EP3334995B1 - Wärmetauscher - Google Patents

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Publication number
EP3334995B1
EP3334995B1 EP16747730.6A EP16747730A EP3334995B1 EP 3334995 B1 EP3334995 B1 EP 3334995B1 EP 16747730 A EP16747730 A EP 16747730A EP 3334995 B1 EP3334995 B1 EP 3334995B1
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EP
European Patent Office
Prior art keywords
heat exchanger
threaded spindle
cleaning element
cylinder tube
exchanger according
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.)
Active
Application number
EP16747730.6A
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German (de)
English (en)
French (fr)
Other versions
EP3334995A1 (de
Inventor
Robert Adler
Ekkehardt Klein
Christoph Nagl
Andreas POLLAK
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.)
Linde GmbH
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Linde GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Priority to PL16747730T priority Critical patent/PL3334995T3/pl
Publication of EP3334995A1 publication Critical patent/EP3334995A1/de
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Publication of EP3334995B1 publication Critical patent/EP3334995B1/de
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Classifications

    • 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
    • F28G3/00—Rotary appliances
    • F28G3/08—Rotary appliances having coiled wire tools, i.e. basket type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B1/00—Cleaning by methods involving the use of tools
    • B08B1/30—Cleaning by methods involving the use of tools by movement of cleaning members over a surface
    • 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
    • F28G1/00—Non-rotary, e.g. reciprocated, appliances
    • F28G1/08—Non-rotary, e.g. reciprocated, appliances having scrapers, hammers, or cutters, e.g. rigidly mounted
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B9/00—Cleaning hollow articles by methods or apparatus specially adapted thereto 
    • B08B9/02—Cleaning pipes or tubes or systems of pipes or tubes
    • B08B9/027—Cleaning the internal surfaces; Removal of blockages
    • B08B9/04—Cleaning the internal surfaces; Removal of blockages using cleaning devices introduced into and moved along the pipes
    • B08B9/043—Cleaning the internal surfaces; Removal of blockages using cleaning devices introduced into and moved along the pipes moved by externally powered mechanical linkage, e.g. pushed or drawn through the pipes
    • B08B9/0436—Cleaning the internal surfaces; Removal of blockages using cleaning devices introduced into and moved along the pipes moved by externally powered mechanical linkage, e.g. pushed or drawn through the pipes provided with mechanical cleaning tools, e.g. scrapers, with or without additional fluid jets
    • 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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • F28D7/106—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 arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28G1/00—Non-rotary, e.g. reciprocated, appliances
    • F28G1/14—Pull-through rods
    • 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
    • F28G15/08—Locating position of cleaning appliances within conduits
    • 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
    • F28G3/00—Rotary appliances
    • F28G3/10—Rotary appliances having scrapers, hammers, or cutters, e.g. rigidly mounted

Definitions

  • the present invention relates to a heat exchanger, in particular for natural gas as the working medium for the purpose of drying and cleaning the natural gas.
  • Natural gas from storage facilities often has a particularly high percentage of undesirable accompanying substances and particularly high proportions of water. It is desirable to remove the accompanying substances and the water content from the natural gas before it is used for other purposes.
  • One possibility for this is to cool the natural gas in one or more steps to suitable low temperatures. In particular, liquefaction of the natural gas can be expedient here.
  • Heat exchangers with cleaning devices are for example in the GB375132 or the DE29724316U described. For the reasons mentioned, however, it is difficult to specify generally valid cleaning intervals for the heat exchangers in question.
  • Known gas dryer systems work, for example, with beds made of porous materials such as silica gel.
  • Another method uses triethylene glycol to dehumidify the working gas, whereby the process usually has to be carried out in several stages in order to be able to achieve the desired purity.
  • Moist working gases are the cause of hydrate formation and corrosion.
  • limit values apply to the water content.
  • Compressor stations and downstream Compressor stations and downstream elements such as pipelines, valves, etc., are basically designed for operation with dry working gas, which is why water should be removed from the working medium in addition to accompanying substances.
  • the gas drying process can include, for example, mechanical steps (mechanical separation of free water) and thermodynamic steps (separation by pressure reduction) and finally the step of absorption, for example by highly hygroscopic substances such as the triethylene glycol mentioned.
  • the triethylene glycol can be sprayed into the gas stream and absorbs the remaining water.
  • Condensing and freezing accompanying substances such as water, CO2 and hydrocarbon compounds are deposited on the heat transfer surfaces and thus reduce the heat transfer. Even at operating temperatures above the freezing point of water, methane hydrate is formed on the heat transfer surfaces.
