EP3334995B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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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
Authority
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
Other languages
German (de)
French (fr)
Other versions
EP3334995A1 (en
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
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Filing date
Publication date
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Priority to PL16747730T priority Critical patent/PL3334995T3/en
Publication of EP3334995A1 publication Critical patent/EP3334995A1/en
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Publication of EP3334995B1 publication Critical patent/EP3334995B1/en
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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)
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Description

Die vorliegende Erfindung betrifft einen Wärmetauscher, insbesondere für Erdgas als Arbeitsmedium zum Zwecke der Trocknung und Reinigung des Erdgases.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.

Stand der TechnikState of the art

Wärmetauscher zum Wärmen oder zum Abkühlen eines Arbeitsmediums sind aus dem Stand der Technik vielfältig bekannt. Ohne Beschränkung der Allgemeinheit soll im Folgenden das Arbeitsmedium Erdgas näher betrachtet werden. Erdgas aus Bodenspeichern weist häufig einen besonders hohen Prozentsatz an unerwünschten Begleitstoffen und besonders hohe Wasseranteile auf. Es ist wünschenswert, die Begleitstoffe sowie den Wasseranteil aus dem Erdgas zu entfernen, bevor es für weitere Zwecke eingesetzt wird. Eine Möglichkeit hierzu stellt die Kühlung des Erdgases in einem oder mehreren Schritten auf geeignete tiefe Temperaturen dar. Insbesondere kann hierbei eine Verflüssigung des Erdgases zweckmäßig sein.A wide variety of heat exchangers for heating or cooling a working medium are known from the prior art. Without limiting the generality, the working medium natural gas will be considered in more detail below. 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.

Bei der Abkühlung von Erdgas kommt es durch die genannten Begleitstoffe im Wärmetauscher zumeist zu Ablagerungen auf den Wärmeübertragungsflächen, wobei der zeitliche Verlauf solcher Ablagerungen von den Betriebsbedingungen und der jeweiligen Erdgaszusammensetzung abhängt. Die Wärmeübertragungsflächen müssen daher in bestimmten Intervallen gereinigt werden. Wärmetauscher mit Reinigungsvorrichtungen sind beispielsweise in der GB375132 oder der DE29724316U beschrieben. Aus den genannten Gründen ist es allerdings schwierig, allgemein gültige Reinigungsintervalle für die betreffenden Wärmetauscher anzugeben. Bekannte Gas-Trocknersysteme arbeiten beispielsweise mit Schüttungen aus porösen Materialien wie beispielsweise Kieselgel. Ein anderes Verfahren verwendet zur Entfeuchtung des Arbeitsgases Triethylenglykol, wobei der Prozess meist mehrstufig gehalten werden muss, um die gewünschte Reinheit erreichen zu können. Feuchte Arbeitsgase sind die Ursache für Hydratbildung und Korrosion. In den Gastransportnetzen gelten daher Grenzwerte bezüglich des Wassergehalts. Verdichterstationen und nachgeschaltete Verdichterstationen und nachgeschaltete Elemente, wie Rohrleitungen, Ventile etc., sind grundsätzlich für einen Betrieb mit trockenem Arbeitsgas ausgelegt, weshalb neben Begleitstoffen auch Wasser aus dem Arbeitsmedium entfernt werden sollte. Der Prozess der Gastrocknung kann beispielsweise mechanische Schritte (mechanisches Abscheiden von freiem Wasser) und thermodynamische Schritte (Abscheiden durch Druckreduktion) und schließlich den Schritt der Absorption, beispielsweise durch stark hygroskopische Substanzen wie das genannte Triethylenglykol umfassen. Das Triethylenglykol, kann in den Gasstrom eingesprüht werden und absorbiert das verbliebene Wasser.When natural gas is cooled, the above-mentioned accompanying substances in the heat exchanger usually lead to deposits on the heat transfer surfaces, the time course of such deposits depending on the operating conditions and the respective natural gas composition. The heat transfer surfaces must therefore be cleaned at certain intervals. 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. In the gas transport networks, 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.

Kondensierende und gefrierende Begleitstoffe wie Wasser, CO2 sowie Kohlenwasserstoffverbindungen scheiden sich an den Wärmeübertragungsflächen ab und reduzieren somit den Wärmeübergang. Auch bei Betriebstemperaturen über dem Gefrierpunkt von Wasser kommt es an den Wärmeübertragungsflächen zu Bildung von Methanhydrat.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.

Die porösen Schüttungen in Trockneranlagen nach dem Stand der Technik benötigen prinzipbedingt ein sehr großes Volumen. Weiters absorbieren die Schüttungen lediglich den Flüssigkeitsanteil, vornehmlich den Wasseranteil, aus dem Arbeitsgas. Bei Regeneration der Schüttung, die beispielsweise mittels Durchströmen mit einem trockenen ungesättigten Inertgas und/oder Ausheizen und/oder Setzen der Schüttung erfolgt, wird ein großer Anteil an Arbeitsgas ungenutzt abgelassen. Beim Ersetzen der Schüttung ist bei bekannten Trocknern gemäß Stand der Technik ein Öffnen des Behälters notwendig, um die Schüttung restlos ersetzen zu können. Dies ist kosten- und arbeitsintensiv und führt zu einer Unterbrechung des Produktionszyklus.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.

Die genannten Prozesse zur Trocknung und Reinigung von Gasen als Arbeitsmedium erweisen sich als aufwändig. Es ist wünschenswert, die Anzahl der Prozessschritte zu verringern, ohne dabei die oben genannten Nachteile in Kauf nehmen zu müssen.The processes mentioned for drying and cleaning gases as a working medium prove to be complex. It is desirable to reduce the number of process steps without having to accept the disadvantages mentioned above.

Kurzfassung der ErfindungSummary of the invention

Die Erfindung schlägt einen Wärmetauscher mit den Merkmalen des Anspruchs 1. Dieses Reinigungselement dient zur Reinigung von Ablagerungen auf den Wärmeübertragungsflächen zwischen der Innenfläche des ersten Zylinderrohrs und der Gewindespindel. Dieses Reinigungselement ist entweder in Form eines Mitnehmers direkt auf der Gewindespindel angebracht oder an einem solchen Mitnehmer befestigt, der seinerseits direkt an der Gewindespindel angebracht ist. Ein Arbeitsmedium, das zum Wärmetausch in einem Zwischenraum zwischen dem ersten Zylinderrohr und der Gewindespindel strömt, wird - wie eingangs erläutert - insbesondere beim Abkühlen Ablagerungen auf den Wärmeübertragungsflächen hinterlassen. Bei Erdgas als Arbeitsmedium bestehen diese Ablagerungen insbesondere aus Begleitstoffen und Wasser. Die genannten Ablagerungen können von dem Reinigungselement aufgenommen und/oder wegtransportiert bzw. mitgenommen werden. Zur Reinigung wird also die Gewindespindel betätigt, wodurch das Reinigungselement in axialer Richtung innerhalb des ersten Zylinderrohrs verschoben wird, wodurch es Ablagerungen von den wärmeübertragenden Flächen entfernen kann. Solche Ablagerungen entstehen insbesondere an der Gewindespindel sowie an den axial verlaufenden Führungsnuten des Wärmetauschers. Das Reinigungselement reinigt diese Flächen ab. Für das Reinigungselement können vorzugsweise Stähle, im speziellen Vergütungsstähle und Legierungen aus Buntmetallen, ferner kaltzähe Nickel-Legierungen (wie Inconel) sowie Gusswerkstoffe, verwendet werden.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. For cleaning, 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. Such 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. For the cleaning element, 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.

