced. This can lead to increased operating costs or in extreme cases, the heat exchange system can no longer provide the required heat exchange performance, which can lead to serious damage in the worst case.
  • Louvers particularly susceptible to contamination are the above-mentioned Louvers. Especially these provide a good grip for all types of contamination.
  • the dirt accumulates on the edges of the Louvers in the slats and thus lead to a deterioration of the heat transfer of the lamella and thus to loss of performance of the heat exchanger, resulting in an increase in consumption of Energy, right down to one
  • the heat exchanger To counteract contamination, the heat exchanger must be either regularly cleaned consuming or provided with an appropriate filter. However, the filters must be cleaned regularly. It is in the known systems, the cleaning of the heat exchanger alone for design reasons, for example because of
  • Heat exchanger in the installed state is not readily accessible directly, cumbersome so consuming and expensive.
  • heat exchange systems require opening a housing, e.g. the heat exchanger itself or other essential
  • Pollution of the heat exchange system must be known, and although preferably not only qualitatively but also quantitatively must be known and especially the change in pollution as a function of time must be detectable.
  • the object of the invention is therefore to provide an improved
  • a heat exchange system which overcomes the problems known from the prior art and in particular allows to continuously monitor the degree of contamination of the heat exchange system, in particular the fins of the heat exchanger.
  • a heat exchange system is proposed in which certain relevant Bethebsgrössen can be adapted to the changing pollution of the heat exchange system, so that a heat transfer performance of the heat exchanger or the entire heat exchange system can be optimized over a longer period of operation, and also over long periods of operation a predefinable
  • Heat transfer performance is guaranteed even with increasing pollution.
  • a predeterminable degree of contamination is detected automatically, so that the optimal time for necessary cleaning work is automatically recognizable without much effort.
  • the invention thus relates to a heat exchange system comprising a
  • Transport fluid and a flowing through the flow channel in the operating state heating means is the Transportfluidum on a
  • Inlet surface can be brought into flowing contact with the heat exchanger, and via an outflow from the heat exchanger again wegwoodbar.
  • a pollution sensor in the form of a pressure sensor and / or a speed sensor, with which a
  • Transport characteristic which is characteristic of the flow of the transport fluid from the inflow over the outflow surface determinable.
  • Pollution sensor is already detected before the pressure drop across the heat exchanger increases significantly. It is in fact an essential realization of the invention that the power take-off of the heat exchanger is already used massively even at a degree of contamination in which the increasing contamination of the heat exchanger does not lead to an increase in the pressure loss across the heat exchanger. But in the
  • the present invention it is possible for the first time, from the characteristic transport characteristic of the heat exchanger, for example, from the pressure drop across the heat exchanger or from a
  • Flow rate of the transport fluid e.g. the one by the
  • Contamination of réelletau seh system are compensated, for example, by a performance of a fan, which conveys the air for heat exchange through the heat exchanger, in its performance as a function of Pollution degree is adjusted. Or by a flow or an operating pressure of a heating medium is suitably readjusted by the heat exchanger or another operating variable is adjusted accordingly. It is possible in a particularly important for practice embodiment of the present invention, to determine the degree of contamination of the heat exchange system continuously, if necessary not only qualitatively, but also quantitatively, in particular, the
  • Heat exchange system to be monitored continuously.
  • Heat transfer performance of the heat exchanger or the entire heat exchange system even over a longer period of operation, even with increasing pollution is constantly optimized, which also over long periods of operation regardless of the pollution of the
  • Heat exchanger ensures a predetermined heat transfer performance.
  • a predefinable degree of contamination can be automatically detected by the invention, so that the optimum time for necessary cleaning and maintenance is automatically recognizable without much effort.
  • the invention is based on the knowledge that a
  • the transport parameter can, for example, a
  • the transport characteristic may also be a pressure of the transport fluid, for example a pressure of the air before it enters the heat exchanger via the inflow surface, or a pressure during or after the outflow over the outflow surface of the heat exchanger.
  • the transport parameter is a pressure difference or a pressure drop across the heat exchanger.
  • a look-up table or a mathematical function can be generated, which reflects the degree of soiling of the heat exchange system depending on the pressure loss and / or an absolute pressure value and / or a characteristic flow velocity of the transport fluid, possibly further parameters such For example, the speed of a fan, a temperature or other parameters or operating and
  • the invention can be used in heat exchangers that a blade to increase the effective
  • Heat transfer surface wherein the blade is preferably equipped with the initially provided Louvern.
  • the contamination of the Louvers initially leads to a reduced pressure loss, as will be explained later with reference to FIG. 5.
  • the pressure loss as a function of the amount of pollution initially falls to a minimum, and then increase again as pollution progresses. That means, the
  • Pressure loss across the heat exchanger initially decreases with increasing pollution, completely different than expected.
  • Embodiment a very simple contamination sensor for measuring the pressure loss installed on a novel heat exchange system that detects a drop in pressure loss across the heat exchanger and thus can measure the degree of pollution, preferably time-dependent.
  • Variable speed fans according to EC technology can, among other things, also use the current consumption of the motor as a signal.
  • a lamella can be provided in a particularly important embodiment for increasing the rate of heat exchange on a flow segment, wherein a flow-through opening, in particular in the form of a Louver, is preferably provided on the lamella.
  • Heat exchange system a microchannel heat exchanger and / or at least one heat exchanger is a tubular heat exchanger.
  • a transport device is known per se in a manner known per se.
  • a fan may be provided for transporting the transport fluid from the inflow surface to the outflow surface, wherein in practice the transport fluid is very often the ambient air.
  • the transport characteristic variable can be a pressure of the transport fluid, in particular a pressure loss between the transport fluid