  • the porous beds in dryer systems according to the prior art require a very large volume due to their principle. Furthermore, the beds only absorb the liquid portion, primarily the water portion, from the working gas. During regeneration of the bed, which takes place, for example, by flowing through it with a dry, unsaturated inert gas and / or heating and / or settling of the bed, a large proportion of working gas is discharged unused. When replacing the bed, it is necessary in known dryers according to the prior art to open the container in order to be able to completely replace the bed. This is costly and labor intensive and leads to an interruption in the production cycle.
  • the invention proposes a heat exchanger with the features of claim 1.
  • This cleaning element is used to clean deposits on the heat transfer surfaces between the inner surface of the first cylinder tube and the threaded spindle.
  • This cleaning element is either attached directly to the threaded spindle in the form of a driver or attached to such a driver, which in turn is attached directly to the threaded spindle.
  • a working medium that flows for heat exchange in an intermediate space between the first cylinder tube and the threaded spindle will - as explained at the beginning - leave deposits on the heat transfer surfaces, especially when it cools down. With natural gas as the working medium, these deposits consist in particular of accompanying substances and water. The mentioned deposits can be picked up and / or transported away or taken along by the cleaning element.
  • the threaded spindle is actuated, whereby the cleaning element is displaced in the axial direction within the first cylinder tube, whereby it can remove deposits from the heat-transferring surfaces.
  • deposits arise in particular on the threaded spindle and on the axially extending guide grooves of the heat exchanger.
  • the cleaning element cleans these surfaces.
  • steels in particular heat-treatable steels and alloys made from non-ferrous metals, and also nickel alloys (such as Inconel) and cast materials, can be used.
  • the cleaning element During normal operation of the heat exchanger, the cleaning element is in a rest position in which it influences the heat exchange between the working medium and the coolant as little as possible or not at all.
  • a coolant it is of course also possible to use a heating medium if the working medium is to be heated.
  • the cleaning takes place, for example, according to empirically determined period durations or when an externally measured maximum permissible differential pressure is reached, which indicates a reduction in the free flow cross section for the working medium due to deposits.
  • the heat exchanger according to the invention with a cleaning element allows the heat transfer surfaces to be cleaned effectively without having to be opened manually.
  • the cleaning process described is easy to carry out. For this only the Threaded spindle are rotated to move the cleaning element in the axial direction. Further process steps are not required. It is particularly advantageous if the cleaning element takes with it or transports away deposits. In this way a change and thus wear and tear or aging of the cleaning element can be prevented.
  • the heat exchanger has a second cylinder tube which is arranged coaxially to the first cylinder tube.
  • the coolant in order to let coolant in and out of an intermediate space between the second and first cylinder tube.
  • it is useful if there is an inlet and an outlet opening for a working medium in order to let the working medium in or out of an intermediate space between the first cylinder tube and the threaded spindle.
  • the cleaning element is designed as an essentially hollow-cylindrical cleaning element, the inner surface of the cleaning element having an internal thread corresponding to the thread of the threaded spindle and the outer surface of the cleaning element having external grooves corresponding to the guide grooves of the internal surface of the first cylinder tube.
  • the cleaning element can be attached to the threaded spindle in a simple manner (without a separate driver) and remove as thoroughly existing deposits as possible on heat-transferring inner surfaces in the space between the inner surface of the first cylinder tube and threaded spindle.
  • the cleaning element has recesses in the otherwise essentially cylindrically shaped circumference of the cleaning element, these recesses extending parallel to the axial direction. These recesses are in particular in the cleaning element in the circumferential direction arranged equidistantly.
  • the recesses or millings produce “teeth” or “claws” in the cleaning element, which in particular help to avoid seizing or blocking of the cleaning element during cleaning.
  • Deposits loosened from the threaded spindle can get into the recesses or millings mentioned and from there fall downwards (in the direction of movement of the cleaning element) when the heat exchanger is operated vertically, at least during the cleaning phase. In this way, a blockage of the cleaning element due to accumulating deposits can be effectively avoided.
  • the internal thread of the cleaning element has a diameter that increases in the axial direction. This configuration ensures that the thread grooves are not cleaned as abruptly as, for example, in the case of a cleaning element which is seated on the thread grooves in the axial direction over its entire extent. This avoids any possible jamming of the cleaning element.
  • the individual "claws" or “teeth” produced thereby become more elastic and press better against the outer wall or the thread grooves.