Bei Normalbetrieb des Wärmetauschers befindet sich das Reinigungselement in einer Ruheposition, in der es den Wärmetausch zwischen Arbeitsmedium und Kühlmittel geringstmöglich oder gar nicht beeinflusst. Statt eines Kühlmittels ist selbstverständlich auch die Verwendung eines Wärmemittels möglich, wenn das Arbeitsmedium erwärmt werden soll. Die Reinigung erfolgt beispielsweise nach empirisch ermittelten Periodendauern oder bei Erreichen eines extern gemessenen maximal zulässigen Differenzdrucks, der auf eine Verkleinerung des freien Strömungsquerschnitts für das Arbeitsmedium bedingt durch Ablagerungen schließen lässt.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. Instead of 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.

Der erfindungsgemäße Wärmetauscher mit Reinigungselement erlaubt eine effektive Reinigung der Wärmeübertragungsflächen, ohne manuell geöffnet werden zu müssen. Der geschilderte Reinigungsprozess ist einfach ausführbar. Hierzu muss lediglich die Gewindespindel gedreht werden, um das Reinigungselement in axialer Richtung zu verschieben. Weitere Prozessschritte sind nicht erforderlich. Es ist insbesondere vorteilhaft, wenn das Reinigungselement vorhandene Ablagerungen mitnimmt bzw. wegtransportiert. Auf diese Weise kann eine Veränderung und somit Abnutzung bzw. Alterung des Reinigungselements verhindert werden.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.

Das ohne Beschränkung der Allgemeinheit zum Wärmetausch genutzte Kühlmittel umströmt eine Außenfläche des ersten Zylinderrohrs. Erfindungsgemäss weist der Wärmetauscher ein zweites Zylinderrohr auf, das koaxial zu dem ersten Zylinderrohr angeordnet ist. In diesem Zusammenhang ist es weiterhin zweckmäßig, wenn eine Ein- und eine Austrittsöffnung für das Kühlmittel vorhanden ist, um Kühlmittel in einen bzw. aus einem Zwischenraum zwischen zweitem und erstem Zylinderrohr ein- bzw. auszulassen. In gleicher Weise ist es zweckmäßig, wenn eine Ein- und eine Austrittsöffnung für ein Arbeitsmedium vorhanden ist, um das Arbeitsmedium in einen bzw. aus einem Zwischenraum zwischen erstem Zylinderrohr und Gewindespindel ein- bzw. auszulassen.The coolant used for heat exchange without limiting the generality flows around an outer surface of the first cylinder tube. According to the invention, the heat exchanger has a second cylinder tube which is arranged coaxially to the first cylinder tube. In this context, it is also expedient if there is an inlet and an outlet opening for the coolant in order to let coolant in and out of an intermediate space between the second and first cylinder tube. In the same way, 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.

Es ist vorteilhaft, wenn das Reinigungselement als im Wesentlichen hohlzylindrisch geformtes Reinigungselement ausgebildet ist, wobei die Innenfläche des Reinigungselements ein Innengewinde korrespondierend zum Gewinde der Gewindespindel aufweist und wobei die Außenfläche des Reinigungselements Außennuten korrespondierend zu den Führungsnuten der Innenfläche des ersten Zylinderrohrs aufweist. Auf diese Weise kann das Reinigungselement in einfacher Weise (ohne gesonderten Mitnehmer) an der Gewindespindel angebracht werden und möglichst gründlich vorhandene Ablagerungen auf wärmeübertragenden Innenflächen im Zwischenraum zwischen Innenfläche des ersten Zylinderrohrs und Gewindespindel abräumen.It is advantageous if 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. In this way, 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.

Es ist zweckmäßig, wenn das Reinigungselement Aussparungen im ansonsten im Wesentlichen zylindrisch geformten Umfang des Reinigungselements aufweist, wobei sich diese Aussparungen parallel zur axialen Richtung erstrecken. Diese Aussparungen sind insbesondere im Reinigungselement in Umfangsrichtung äquidistant angeordnet. Die Aussparungen bzw. Einfräsungen erzeugen "Zähne" oder "Klauen" im Reinigungselement, die insbesondere ein Festfressen oder eine Blockade des Reinigungselements beim Reinigen vermeiden helfen. Von der Gewindespindel gelöste Ablagerungen können in die genannten Aussparungen bzw. Einfräsungen gelangen und von dort aus bei vertikalem Betrieb des Wäremtauschers zumindest in der Reinigungsphase nach unten (in Bewegungsrichtung des Reinigungselements) fallen. Auf diese Weise kann effektiv eine Blockade des Reinigungselements durch sich ansammelnde Ablagerungen vermieden werden.It is expedient if 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.

Weiterhin ist es zweckmäßig, wenn das Innengewinde des Reinigungselements einen in axialer Richtung sich vergrößernden Durchmesser aufweist. Durch diese Ausgestaltung wird erzielt, dass die Abreinigung der Gewindenuten nicht so abrupt erfolgt wie beispielsweise bei einem Reinigungselement, das in axialer Richtung über seine gesamte Ausdehnung auf den Gewindenuten aufsitzt. Hierdurch wird ein mögliches Festklemmen des Reinigungselements vermieden. In Verbindung mit der oben genannten Ausführungsform, bei der das Reinigungselement axiale Aussparungen aufweist, werden die hierdurch erzeugten einzelnen "Klauen" oder "Zähne" elastischer und pressen sich besser an die Außenwandung bzw. an die Gewindenuten an. Ein weiterer Vorteil ist der hierdurch gebildete Freiraum, vergleichbar mit einem Spankanal eines spanenden Bearbeitungsverfahrens.It is also useful if 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. In connection with the above-mentioned embodiment, in which the cleaning element has axial recesses, 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.

Gemäss der Erfindung weist die Außenfläche des ersten Zylinderrohrs eine in axialer Richtung spiralförmig verlaufende Wendel auf. Diese Wendel ist Bestandteil der Außenfläche des ersten Zylinderrohrs und ist auf diese Außenfläche aufgebracht oder durch Fräsen erzeugt. In den Zwischenräumen dieser Wendel kann dann das Kühlmittel spiralförmig in axialer Richtung fließen. Dieses erste Zylinderrohr mit dieser Wendel kann daher auch als Kühlwendel bezeichnet werden.According to the invention, 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.