  • Be inflow and the outflow of the heat exchanger, and / or the transport characteristic may have a flow velocity of the
  • a drive unit for controlling and / or regulating and / or for the purpose of data acquisition of an operating or state parameter of the heat exchange system, is particularly advantageous
  • the inventive heat exchange system may be a radiator, in particular a radiator for a vehicle, in particular for a land vehicle, for an aircraft or for a watercraft, or a radiator, a condenser or an evaporator for a mobile or stationary heating system, cooling system or air conditioning, especially one
  • Cooler device for a machine, a data processing system or for a building.
  • the invention further relates to a method for operating a described heat exchange system according to the present invention, wherein a transport characteristic variable is measured, and from the transport characteristic a degree of contamination of the heat exchanger is determined.
  • a pressure drop across the heat exchanger is ascertained from the transport characteristic variable, with it being possible in particular to determine a decrease in heat transfer performance of the heat exchanger from the pressure loss.
  • a power of the transport device in particular a rotational speed of the fan depending on the degree of contamination of the
  • Time for a maintenance routine can be determined automatically, for example, depending on the degree of contamination.
  • operating and / or status data are monitored by a control center and / or the heat exchange system is controlled and / or regulated in this manner.
  • Fig. 1 shows a first embodiment of an inventive
  • Fig. 2 shows a second embodiment according to FIG. 1 with laminated
  • Fig. 3 shows an embodiment with differential pressure measurement for
  • FIG. 1 is a schematic representation of a first embodiment of an inventive heat exchange system with a Microchannel heat exchanger shown, which is provided throughout the following by the reference numeral 1.
  • the heat exchange system 1 according to the invention of FIG. 1 comprises a heat exchanger 2, which in the present example is a known per se
  • Microchannel heat exchanger 2 with a flow channel 210 arranged in a flow segment 21.
  • a transport fluid 3 which in the present case is the ambient air
  • a heat medium 4 flowing through the flow channel 210 in the operating state which is, for example, a refrigerant 4, such as CO 2
  • the Transportfluidum 3 via an inflow surface 201 with the heat exchanger 2 in flowable contact and via an outflow surface 202 of
  • a contamination sensor 5 is provided for determining a contamination of the heat exchanger 2, which is arranged in the flow direction of the air 3 in front of the disk set of lamellae 6 in the present example.
  • the contamination sensor 6 is either a pressure sensor 6 or a speed sensor 6 or another suitable pollution sensor 6, with which a transport characteristic TK, which is characteristic of the flow of the transport fluid 3 from the inflow surface 201 via the outflow surface 202, can be determined.
  • the plate pack with the plurality of fins 6 with fin surface 62 serves to increase a heat exchange rate between the
  • any existing louvers are not explicitly shown. It can thus with a special Embodiment according to FIG. 1 Louver be provided on the blade 6 and not in another embodiment, because no Louver needed for a corresponding other application.
  • a fan 7 (not shown in FIG. 1 for reasons of clarity) for transporting the air 3 through the pack of lamellae 6 is provided so that, for example, a flow rate LG according to FIG. 4 can be set, for example as a function of a thickness the pollution of the heat exchanger 2, with the help of
  • FIG. 1 which relates to an inventive
  • Embodiment with a micro-channel heat exchanger 2 the plurality of flow channels 210, which are here micro-channels 210.
  • Fig. 2 differs from the embodiment of Fig. 1 essentially only in that instead of a micro-channel heat exchanger 2, a classic laminated tube heat exchanger 2 is used, wherein clearly the Louver 61 can be seen in the slats 6, in the example of Fig. 2 yet are not polluted.
  • Another difference to the example of Fig. 1 is that the pollution sensor 5 is housed within the disk set of lamellae 6.
  • Embodiment also other pollution sensors 5 alternatively arranged at suitable locations or in addition several
  • Pollution sensors 5 may be provided simultaneously.
  • Fig. 3 is another, very significant in practice embodiment with differential pressure measurement for determining a pressure drop .DELTA.P across the heat exchanger 2 is shown schematically.
  • the fan 7 conveys in a conventional manner ambient air 3 with the characteristic
  • Heat exchanger 2 and leads the air 3 via the discharge surface 202 by a cover A from the heat exchange system 1 back to the environment.
  • To determine the pressure loss .DELTA.P in the passage of the air 3 through the heat exchanger 2 are respectively in accordance with the left before
  • measured pressure difference of the pressure loss .DELTA.P via the heat exchanger 2 can be determined.
  • characteristic transport characteristic TK for a heat exchange system 1 with a microchannel heat exchanger 2 with lamellae 6 and Louvern 61
  • the curve V 0 belongs to a heat exchange system 1, which has been freshly cleaned, that is not dirty yet. After a certain period of operation was in the same heat exchanger system 1, the curve Vi of
  • FIG. 5 shows a schematic diagram of a characteristic diagram which explains the relationship between the degree of contamination V and the resulting change in the pressure loss ⁇ P and the associated decrease in the heat transfer capacity PW of the heat exchanger 2.
  • Heat exchanger 2 shown, which increases according to the illustration from left to right, wherein on the left axis of ordinate .DELTA.P the pressure loss .DELTA.P is plotted on the heat exchanger 2, while on the right
  • Heat transfer power PW is read.
  • the solid line ⁇ P corresponds to the curve of the pressure loss .DELTA.P as a function of the degree of contamination V, while the dotted line the drop in the heat transfer power PW as a function of
  • Heat transfer power PW are at a pollution level V identical zero, that is normalized for the non-polluted heat exchanger 2 each to 100%.
  • Transport fluid 3 e.g. the more the Louvers 61 are clogged with dirt, the more the air 3 flowing through the heat exchanger 2 is reduced.
  • the air 3 can thereby pass through the heat exchanger 2 easier and / or faster.
  • this results in a reduction of the pressure loss ⁇ P and, on the other hand, reduces the effective contact time or the effective contact area between transport medium 3 and heat exchanger 2, which results in the observed massive reduction of the heat transfer power PW.
  • the maintenance of cleaning intervals can be optimally ensured, and on the other hand, an optimally designed operation of the inventive heat exchanger system can be guaranteed.
  • the quasi-automatically incurred electronic signals are also available for other purposes and can for example also be used advantageously for various service purposes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)