  • Another advantage is the free space that this creates, comparable to a chip channel in a machining process.
  • the outer surface of the first cylinder tube has a helix running helically in the axial direction.
  • This helix is part of the outer surface of the first cylinder tube and is applied to this outer surface or is produced by milling.
  • the coolant can then flow helically in the axial direction in the spaces between this coil.
  • This first cylinder tube with this helix can therefore also be referred to as a cooling helix.
  • a deposit storage device for deposits / contaminants cleared out by means of the cleaning element is connected, in particular thermally decoupled, to the space between the threaded spindle and the inner surface of the first cylinder tube / cooling coil.
  • the cleaning element transports contaminants into the deposit reservoir, which is in particular from the heat-transferring surfaces mentioned, i.e. the space between the threaded spindle and the inner surface of the first cylinder tube, is thermally decoupled. This thermal decoupling allows thermal treatment of the accompanying substances or other deposits collected in the deposit reservoir without affecting the further operation of the heat exchanger.
  • a heating element is advantageously present in or on the heat exchanger and is arranged in such a way that accompanying substances / impurities present in the deposit reservoir can be heated.
  • the cleaning element can transport the condensed impurities into the deposit reservoir, which can then also be referred to, for example, as a condensate reservoir.
  • the collected condensate can then be heated by means of the heating element mentioned.
  • the heated condensate, which has been melted, can be drained through a condensate drain by opening a downstream valve. In this way, the deposit storage can be freed from existing impurities at given times.
  • a position measuring means is advantageously provided and arranged such that the position of the cleaning element can be measured in the axial direction.
  • Such a position measurement enables or simplifies the reversal of the direction of rotation of the threaded spindle at a certain predetermined position so that the cleaning element moves back in the opposite direction. Reaching a predetermined rest position can also be detected in a simple manner by means of the position meter.
  • a drive motor To drive the threaded spindle, it is advantageous to use a drive motor, a particle barrier being present between the drive motor and the space between the threaded spindle and the inner surface of the first cylinder tube, i.e. between the drive motor and the heat-conducting surfaces of the heat exchanger.
  • a particle barrier prevents foreign matter from entering the space in which the working medium flows to the heat exchanger and, conversely, serves to protect the drive motor or its bearings from particles.
  • the internal threaded spindle is surrounded by a first cylinder tube or the cooling coil.
  • the latter is in turn surrounded by a second cylinder tube or an outer cylinder tube.
  • the space between the threaded spindle and the cooling coil forms the working space for the working medium, which is supplied to this space via an inlet opening and removed from this space via an outlet opening after heat exchange.
  • the named inlet opening is used as the outlet opening and the named outlet opening is used as the inlet opening.
  • the threaded spindle On one side of the heat exchanger there is a drive motor that sets the threaded spindle in rotation.
  • the threaded spindle is mounted in a bearing.
  • a position measuring means which, based on the number of revolutions of the drive motor with a known pitch of the thread of the threaded spindle, can provide information on the position of the cleaning element moved by the threaded spindle.
  • the cleaning element which can also be referred to as a scraper, is preferably located in its rest position on the same side as the drive motor and is from this through a particle barrier Cut.
  • a particle barrier can be made of PTFE, for example, and is then so soft, even at low temperatures, that particles can accumulate in it.
  • the radial distance from the shaft is as small as possible, ideally a few tenths of a mm, preferably less than 0.4 mm, more preferably less than 0.3 mm, more preferably approximately equal to 0.2 mm.
  • a deposit storage or a condensate reservoir which in particular is thermally decoupled from this working space.
  • a heating element that is thermally coupled to the condensate reservoir in order to heat it.
  • the condensate reservoir is connected to the surroundings of the heat exchanger via a condensate drain in order to be able to empty the contents of the condensate reservoir.
  • a plain bearing bush for the threaded spindle at this end of the heat exchanger.
  • the threaded spindle is set in rotation by the drive motor.
  • the housing of the drive motor is preferably connected to the space through which the working medium flows and is thus loaded with the operating pressure.
  • the thread of the threaded spindle is preferably designed as a right-hand thread with a trapezoidal profile, left-handed threads and other flank shapes can in principle also be conceivable and advantageous. In this regard, reference is also made to what is below.
  • the cleaning element or the scraper engages on the one hand in the thread of the threaded spindle and on the other hand in the guide or profile grooves of the cooling coil, whereby the cleaning element is set in a translational movement.