Es ist vorteilhaft, wenn ein Ablagerungsspeicher für mittels des Reinigungselements ausgereinigte Ablagerungen/Verunreinigungen mit dem Zwischenraum zwischen Gewindespindel und Innenfläche des ersten Zylinderrohrs/Kühlwendel insbesondere thermisch entkoppelt verbunden ist. In dieser vorteilhaften Ausgestaltung transportiert das Reinigungselement Verunreinigungen in den Ablagerungsspeicher, der insbesondere von den genannten wärmeübertragenden Flächen, also dem Zwischenraum zwischen Gewindespindel und Innenfläche des ersten Zylinderrohrs, thermisch entkoppelt ist. Diese thermische Entkopplung erlaubt eine thermische Behandlung der im Ablagerungsspeicher gesammelten Begleitstoffe oder sonstige Ablagerungen ohne Einfluss auf den weiteren Betrieb des Wärmetauschers. Hierzu ist vorteilhafterweise ein Heizelement in oder am Wärmetauscher vorhanden und derart angeordnet, dass im Ablagerungsspeicher vorhandene Begleitstoffe/Verunreinigungen erwärmt werden können. Bei einer Abkühlung des Arbeitsmediums kommt es zu einem Auskondensieren der im Arbeitsmedium vorhandenen Verunreinigungen, wie Begleitstoffe und Wasser. Das Reinigungselement kann die auskondensierten Verunreinigungen in den Ablagerungsspeicher, der dann beispielsweise auch als Kondensatreservoir bezeichnet werden kann, transportieren. Das gesammelte Kondensat kann anschließend mittels des genannten Heizelements erwärmt werden. Das erwärmte, zum Schmelzen gebrachte Kondensat kann durch Öffnen eines nachgeschalteten Ventils über einen Kondensatablass abgelassen werden. Auf diese Weise kann zu gegebenen Zeiten der Ablagerungsspeicher seinerseits von vorhandenen Verunreinigungen befreit werden.It is advantageous if 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. In this advantageous embodiment, 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. For this purpose, 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. When the working medium cools down, the impurities present in the working medium, such as accompanying substances and water, condense. 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.

Es ist sinnvoll, während des Reinigungsvorgangs Kenntnis von der Position des Reinigungselements zu erhalten. Zu diesem Zweck ist vorteilhafterweise ein Positionsmessmittel vorhanden und derart angeordnet, dass die Position des Reinigungselements in axialer Richtung gemessen werden kann. Eine solche Positionsmessung ermöglicht bzw. vereinfacht es, die Drehrichtung der Gewindespindel an einer bestimmten vorgegebenen Position umzukehren, damit sich das Reinigungselement in entgegengesetzte Richtung zurückbewegt. Auch kann das Erreichen einer vorbestimmten Ruheposition mittels des Positionsmessers in einfacher Weise detektiert werden.It is useful to have knowledge of the position of the cleaning element during the cleaning process. For this purpose, 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.

Zum Antrieb der Gewindespindel ist es vorteilhaft, einen Antriebsmotor einzusetzen, wobei zwischen Antriebsmotor und dem Zwischenraum zwischen Gewindespindel und Innenfläche des ersten Zylinderrohrs, also zwischen Antriebsmotor und den wärmeleitenden Flächen des Wärmetauschers eine Partikelbarriere vorhanden ist. Eine solche Partikelbarriere verhindert das Eindringen von Fremdstoffen in den Raum, in dem das Arbeitsmedium zum Wärmetauscher fließt, und dient umgekehrt zum Schutz des Antriebsmotors bzw. dessen Lagers vor Partikeln.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. Such 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.

Zusammenfassend lässt sich folgender bevorzugter Aufbau eines erfindungsgemäßen Wärmetauschers festhalten, wobei die einzelnen Merkmale nicht zwingend in der hier angegeben Kombination verwirklicht sein müssen. Die innenliegende Gewindespindel ist von einem ersten Zylinderrohr bzw. der Kühlwendel umgeben. Letztere ist ihrerseits von einem zweiten Zylinderrohr bzw. einem Außenzylinderrohr umgeben. Der Zwischenraum zwischen Gewindespindel und Kühlwendel bildet den Arbeitsraum für das Arbeitsmedium, das über eine Eintrittsöffnung diesem Raum zugeführt und über ein Austrittsöffnung von diesem Raum nach Wärmetausch entfernt wird. Es kann zweckmäßig sein, die Strömungsrichtung umzukehren, wobei hierzu die genannte Eintrittsöffnung als Austrittsöffnung und die genannte Austrittsöffnung als Eintrittsöffnung verwendet wird. Es ist in einem solchen Fall jedoch vorteilhaft, auf der Seite der genannten Eintrittsöffnung eine weitere Austrittsöffnung und auf der Seite der genannten Austrittsöffnung eine weitere Eintrittsöffnung für das Arbeitsmedium am Wärmetauscher vorzusehen. In diesem Fall stehen zwei gegenüberliegende Anschlüsse jeweils für den Eintritt und für den Austritt des Arbeitsmediums zur Verfügung, die im Folgenden auch als "beidseitige" Eintrittsöffnung bzw. als "beidseitige" Austrittsöffnung bezeichnet werden.. Ein Kühlmittel wird über eine Kühlmitteleintrittsöffnung dem Zwischenraum zwischen Kühlwendel und Außenzylinderrohr zugegeben und durchströmt diesen Zwischenraum zu einer Kühlmittelaustrittsöffnung, um diesen Zwischenraum wieder zu verlassen. Für die Kühlmitteleintritts- und -austrittsöffnung gilt in analoger Weise das für die Eintritts- und Austrittsöffnung für das Arbeitsmedium gesagte, das heißt es ist vorteilhaft, einen beidseitigen Kühlmittel-Eintritt und -Austritt vorzusehen. Es ist sinnvoll, wenn die Strömung des Kühlmittels im Gegenstrom zur Strömung des Arbeitsmediums erfolgt. Es kann auch sinnvoll sein, wenn die Strömung des Kühlmittels im Gleichstrom zur Strömung des Arbeitsmediums erfolgt.In summary, the following preferred structure of a heat exchanger according to the invention can be recorded, the individual features not necessarily having to be implemented in the combination given here. 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. It can be expedient to reverse the direction of flow, for this purpose the named inlet opening is used as the outlet opening and the named outlet opening is used as the inlet opening. In such a case, however, it is advantageous to provide a further outlet opening on the side of the named inlet opening and a further inlet opening for the working medium on the heat exchanger on the side of the named outlet opening. In this case, two opposite connections are available for the inlet and outlet of the working medium, which are hereinafter also referred to as "double-sided" inlet or "double-sided" outlet. A coolant is supplied to the space between the cooling coil via a coolant inlet and outer cylinder tube is added and flows through this space to a coolant outlet opening in order to leave this space again. For the coolant inlet and outlet openings, the same applies to the inlet and outlet openings for the working medium, that is, it is advantageous to provide a coolant inlet and outlet on both sides. It makes sense if the flow of the coolant is countercurrent to the flow of the working medium. It can also be useful if the flow of the coolant takes place in parallel with the flow of the working medium.

Auf einer Seite des Wärmetauschers befindet sich ein Antriebsmotor, der die Gewindespindel in Drehung versetzt. Die Gewindespindel ist in einem Lager gelagert. An diesem Lager befindet sich ein Positionsmessmittel, das anhand der Anzahl von Umdrehungen des Antriebsmotors bei bekannter Steigung des Gewindes der Gewindespindel eine Information zur Position des von der Gewindespindel bewegten Reinigungselements liefern kann. Das Reinigungselement, das auch als Räumer bezeichnet werden kann, befindet sich in seiner Ruheposition bevorzugt auf der gleichen Seite wie der Antriebsmotor und ist von diesem durch eine Partikelbarriere getrennt. Eine solche Partikelbarriere kann beispielsweise aus PTFE gefertigt sein und ist dann auch bei niedrigen Temperaturen so weich, dass sich Partikel darin akkumulieren können. Der radiale Abstand zur Welle ist möglichst klein, idealerweise wenige Zehntel mm, vorzugsweise weniger als 0,4 mm, weiter vorzugsweise weniger als 0,3 mm, weiter vorzugsweise etwa gleich 0,2 mm.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. At this bearing there is 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. Such 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.