Abstract

L'invention concerne un système (1) d'échange de chaleur qui comprend un échangeur de chaleur (2) qui présente un canal d'écoulement (210) disposé dans un segment d'écoulement (21). Pour échanger de la chaleur entre un fluide de transport (3) et un agent calorifique (4) qui traverse, en fonctionnement, le canal d'écoulement (210), le fluide de transport (3) peut être mis en contact d'écoulement avec l'échangeur de chaleur (2) par une surface d'entrée d'écoulement (201) et peut de nouveau être retiré de l'échangeur de chaleur (2) par une surface de sortie d'écoulement (202). Selon l'invention, un détecteur d'encrassement (5) qui présente la forme d'un détecteur de pression (5) et/ou d'un détecteur de vitesse (5) est prévu pour déterminer un degré d'encrassement (V) de l'échangeur de chaleur (2) et permet de déterminer une grandeur caractéristique de transport (TK) qui est caractéristique de l'écoulement du fluide de transport (3) entre la surface d'entrée d'écoulement (201) et la surface de sortie d'écoulement (202). L'invention concerne en outre un procédé d'utilisation d'un système (1) d'échange de chaleur.
PCT/EP2009/058632 2009-07-07 2009-07-07 Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur WO2011003444A1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
CN2009801603516A CN102472602A (zh) 2009-07-07 2009-07-07 热交换系统、以及用于操作热交换系统的方法
PCT/EP2009/058632 WO2011003444A1 (fr) 2009-07-07 2009-07-07 Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur
EP09780284A EP2452148A1 (fr) 2009-07-07 2009-07-07 Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur
JP2012518760A JP2012532306A (ja) 2009-07-07 2009-07-07 熱交換システム及び熱交換システムを動作させる方法
RU2012104027/06A RU2012104027A (ru) 2009-07-07 2009-07-07 Теплообменная система, а также способ эксплуатации теплообменной системы
AU2009349362A AU2009349362A1 (en) 2009-07-07 2009-07-07 Heat exchange system and method for operating a heat exchange system
US13/382,635 US20120199310A1 (en) 2009-07-07 2009-07-07 Heat exchange system, as well as a method for the operation of a heat exchange system
MX2012000210A MX2012000210A (es) 2009-07-07 2009-07-07 Sistema de intercambio de calor y metodo de operacion para sistema de intercambio de calor.
CA2767378A CA2767378A1 (fr) 2009-07-07 2009-07-07 Systeme d'echange de chaleur et procede d'utilisation d'un systeme d'echange de chaleur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2009/058632 WO2011003444A1 (fr) 2009-07-07 2009-07-07 Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur

Publications (1)

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WO2011003444A1 true WO2011003444A1 (fr) 2011-01-13

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PCT/EP2009/058632 WO2011003444A1 (fr) 2009-07-07 2009-07-07 Système d'échange de chaleur et procédé d'utilisation d'un système d'échange de chaleur

Country Status (9)

Country Link
US (1) US20120199310A1 (fr)
EP (1) EP2452148A1 (fr)
JP (1) JP2012532306A (fr)
CN (1) CN102472602A (fr)
AU (1) AU2009349362A1 (fr)
CA (1) CA2767378A1 (fr)
MX (1) MX2012000210A (fr)
RU (1) RU2012104027A (fr)
WO (1) WO2011003444A1 (fr)

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WO2013071967A1 (fr) * 2011-11-16 2013-05-23 A-Heat Allied Heat Exchange Technology Ag Procédé de minimisation de la consommation d'énergie d'une machine à recirculation de chaleur et machine à recirculation de chaleur
EP2696159A1 (fr) 2012-08-09 2014-02-12 A-heat Allied Heat Exchange Technology Ag Échangeur thermique et procédé de mise en réseau d'échangeurs thermiques
EP3441694A1 (fr) * 2017-08-11 2019-02-13 Robert Bosch GmbH Procédé de fonctionnement d'une installation thermique
US11584219B2 (en) 2020-09-25 2023-02-21 Brose Fahrzeugteile Se & Co. Kommanditgesellschaft Radiator assembly for vehicle

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US10054473B2 (en) 2015-12-03 2018-08-21 International Business Machines Corporation Airflow sensor for a heat sink
US9874415B2 (en) 2016-02-15 2018-01-23 International Business Machines Corporation Airflow sensor for a heat sink
DE102017210554B4 (de) * 2017-06-22 2020-06-04 Lufthansa Technik Aktiengesellschaft Reinigungsverfahren für Oberflächen im Innenvolumen von durchströmten Flugzeugkomponenten
US20190162455A1 (en) * 2017-11-29 2019-05-30 Lennox Industries, Inc. Microchannel heat exchanger
CN111026192B (zh) * 2019-12-23 2021-11-23 金马工业集团股份有限公司 一种对热挤压件控温冷却系统
WO2021245792A1 (fr) * 2020-06-02 2021-12-09 三菱電機株式会社 Dispositif de refroidissement
GB202008533D0 (en) * 2020-06-05 2020-07-22 Empig As Method, system and apparatus for hydrocarbon flow system fluid cooling
CN117234166B (zh) * 2023-11-10 2024-03-08 无锡市前卫化工装备有限公司 一种设备的故障感知运维方法及系统

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Publication number Priority date Publication date Assignee Title
WO2013071967A1 (fr) * 2011-11-16 2013-05-23 A-Heat Allied Heat Exchange Technology Ag Procédé de minimisation de la consommation d'énergie d'une machine à recirculation de chaleur et machine à recirculation de chaleur
EP2696159A1 (fr) 2012-08-09 2014-02-12 A-heat Allied Heat Exchange Technology Ag Échangeur thermique et procédé de mise en réseau d'échangeurs thermiques
EP3249341A1 (fr) 2012-08-09 2017-11-29 A-Heat Allied Heat Exchange Technology AG Échangeur thermique et procédé de mise en réseau d'échangeurs thermiques
EP3249341B1 (fr) 2012-08-09 2020-09-02 A-Heat Allied Heat Exchange Technology AG Échangeur thermique et procédé de mise en réseau d'échangeurs thermiques
EP3441694A1 (fr) * 2017-08-11 2019-02-13 Robert Bosch GmbH Procédé de fonctionnement d'une installation thermique
US11584219B2 (en) 2020-09-25 2023-02-21 Brose Fahrzeugteile Se & Co. Kommanditgesellschaft Radiator assembly for vehicle

Also Published As

Publication number Publication date
CN102472602A (zh) 2012-05-23
AU2009349362A1 (en) 2011-12-22
EP2452148A1 (fr) 2012-05-16
CA2767378A1 (fr) 2011-01-13
RU2012104027A (ru) 2013-08-20
US20120199310A1 (en) 2012-08-09
JP2012532306A (ja) 2012-12-13
MX2012000210A (es) 2012-02-28

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