  • the position of the cleaning element can be detected with the aid of the number of revolutions of the drive motor measured by the position means.
  • the cleaning element slides up to the thermally decoupled condensate reservoir or deposit store at the end of the working space.
  • the cleaning element pushes the existing sediments carried along into the condensate reservoir.
  • the direction of rotation of the drive motor is reversed and the cleaning element moves back to its rest position next to the particle barrier.
  • the collected condensate can be heated by the heating element and, depending on the state of aggregation, made to melt or evaporate and then drained through the condensate drain, preferably on both sides, by opening a downstream valve.
  • a threaded spindle with a cross thread can be used with advantage.
  • Such threaded spindles are known per se and are referred to as cross-threaded spindles.
  • Threaded spindles with trapezoidal profiles can only map one assigned direction of movement according to their direction of rotation, which as a result is also reversed when the direction of rotation is reversed.
  • the reversal of the direction of rotation requires a switching element in the electrical supply of the drive motor or a change gear.
  • sliding elements, such as the cleaning element these are common equipped with a position stop.
  • the position of the sliding element is detected with a position detection means.
  • a cross thread is constructed in such a way that both a left-hand and a right-hand thread turn, preferably with the same pitch, is mapped on a spindle, which has a reversal point in its respective end positions, in which at least one sliding block sliding in the thread groove from a first direction of movement to a second Direction of movement is transferred.
  • the direction of rotation of the shaft of the threaded spindle thus always remains the same.
  • the determination of the rest position of the cleaning element must be carried out using an alternative method.
  • a torque measurement is possible, for example, which registers significant changes in the torque in the two end positions of the cleaning element.
  • the end positions or at least the upper end position of the rest position can be determined by means of initiators, that is to say limit switches.
  • the heat exchanger according to the invention consequently has a cross-threaded spindle with at least one sliding block that slides in the threads and a scraper or cleaning element connected to the sliding block, for example via a bolt.
  • the advantages of using the cross-thread spindle are an automatic reversal of the direction of movement without changing the direction of rotation of the shaft, so that braking and restarting the electric motor becomes obsolete, which in turn results in a more energy-efficient process. Furthermore, as already stated, no electrical device for reversing the direction of rotation has to be provided or a corresponding program part in the control is omitted. Overall, the cleaning process of the heat exchanger is shortened by the omitted direction reversal. The end positions of the cleaning element are automatically defined by the reverse grinding of the cross thread and can therefore not be exceeded. Finally, the position measuring means described above can be omitted.
  • the invention also relates to a use of the heat exchanger according to the invention for liquefying a gas.
  • a second cylinder tube is arranged coaxially to the first cylinder tube of the heat exchanger, with a coolant flowing between the first and second cylinder tubes.
  • a working medium containing the gas to be liquefied flows between the first cylinder tube and the threaded spindle.
  • the gas to be liquefied can be nitrogen, for example.
  • the cooling medium flows at a lower temperature than the working medium, the pressure and the temperature of the cooling medium and the pressure of the working medium being set such that the gas to be liquefied in the working medium is liquefied through the heat exchange with the cooling medium.
  • natural gas for example, liquefied nitrogen at a pressure of 1 bar and a temperature of -196 ° C can be used as the cooling medium.
  • the working medium naturally gas
  • the working medium is introduced through an upstream heat exchanger at a pressure of, for example, 10 bar, in particular after appropriate pre-cooling.
  • the nitrogen contained in natural gas can cool down to a temperature of - 170 ° C and below, so that it liquefies at a pressure of 10 bar.
  • the process mentioned can be used analogously to the liquefaction of helium, oxygen and / or hydrogen as one or more components in a working medium.
  • Specific examples for the liquefaction of helium, hydrogen and oxygen are given below: Liquefaction of various gases, for example for the purpose of separating them from gas mixtures
  • the pressure of the cooling medium is chosen so that the temperature of the cooling medium is always lower than that of the working medium.
  • the pressure of the cooling medium is chosen so that the temperature of the cooling medium is always lower than that of the working medium.
  • FIG 1 shows schematically a longitudinal section through an embodiment of a heat exchanger 13, as it can be used in particular for cooling natural gas.
  • the heat exchanger 13 has an outer cylinder tube 1 which surrounds a cooling coil 2.
  • This cooling coil 2 is in turn designed as a cylinder tube and has at least one, preferably spiral-shaped channel 23 on its outer surface, which is used to guide a coolant.
  • this channel 23 is generated by a corresponding coil 21 on the outer surface of the cooling coil 2.