Auf der anderen Seite des Wärmetauschers befindet sich am Ende des Arbeitsraums, durch den das Arbeitsmedium fließt, ein Ablagerungsspeicher bzw. ein Kondensatreservoir, das insbesondere von diesem Arbeitsraum thermisch entkoppelt ist. Hieran anschließend folgt ein Heizelement, das mit dem Kondensatreservoir thermisch gekoppelt ist, um dieses zu erhitzen. Das Kondensatreservoir ist über einen Kondensatablass mit der Umgebung des Wärmetauschers verbunden, um den Inhalt des Kondensatreservoirs entleeren zu können. Ebenfalls an diesem Ende des Wärmetauschers befindet sich eine Gleitlagerbuchse für die Gewindespindel.On the other side of the heat exchanger, at the end of the working space through which the working medium flows, there is a deposit storage or a condensate reservoir, which in particular is thermally decoupled from this working space. This is followed by 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. There is also a plain bearing bush for the threaded spindle at this end of the heat exchanger.

Im Folgenden sei die Betriebsweise eines solchen vorteilhaften erfindungsgemäßen Wärmetauschers näher beschrieben: Je nach Strömungsrichtung strömt durch die jeweilige Arbeitsmedium-Eintrittsöffnung feuchtes, verschmutztes Arbeitsmedium in den Raum zwischen Gewindespindel und Kühlwendel ein und fließt in Richtung der gegenüberliegenden Austrittsöffnung. Das Arbeitsmedium strömt dabei in den Führungsnuten der Innenfläche der Kühlwendel entlang der Drehachse der Gewindespindel. Der Kühlwendel wird durch ein Kühlmittel Wärme entzogen, wobei dieses Kühlmittel vorzugsweise im Gegenstrom zum Arbeitsmedium in dem Raum fließt, der zwischen Kühlwendel und Außenzylinderrohr gebildet ist. Bedingt durch diese Kühlung fällt die Temperatur des Arbeitsmediums ab und Begleitstoffe bzw. Verunreinigungen fallen entsprechend ihrer Verflüssigungs- bzw. Erstarrungstemperaturen an den Wärmeübertragungsflächen aus. Diese Verunreinigungen verringern die Wärmeübertragungskapazität zwischen Arbeitsmedium und Kühlwendel.The operating mode of such an advantageous heat exchanger according to the invention is described in more detail below: Depending on the direction of flow, moist, dirty working medium flows through the respective working medium inlet opening into the space between the threaded spindle and cooling coil and flows in the direction of the opposite outlet opening. The working medium flows in the guide grooves of the inner surface of the cooling coil along the axis of rotation of the threaded spindle. Heat is extracted from the cooling coil by a coolant, this coolant preferably flowing in countercurrent to the working medium in the space that is formed between the cooling coil and the outer cylinder tube. As a result of this cooling, the temperature of the working medium drops and accompanying substances or impurities are precipitated on the heat transfer surfaces according to their liquefaction or solidification temperatures. These impurities reduce the heat transfer capacity between the working medium and the cooling coil.

Zum Zweck der Reinigung der Wärmeübertragungsflächen wird die Gewindespindel durch den Antriebsmotor in Rotation versetzt. Das Gehäuse des Antriebsmotors ist dabei vorzugsweise mit dem Zwischenraum, durch den das Arbeitsmedium strömt, verbunden und somit mit dem Betriebsdruck belastet. Das Gewinde der Gewindespindel ist dabei vorzugsweise als Rechtsgewinde mit Trapezprofil ausgeführt, wobei prinzipiell auch Linksgewinde und auch andere Flankenformen denkbar und vorteilhaft sein können. Hierzu sei auch auf das weiter unten stehende verwiesen. Das Reinigungselement bzw. der Räumer greift einerseits in das Gewinde der Gewindespindel ein und andererseits in die Führungs- bzw. Profilnuten der Kühlwendel, wodurch das Reinigungselement in eine Translationsbewegung versetzt wird.For the purpose of cleaning the heat transfer surfaces, 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.

Aufgrund der definierten Gewindesteigung der Gewindespindel kann mit Hilfe der durch das Positionsmittel gemessenen Anzahl von Umdrehungen des Antriebsmotors die Position des Reinigungselements erfasst werden. Das Reinigungselement gleitet dabei bis zu dem thermisch entkoppelten Kondensatreservoir bzw. Ablagerungsspeicher am Ende des Arbeitsraums. Das Reinigungselement schiebt somit die vorhandenen mitgeführten Ablagerungen in das Kondensatreservoir. Sobald die entsprechende Position erreicht ist, wird die Drehrichtung des Antriebsmotors umgekehrt und das Reinigungselement wandert zurück in seine Ruheposition neben der Partikelbarriere. Das gesammelte Kondensat kann von dem Heizelement erwärmt werden und je nach Aggregatzustand zum Schmelzen oder zum Verdampfen gebracht und anschließend durch Öffnen eines nachgeschalteten Ventils durch den vorzugsweise beidseitigen Kondensatablass abgelassen werden.Due to the defined thread pitch of the threaded spindle, 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. As soon as the corresponding position is reached, 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.

Es ist insbesondere vorteilhaft, mehrere in Serie geschaltete Wärmetauscher zu einer Wärmetauscheranlage zu kombinieren. Durch einen solchen stufenweisen Aufbau können Verunreinigungen "ausgefroren" werden, wenn die einzelnen Stufen jeweils bei tieferen Temperaturen betrieben werden.It is particularly advantageous to combine several heat exchangers connected in series to form a heat exchanger system. With such a step-by-step structure, impurities can be "frozen out" if the individual steps are operated at lower temperatures.

Alternativ zu der genannten Gewindespindel mit Trapezprofil kann mit Vorteil eine Gewindespindel mit Kreuzgewinde eingesetzt werden. Solche Gewindespindeln sind an sich bekannt und werden als Kreuzgewindespindeln bezeichnet. Gewindespindeln mit Trapezprofilen können entsprechend ihrer Rotationsrichtung immer nur eine zugeordnete Bewegungsrichtung abbilden, die sich in Folge dessen bei der Umkehr der Rotationsrichtung ebenfalls umkehrt. Die Umkehrung der Drehrichtung bedarf eines Schaltelements in der elektrischen Anspeisung des Antriebsmotors bzw. einem Wechselgetriebe. Um ein Überfahren von definierten Endlagen auf Gewindespindeln gleitenden Elementen, wie das Reinigungselement, zu vermeiden, sind diese häufig mit einem Positionsanschlag ausgestattet. Alternativ wird die Position des gleitenden Elements mit einem Positionserfassungsmittel erfasst.As an alternative to the aforementioned threaded spindle with a trapezoidal profile, 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. In order to avoid overrunning defined end positions on threaded spindles sliding elements, such as the cleaning element, these are common equipped with a position stop. Alternatively, the position of the sliding element is detected with a position detection means.