  • the inner surface of the hollow-cylindrical cooling coil has guide or profile grooves 22. This at least one guide groove 22 serves to guide a cleaning element or scraper 12.
  • a threaded spindle 3 is located in the interior of the cooling coil 2 coaxially with it.
  • the threaded spindle 3 is driven by a drive motor 4 and is mounted in a bearing, which is preferably designed as an axial / radial mixed bearing 5.
  • a bearing which is preferably designed as an axial / radial mixed bearing 5.
  • this is in a radial bearing that is preferably designed as a plain bearing bush 8, stored.
  • At this end of the heat exchanger 13 there is also a thermally decoupled condensate reservoir 7 and a heating element 9 for heating condensate in the condensate reservoir 7.
  • a particle barrier 11 separates the drive motor 4 from the working space for the working medium.
  • the particle barrier 11 also serves to protect the drive motor 4 and the bearing 5 from coarse particles, but does not act as a gas seal.
  • a plurality of outer cylinder tubes 1 are connected by a clamping device 10.
  • the clamping device 10 is constructed in such a way that two union rings with an internal thread are screwed onto the external cylinder tube 1, which in turn is provided with an external thread.
  • the union rings are pulled together by means of screws and the individual segments are pressed together and sealed with a seal.
  • a plurality of such outer cylinder tubes can also be understood and referred to as one “outer cylinder tube”.
  • a cleaning element or scraper 12 is arranged next to the particle barrier 11 in its rest position.
  • the threaded spindle 3 is set in rotation, so that the reamer 12 is displaced on the threaded spindle along the guide or profile grooves 22 of the cooling coil 2 in the axial direction.
  • a threaded spindle 3 is used, for example with a trapezoidal profile.
  • a reversal of the direction of movement of the reamer 12 requires a reversal of the direction of rotation of the threaded spindle 3.
  • Another embodiment of the threaded spindle 3 is further below in connection with Figure 4 explained.
  • moist, contaminated working medium is passed through a working medium inlet opening 14 into the space between the threaded spindle 3 and between the cooling coil 2 and flows in the axial direction to the working medium outlet opening 15 at the other end of the heat exchanger 13.
  • the working medium flows in the process in the profile grooves 22 on the inner surface of the hollow cylindrical cooling coil 2 (cf. Figure 2 ) along the axis of rotation of the Threaded spindle 3.
  • Coolant is supplied to the space between cooling coil 2 and outer cylinder tube 1 via a coolant inlet opening 16, which coolant flows to the other end of heat exchanger 13 and leaves it through coolant outlet opening 17.
  • the coolant flows in a spiral in the axial direction in the channel 23 formed between the outer cylinder tube 1 and the cooling coil 2.
  • the coolant removes heat from the cooling coil 2, so that heat is in turn removed from the working medium.
  • natural gas is heated to a temperature of approx. 20 ° C from an underground cavern at a pressure of 4 to a maximum of 220 bar.
  • the working medium is preferably cooled to 1 ° C. in a first heat exchanger.
  • the working medium is preferably cooled to -40 ° C to -60 ° C.
  • the working medium is cooled to preferably -80 ° C. to -150 ° C. and in a last stage the working medium is liquefied via a heat exchanger again connected in series.
  • the temperature of the natural gas is reduced to as low as -196 ° C, causing the natural gas to undercool.
  • the first stage falls out of a large part of the water, the next stages mainly the higher hydrocarbons, CO 2 and other accompanying substances.
  • the scrapers 12 present in the respective stages of the heat exchangers 13 condensed components can be cleaned from the heat-transferring surfaces.
  • the first two heat exchanger stages are cooled by refrigeration machines, the other two by liquid nitrogen, cryogenic liquid CNG or cryogenic gaseous nitrogen.
  • the maximum operating pressure of the heat exchanger is 300 bar, the permissible operating temperatures are 100 ° C to -200 ° C.
  • nitrogen can be used as an accompanying substance at high pressure (e.g. at 10 bar) through liquid nitrogen low pressure (e.g. at 1 bar), due to the different pressure-dependent phase transitions, liquefied and separated.
  • the proposed heat exchanger 13 can thus also be used to liquefy nitrogen.
  • the threaded spindle 3 of one stage is set in rotation by the drive motor 4.
  • the reamer 12 which engages on the one hand in the thread of the threaded spindle 3 and on the other hand in the profile grooves 22 of the cooling coil 2, is thereby set in a translational movement.