Der Einsatz von Kreuzgewindespindeln überwindet diese Nachteile. Ein Kreuzgewinde ist derart aufgebaut, dass auf einer Spindel sowohl ein Links- als auch ein Rechtsgewindegang vorzugsweise jeweils gleicher Steigung abgebildet ist, der in seinen jeweiligen Endlagen eine Umkehrstelle besitzt, in der wenigstens ein in der Gewindenut gleitender Gleitstein von einer ersten Bewegungsrichtung in eine zweite Bewegungsrichtung überführt wird. Die Rotationsrichtung der Welle der Gewindespindel bleibt somit stets gleich. Somit entfällt bei Verwendung einer Kreuzgewindespindel auch die Notwendigkeit des oben erläuterten Positionsmessmittels für die Position des Reinigungselements. Hierzu muss die obere Endlagenbestimmung, also die Bestimmung der Ruheposition des Reinigungselements über ein alternatives Verfahren erfolgen. Hierzu ist beispielsweise eine Drehmomentmessung möglich, die markante Änderungen des Drehmoments in den beiden Endlagen des Reinigungselements registriert. Zusätzlich oder alternativ können die Endlagen oder zumindest die obere Endlage der Ruheposition mittels Initiatoren, also Endlagenschalter, ermittelt werden.The use of cross-thread spindles overcomes these disadvantages. 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. Thus, when using a cross-threaded spindle, the need for the position measuring means explained above for the position of the cleaning element is eliminated. For this purpose, the upper end position determination, i.e. the determination of the rest position of the cleaning element, must be carried out using an alternative method. For this purpose, a torque measurement is possible, for example, which registers significant changes in the torque in the two end positions of the cleaning element. Additionally or alternatively, 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.

In einer vereinfachten Ausgestaltung verfügt der erfindungsgemäße Wärmetauscher folglich über eine Kreuzgewindespindel mit wenigstens einem Gleitstein, der in den Gewindegängen gleitet und einen mit dem Gleitstein beispielsweise über einen Bolzen verbundenen Räumer bzw. Reinigungselement.In a simplified embodiment, 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.

Die Vorteile der Verwendung der Kreuzgewindespindel liegen in einer automatischen Umkehr der Bewegungsrichtung, ohne die Drehrichtung der Welle zu ändern, sodass ein Abbremsen und erneutes Anfahren des Elektromotors obsolet wird, was wiederum einen energetisch sparsameren Prozess zur Folge hat. Weiterhin muss, wie bereits ausgeführt, keine elektrische Einrichtung zur Drehrichtungsumkehr vorgesehen werden bzw. entfällt ein entsprechender Programmteil in der Steuerung. Insgesamt wird der Reinigungsvorgang des Wärmetauschers durch die entfallene Richtungsumkehr verkürzt. Die Endlagenpositionen des Reinigungselements werden durch den Umkehrschliff des Kreuzgewindes automatisch definiert und können somit nicht überfahren werden. Schließlich können die oben beschriebenen Positionsmessmittel entfallen.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.

Die Erfindung betrifft weiterhin eine Verwendung des erfindungsgemäßen Wärmetauschers zur Verflüssigung eines Gases. Hierbei ist koaxial zum ersten Zylinderrohr des Wärmetauschers ein zweites Zylinderrohr angeordnet, wobei zwischen erstem und zweitem Zylinderrohr ein Kühlmittel strömt. Weiterhin strömt zwischen erstem Zylinderrohr und Gewindespindel ein Arbeitsmedium, welches das zu verflüssigende Gas enthält. Beim oben beschriebenen Beispiel von Erdgas kann das zu verflüssigende Gas beispielsweise Stickstoff sein. Das Kühlmedium strömt bei einer niedrigeren Temperatur als das Arbeitsmedium, wobei der Druck und die Temperatur des Kühlmediums sowie der Druck des Arbeitsmediums derart eingestellt werden, dass durch den Wärmetausch mit dem Kühlmedium das zu verflüssigende Gas im Arbeitsmedium sich verflüssigt. Im oben genannten Beispiel von Erdgas kann beispielsweise als Kühlmedium verflüssigter Stickstoff bei einem Druck von 1 bar und einer Temperatur von -196°C eingesetzt werden. Das Arbeitsmedium (Erdgas) wird, insbesondere nach entsprechender Vorkühlung durch vorgeschaltete Wärmetauscher mit einem Druck von beispielsweise 10 bar eingeleitet. Durch Wärmetausch mit dem Kühlmedium kann sich der im Erdgas enthaltene Stickstoff auf eine Temperatur von - 170°C und darunter abkühlen, so dass er bei einem Druck von 10 bar sich verflüssigt.The invention also relates to a use of the heat exchanger according to the invention for liquefying a gas. Here, 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. Furthermore, a working medium containing the gas to be liquefied flows between the first cylinder tube and the threaded spindle. In the example of natural gas described above, 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. In the above example of 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 (natural gas) is introduced through an upstream heat exchanger at a pressure of, for example, 10 bar, in particular after appropriate pre-cooling. By exchanging heat with the cooling medium, 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.

Das genannte Verfahren kann analog zur Verflüssigung von Helium, Sauerstoff und/oder Wasserstoff als ein oder mehrere Bestandteile in einem Arbeitsmedium eingesetzt werden. Konkrete Beispiele für die Verflüssigung von Helium, Wasserstoff und Sauerstoff sind im Folgenden angegeben:
Verflüssigung von verschiedenen Gasen beispielsweise zum Zweck der Abscheidung aus GasgemischenThe 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

Verflüssigung von OLiquefaction of O 22 ::

  • Kühlmedium vorzugsweise Flüssigstickstoff zwischen 1 und 15bar;Cooling medium preferably liquid nitrogen between 1 and 15bar;
  • Temperaturbereich des Kühlmediums -163°C@15bar bis -196°C@1bar;Temperature range of the cooling medium -163 ° C @ 15bar to -196 ° C @ 1bar;
  • Druck des zu verflüssigenden O2 1bar-50bar;Pressure of the O 2 to be liquefied 1 bar-50 bar;
  • erste Verflüssigungstemperatur @ 1bar -183°C;first condensing temperature @ 1bar -183 ° C;
  • zweite Verflüssigungstemperatur @ 50bar -119°C;second condensing temperature @ 50bar -119 ° C;

Der Druck des Kühlmediums wird jeweils so gewählt, dass die Temperatur des Kühlmediums stets geringer ist als die des Arbeitsmediums.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.

Verflüssigung von HLiquefaction of H 22 ::

  • Kühlmedium vorzugsweise Flüssighelium zwischen 1 und 2,2bar;Cooling medium preferably liquid helium between 1 and 2.2 bar;
  • Temperaturbereich des Kühlmediums -267°C@2,2bar bis -268°C@1bar;Temperature range of the cooling medium -267 ° C @ 2.2bar to -268 ° C @ 1bar;

Der Druck des Kühlmediums wird jeweils so gewählt, dass die Temperatur des Kühlmediums stets geringer ist als die des Arbeitsmediums.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.

Alternatives Kühlmedium Flüssigwasserstoff zwischen 1 und 13bar; Temperaturbereich des Kühlmediums -240°C@13bar bis -253°C@1bar. Im speziellen Fall, dass als Kühlmedium das gleiche Medium wie das zu verflüssigende Medium verwendet wird, muss der Druck im Kühlmedium geringer sein als der Druck des Arbeitsmediums, sodass die Kühlmitteltemperatur aufgrund des niedrigeren Gleichgewichtspunkts geringer ist.

  • Druck des zu verflüssigenden H2 1bar - 13bar;
  • erste Verflüssigungstemperatur @ 1bar -253°C;
  • zweite Verflüssigungstemperatur @ 13bar -240°C;
Alternative cooling medium liquid hydrogen between 1 and 13bar; Temperature range of the cooling medium -240 ° C @ 13bar to -253 ° C @ 1bar. In the special case that the same medium as the medium to be liquefied is used as the cooling medium, the pressure in the cooling medium must be lower than the pressure of the working medium, so that the coolant temperature is lower due to the lower equilibrium point.
  • Pressure of the H 2 to be liquefied 1 bar - 13 bar;
  • first condensing temperature @ 1bar -253 ° C;
  • second condensing temperature @ 13bar -240 ° C;

Verflüssigung von He:Liquefaction of He:

  • Kühlmedium vorzugsweise Flüssighelium zwischen 1 und 2,2bar;Cooling medium preferably liquid helium between 1 and 2.2 bar;
  • Temperaturbereich des Kühlmediums -267°C@2,2bar bis -268°C@1bar;Temperature range of the cooling medium -267 ° C @ 2.2bar to -268 ° C @ 1bar;

Im speziellen Fall, dass als Kühlmedium das gleiche Medium wie das zu verflüssigende Medium verwendet wird, muss der Druck im Kühlmedium geringer sein als der Druck des Arbeitsmediums, sodass die Kühlmitteltemperatur aufgrund des niedrigeren Gleichgewichtspunkts geringer ist.

  • Druck des zu verflüssigenden He 1bar - 2,2bar;
  • erste Verflüssigungstemperatur @ 1bar -268°C;
  • zweite Verflüssigungstemperatur @ 2,2bar -267°C;
In the special case that the same medium as the medium to be liquefied is used as the cooling medium, the pressure in the cooling medium must be lower than the pressure of the working medium, so that the coolant temperature is lower due to the lower equilibrium point.
  • Pressure of the He to be liquefied 1bar - 2.2bar;
  • first condensing temperature @ 1bar -268 ° C;
  • second condensing temperature @ 2.2bar -267 ° C;

Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It goes without saying that the features mentioned above and those yet to be explained below can be used not only in the respectively specified combination, but also in other combinations or alone, without departing from the scope of the present invention.

Die Erfindung ist anhand eines Ausführungsbeispiels in der Zeichnung schematisch dargestellt und wird im Folgenden unter Bezugnahme auf die Zeichnung beschrieben.The invention is shown schematically in the drawing using an exemplary embodiment and is described below with reference to the drawing.

Kurze Beschreibung der FigurenBrief description of the figures

Figur 1Figure 1
zeigt schematisch einen in Längsschnitt einer vorteilhaften Ausführungsform eines erfindungsgemäßen Wärmetauschers,shows schematically a longitudinal section of an advantageous embodiment of a heat exchanger according to the invention,
Figur 2Figure 2
zeigt eine Kühlwendel als erstes Zylinderrohr des in Figur 1 dargestellten Wärmetauschers,shows a cooling coil as the first cylinder tube of the in Figure 1 shown heat exchanger,
Figur 3Figure 3
zeigt ein Reinigungselement, wie es bei dem Wärmetauscher gemäß Figur 1 eingesetzt ist, undshows a cleaning element as it is in the heat exchanger according to FIG Figure 1 is used, and
Figur 4Figure 4
zeigt schematisch den Ausschnitt einer Gewindespindel mit einem Kreuzgewinde.shows schematically the detail of a threaded spindle with a cross thread.
Ausführliche Beschreibung der FigurenDetailed description of the figures

Figur 1 zeigt schematisch einen Längsschnitt durch eine Ausführungsform eines Wärmetauschers 13, wie er insbesondere zur Kühlung von Erdgas verwendet werden kann. In dieser einfachen Ausgestaltung weist der Wärmetauscher 13 ein Außenzylinderrohr 1 auf, das eine Kühlwendel 2 umgibt. Diese Kühlwendel 2 ist ihrerseits als Zylinderrohr ausgeführt und weist wenigstens einen, vorzugsweise spiralförmigen Kanal 23 an ihrer Außenfläche auf, der der Führung eines Kühlmittels dient. Wie in Figur 2 dargestellt, wird dieser Kanal 23 durch eine entsprechende Wendel 21 auf der Außenfläche der Kühlwendel 2 erzeugt. Die Innenfläche der hohlzylindrischen Kühlwendel weist Führungs- bzw. Profilnuten 22 auf. Diese wenigstens eine Führungsnut 22 dient der Führung eines Reinigungselements oder Räumers 12. Figure 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. In this simple embodiment, 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. As in Figure 2 shown, 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.

Im Inneren der Kühlwendel 2 befindet sich koaxial zu dieser eine Gewindespindel 3. Die Gewindespindel 3 wird von einem Antriebsmotor 4 angetrieben und ist in einer Lagerstelle gelagert, die vorzugsweise als Axial-/Radial-Mischlager 5 ausgeführt ist. Am anderen Ende der Gewindespindel 3 ist diese in einer radialen Lagerstelle, die vorzugsweise als Gleitlagerbuchse 8 ausgeführt ist, gelagert. An diesem Ende des Wärmetauschers 13 ist außerdem ein thermisch entkoppeltes Kondensatreservoir 7 sowie ein Heizelement 9 zur Erhitzung von Kondensat in dem Kondensatreservoir 7 vorhanden.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. At the other end of the threaded spindle 3, 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.

Am anderen Ende des Wärmetauschers 13 trennt eine Partikelbarriere 11 den Antriebsmotor 4 von dem Arbeitsraum für das Arbeitsmedium. Die Partikelbarriere 11 dient außerdem zum Schutz des Antriebsmotors 4 und des Lagers 5 vor groben Partikeln, agiert aber nicht als Gasdichtung.At the other end of the heat exchanger 13, 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.

In der hier dargestellten Ausführungsform gemäß Figur 1 sind mehrere Außenzylinderrohre 1 durch eine Klemmvorrichtung 10 verbunden. Die Klemmvorrichtung 10 ist so aufgebaut, dass zwei Überwurfringe mit einem Innengewinde auf das Außenzylinderrohr 1, das wiederum mit einem Außengewinde versehen ist, aufgeschraubt werden. Die Überwurfringe werden mittels Schrauben zusammengezogen und die einzelnen Segmente werden aneinander gepresst und durch eine Dichtung abgedichtet. Auch mehrere solcher Außenzylinderrohre können als ein "Außenzylinderrohr" verstanden und bezeichnet werden.In the embodiment shown here according to Figure 1 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”.