  • the scraper 12 takes the abovementioned condensed accompanying substances with it. When they reach the condensate reservoir 7, these are pushed into the same.
  • the position measuring means 6 can determine the position of the reamer 12 based on the defined thread pitch of the threaded spindle 3 from the number of measured revolutions of the drive motor 4. As soon as the position of the condensate reservoir 7 is reached, the direction of rotation of the drive motor 4 is reversed, so that the scraper 12 moves back to its rest position. It is useful if the rest position represents the upper end position and the position of the condensate reservoir 7 represents the lower end position of the scraper 12 when the heat exchanger is in a vertical position.
  • the collected condensate is heated by the heating element 9 and thus melted.
  • the accompanying substances can be drained off through a condensate drain 18.
  • the cleaning of the heat-exchanging surfaces of the heat exchanger 13 takes place, for example, after empirically determined period durations or when an externally measured maximum permissible differential pressure is reached, which suggests a reduction in the free flow cross-section in the work space due to deposited accompanying substances. As a result of the cleaning, the highest possible and constant heat transfer value is achieved. In comparison to the systems according to the prior art, the heat exchanger 13 takes up a smaller structural volume due to the effectively used heat transfer surfaces.
  • the segmental structure of the heat exchanger 13 enables a modular structure.
  • the heat transfer capacity is thus determined by the enlargement or Reduction of the heat transfer surfaces variable.
  • the actual position of the scraper 12 is always monitored. Any seizure can be detected at an early stage by measuring the slip.
  • the heat exchanger 13 explained here can be adapted and used not only for liquefying natural gas, but also for a large number of industrial applications with corresponding working media.
  • the scraper 12 can be adapted to the needs of the respective areas of use and quickly replaced in the event of damage.
  • Figure 3 shows a scraper 12 or a cleaning element 12, as it can be used in the heat exchanger 13.
  • the internal thread 121 of the reamer 12 corresponds to the thread of the threaded spindle 3.
  • the reamer 12 has recesses or millings 123.
  • the reamer 12 contains “teeth” or “claws” that prevent deposits from collecting in the thread and blocking the reamer 12.
  • the deposits can namely enter the space through the recesses or millings 123 and, when the heat exchanger is in a vertical position, fall downward in the direction of the condensate reservoir 7.
  • the inside diameter of the reamer 12, which increases in the direction of movement of the cleaning serves for easier introduction into the contaminated threaded spindle at the beginning of the cleaning process.
  • Figure 4 finally shows an alternative embodiment of a threaded spindle 3 ', which is a cross-threaded spindle 3'.
  • the cross-threaded shaft is designated 31.
  • the reamer 12 is connected to the sliding block 32 and moves in the axial direction when the threaded spindle 3 'rotates.
  • the threaded spindle 3 ' enables a more energy-efficient process, since the electric motor does not have to be braked and restarted.
  • a position measurement of the reamer 12 and thus the in Figure 1 position measuring means 6 shown are omitted.
  • the cleaning process of the heat exchanger 13 is further shortened by the omission of the direction reversal.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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EP16747730.6A 2015-08-11 2016-08-02 Wärmetauscher Active EP3334995B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16747730T PL3334995T3 (pl) 2015-08-11 2016-08-02 Wymiennik ciepła

Applications Claiming Priority (2)

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DE102015010455.1A DE102015010455A1 (de) 2015-08-11 2015-08-11 Wärmetauscher
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SA518390886B1 (ar) 2021-09-08
JP6890579B2 (ja) 2021-06-18
RU2018102560A (ru) 2019-09-12
KR20180038537A (ko) 2018-04-16
RU2715128C2 (ru) 2020-02-25
PL3334995T3 (pl) 2021-04-19
DK3334995T3 (da) 2021-01-18
WO2017025173A1 (de) 2017-02-16
EP3334995A1 (de) 2018-06-20
US10780460B2 (en) 2020-09-22
ES2843527T3 (es) 2021-07-19
PT3334995T (pt) 2021-01-22
CA2992959A1 (en) 2017-02-16
US20190009306A1 (en) 2019-01-10
CN107923721B (zh) 2020-05-22
CA2992959C (en) 2023-10-17
KR102601037B1 (ko) 2023-11-09
CN107923721A (zh) 2018-04-17
RU2018102560A3 (ru) 2020-01-17
JP2018525600A (ja) 2018-09-06
HUE053288T2 (hu) 2021-06-28
DE102015010455A1 (de) 2017-02-16

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