Ein Reinigungselement oder Räumer 12 ist neben der Partikelbarriere 11 in seiner Ruheposition angeordnet. Bei Inbetriebnahme des Antriebsmotors 4 wird die Gewindespindel 3 in Drehung versetzt, sodass der Räumer 12 auf der Gewindespindel entlang den Führungs- bzw. Profilnuten 22 der Kühlwendel 2 in axialer Richtung verschoben wird. Im vorliegenden Beispiel wird eine Gewindespindel 3 beispielsweise mit Trapezprofil eingesetzt. Eine Umkehr der Bewegungsrichtung des Räumers 12 setzt eine Umkehr der Rotationsrichtung der Gewindespindel 3 voraus. Eine andere Ausführungsart der Gewindespindel 3 ist weiter unten im Zusammenhang mit Figur 4 erläutert.A cleaning element or scraper 12 is arranged next to the particle barrier 11 in its rest position. When the drive motor 4 is started up, 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. In the present example, 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.

Im Betrieb des Wärmetauschers 13 wird über eine Arbeitsmedium-Eintrittsöffnung 14 beispielsweise feuchtes, verschmutztes Arbeitsmedium in den Zwischenraum zwischen Gewindespindel 3 und zwischen Kühlwendel 2 geführt und strömt in axialer Richtung zu der Arbeitsmedium-Austrittsöffnung 15 am anderen Ende des Wärmetauschers 13. Das Arbeitsmedium strömt dabei in den Profilnuten 22 auf der Innenfläche der hohlzylindrischen Kühlwendel 2 (vgl. Figur 2) entlang der Drehachse der Gewindespindel 3. Über eine Kühlmittel-Eintrittsöffnung 16 wird dem Raum zwischen Kühlwendel 2 und Außenzylinderrohr 1 Kühlmittel zugeführt, das zum anderen Ende des Wärmetauschers 13 fließt und diesen durch die Kühlmittel-Austrittsöffnung 17 verlässt. Das Kühlmittel strömt dabei in dem zwischen Außenzylinderrohr 1 und Kühlwendel 2 gebildeten Kanal 23 spiralförmig in axialer Richtung. Das Kühlmittel entzieht der Kühlwendel 2 Wärme, sodass wiederum dem Arbeitsmedium Wärme entzogen wird.During operation of the heat exchanger 13, for example, 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.

In einem speziellen Anwendungsfall wird Erdgas mit einem Druck von 4 bis maximal 220 bar aus einer unterirdischen Kaverne auf eine Temperatur von ca. 20°C temperiert. In einem ersten Wärmetauscher wird das Arbeitsmedium auf vorzugsweise 1°C abgekühlt. In einem zweiten Wärmetauscher, der mit dem ersten Wärmetauscher in Serie geschaltet ist, wird das Arbeitsmedium auf vorzugsweise -40°C bis -60°C abgekühlt. In einer dritten Stufe wird das Arbeitsmedium auf vorzugsweise -80°C bis - 150°C abgekühlt und in einer letzten Stufe wird das Arbeitsmedium über einen wiederum in Serie geschalteten Wärmetauscher verflüssigt. Die Temperatur des Erdgases wird dabei auf bis zu -196°C abgesenkt, wobei es zur Unterkühlung des Erdgases kommt. Die erste Stufe fällt dabei einen Großteil des Wasseranteils aus, die nächsten Stufen hauptsächlich die höheren Kohlenwasserstoffe, CO2 sowie weitere Begleitstoffe. Durch die in den jeweiligen Stufen der Wärmetauscher 13 vorhandenen Räumer 12 können auskondensierte Bestandteile jeweils von den wärmeübertragenden Flächen abgereinigt werden.In a special application, 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. In a second heat exchanger, which is connected in series with the first heat exchanger, the working medium is preferably cooled to -40 ° C to -60 ° C. In a third stage, 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. By means of the scrapers 12 present in the respective stages of the heat exchangers 13, condensed components can be cleaned from the heat-transferring surfaces.

Die ersten beiden Wärmetauscherstufen werden in diesem konkreten Anbindungsfall durch Kältemaschinen gekühlt, die beiden weiteren durch Flüssigstickstoff, tiefkaltes flüssiges CNG oder durch tiefkalten gasförmigen Stickstoff. Der maximale Betriebsdruck des Wärmetauschers ist 300 bar, die zulässigen Betriebstemperaturen betragen 100°C bis -200°C.In this specific connection, 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.

Durch die unterschiedlichen Druckverhältnisse zwischen dem Kühlmedium, beispielsweise Stickstoff bei maximal 10 bar, und dem Arbeitsmedium, hier CNG mit Begleitstoffen unter anderem von Stickstoff von 4 bis 220 bar, kann Stickstoff als Begleitstoff bei hohem Druck (bspw. bei 10 bar) durch Flüssigstickstoff bei niedrigem Druck (bspw. bei 1 bar), bedingt durch die unterschiedlichen druckabhängigen Phasenübergänge zum Verflüssigen gebracht und abgeschieden werden. Der hier vorgeschlagene Wärmetauscher 13 kann somit auch zur Verflüssigung von Stickstoff eingesetzt werden.Due to the different pressure ratios between the cooling medium, for example nitrogen at a maximum of 10 bar, and the working medium, here CNG with accompanying substances including nitrogen from 4 to 220 bar, 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. This here The proposed heat exchanger 13 can thus also be used to liquefy nitrogen.

Zum Zwecke der Reinigung der Wärmeübertragungsflächen, beispielsweise von Wasser bzw. Eis in der ersten Stufe bzw. von höheren Kohlenwasserstoffen, CO2 und weiteren Begleitstoffen in der zweiten und weiteren Stufe, wird die Gewindespindel 3 einer Stufe durch den Antriebsmotor 4 in Rotation versetzt. Der Räumer 12, der einerseits in das Gewinde der Gewindespindel 3 und andererseits in die Profilnuten 22 der Kühlwendel 2 eingreift, wird hierdurch in eine Translationsbewegung versetzt. Auf seinem Weg in Richtung Kondensatreservoir 7 nimmt der Räumer 12 die genannten auskondensierten Begleitstoffe mit. Diese werden bei Erreichen des Kondensatreservoirs 7 in das selbige geschoben. Das Positionsmessmittel 6 kann aufgrund der definierten Gewindesteigung der Gewindespindel 3 aus der Anzahl der gemessenen Umdrehungen des Antriebsmotors 4 die Position des Räumers 12 bestimmen. Sobald die Position des Kondensatreservoirs 7 erreicht ist, wird die Drehrichtung des Antriebsmotors 4 umgekehrt, sodass der Räumer 12 zurück in seine Ruheposition wandert. Es ist zweckmäßig, wenn die Ruheposition die obere Endposition und die Position des Kondensatreservoirs 7 die untere Endposition des Räumers 12 bei vertikaler Stellung des Wärmetauschers darstellt.For the purpose of cleaning the heat transfer surfaces, for example of water or ice in the first stage or of higher hydrocarbons, CO 2 and other accompanying substances in the second and further stages, 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. On its way in the direction of the condensate reservoir 7, 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.

Das gesammelte Kondensat wird über das Heizelement 9 erwärmt und somit zum Schmelzen gebracht. Durch Öffnen eines nachgeschalteten Ventils können die Begleitstoffe durch einen Kondensatablass 18 abgelassen werden.The collected condensate is heated by the heating element 9 and thus melted. By opening a downstream valve, the accompanying substances can be drained off through a condensate drain 18.

Die Reinigung der wärmetauschenden Flächen des Wärmetauschers 13 erfolgt beispielsweise nach empirisch ermitteltem Periodendauern oder bei Erreichen eines extern gemessenen maximal zulässigen Differenzdrucks, der auf eine Verkleinerung des freien Strömungsquerschnitts im Arbeitsraum bedingt durch abgelagerte Begleitstoffe schließen lässt. Durch die Abreinigung wird ein möglichst hoher und konstanter Wärmeübertragungswert erzielt. Im Vergleich zu den Systemen nach dem Stand der Technik beansprucht der Wärmetauscher 13 aufgrund der effektiv genutzten Wärmeübertragungsflächen ein geringeres Bauvolumen.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.

Der segmentweise Aufbau des Wärmeübertragers 13 ermöglicht einen modularen Aufbau. Die Wärmeübertragungsleistung ist somit über die Vergrößerung bzw. Verkleinerung der Wärmeübertragungsflächen variierbar.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.

Durch den Einsatz des genannten Positionserfassungsmittels 6 wird stets die IstPosition des Räumers 12 überwacht. Ein etwaiges Festfressen kann durch Messung des Schlupfs frühzeitig erkannt werden.By using the aforementioned position detection means 6, the actual position of the scraper 12 is always monitored. Any seizure can be detected at an early stage by measuring the slip.

Es sei darauf hingewiesen, dass der hier erläuterte Wärmetauscher 13 nicht nur für die Erdgasverflüssigung, sondern für eine Vielzahl industrieller Anwendungen mit entsprechenden Arbeitsmedien adaptierbar und einsetzbar ist. Der Räumer 12 kann als wenig komplexes Austauschteil an die Bedürfnisse der jeweiligen Einsatzgebiete angepasst und im Schadensfall rasch ersetzt werden.It should be pointed out that 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. As a less complex replacement part, the scraper 12 can be adapted to the needs of the respective areas of use and quickly replaced in the event of damage.

Figur 3 zeigt einen Räumer 12 bzw. ein Reinigungselement 12, wie es in dem Wärmetauscher 13 zum Einsatz kommen kann. Dargestellt sind die Außennuten 122 des Räumers 12, die den Führungsnuten 22 der Kühlwendel 2 entsprechen. Das Innengewinde 121 des Räumers 12 entspricht dem Gewinde der Gewindespindel 3. Der Räumer 12 weist Aussparungen bzw. Einfräsungen 123 auf. Durch letztere enthält der Räumer 12 "Zähne" bzw. "Klauen", die vermeiden, dass sich Ablagerungen im Gewinde ansammeln und zu einem Blockieren des Räumers 12 führen. Die Ablagerungen können nämlich durch die Aussparungen bzw. Einfräsungen 123 in den Zwischenraum eintreten und bei vertikaler Lage des Wärmetauschers nach unten Richtung Kondensatreservoir 7 fallen. Weiterhin dient der in Bewegungsrichtung des Abreinigens sich vergrößernde Innendurchmesser des Räumers 12 zum leichteren Einführen in die verunreinigte Gewindespindel bei Beginn des Reinigungsprozesses. Figure 3 shows a scraper 12 or a cleaning element 12, as it can be used in the heat exchanger 13. The outer grooves 122 of the reamer 12, which correspond to the guide grooves 22 of the cooling coil 2, are shown. 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. As a result of the latter, 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. Furthermore, 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.

Figur 4 zeigt schließlich eine alternative Ausgestaltung einer Gewindespindel 3', bei der es sich um eine Kreuzgewindespindel 3' handelt. Die Welle mit Kreuzgewinde ist mit 31 bezeichnet. Der darin laufende Gleitstein mit 32. Bei dieser Ausgestaltung ist der Räumer 12 mit dem Gleitstein 32 verbunden und bewegt sich bei Rotation der Gewindespindel 3' in axialer Richtung. 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 sliding block running therein with 32. In this embodiment, the reamer 12 is connected to the sliding block 32 and moves in the axial direction when the threaded spindle 3 'rotates.

Vorteil ist hier, wie oben bereits erläutert, dass der in der Gewindenut gleitende Gleitstein 32 bei Drehung der Gewindespindel 3' in einer einzigen Rotationsrichtung von einer ersten Bewegungsrichtung in eine zweite, entgegengesetzte Bewegungsrichtung überführt wird, ohne die Rotationsrichtung der Welle 31 zu ändern. Durch die Überlagerung des Links- und Rechtsgewindegangs bildet sich auf der Welle 32 ein typisch deltoid-förmiges Muster aus.The advantage here, as already explained above, is that the sliding block 32 sliding in the thread groove is transferred from a first direction of movement to a second, opposite direction of movement when the threaded spindle 3 'rotates in a single direction of rotation, without changing the direction of rotation of the shaft 31. As a result of the overlapping of the left-hand and right-hand threads, a typical deltoid-shaped pattern is formed on the shaft 32.

Wie ebenfalls oben beschrieben, ermöglicht die Gewindespindel 3' ein energetisch sparsameren Prozess, da der Elektromotor nicht abgebremst und erneut gestartet werden muss. Außerdem kann eine Positionsmessung des Räumers 12 und somit das in Figur 1 dargestellte Positionsmessmittel 6 entfallen. Der Abreinigungsvorgang des Wärmetauschers 13 wird durch den Entfall der Richtungsumkehr nochmals verkürzt.As also described above, the threaded spindle 3 'enables a more energy-efficient process, since the electric motor does not have to be braked and restarted. In addition, 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.

BezuqszeichenlisteReference list

11
Außenzylinderrohr, zweites ZylinderrohrOuter cylinder tube, second cylinder tube
22
Kühlwendel, erstes ZylinderrohrCooling coil, first cylinder tube
3, 3'3, 3 '
GewindespindelThreaded spindle
44th
AntriebsmotorDrive motor
55
Axial-/RadiallagerAxial / radial bearings
66th
PositionsmessmittelPosition measuring equipment
77th
Kondensatreservoir, AblagerungsspeicherCondensate reservoir, sediment storage
88th
GleitlagerbuchsePlain bearing bush
99
HeizelementHeating element
1010
KlemmvorrichtungClamping device
1111
PartikelbarriereParticle barrier
1212
Räumer, ReinigungselementCleaner, cleaning element
1313
WärmetauscherHeat exchanger
1414th
Arbeitsmedium-EintrittsöffnungWorking medium inlet opening
1515th
Arbeitsmedium-AustrittsöffnungWorking medium outlet opening
1616
Kühlmittel-EintrittsöffnungCoolant inlet opening
1717th
Kühlmittel-AustrittsöffnungCoolant outlet opening
1818th
KondensatablassCondensate drain
2121st
WendelHelix
2222nd
Führungsnut, ProfilnutGuide groove, profile groove
2323
Kanalchannel
121121
Innengewinde des ReinigungselementsInternal thread of the cleaning element
122122
AußennutExternal groove
123123
Aussparung, EinfräsungRecess, milling
3131
Welle der Gewindespindel 3'Lead screw shaft 3 '
3232
GleitsteinSliding block

Claims (15)

  1. Heat exchanger, having
    a first cylinder tube (2) and a threaded spindle (3) extending coaxially in the first cylinder tube (2),
    wherein the inner surface of the first cylinder tube (2) has guide grooves (22), and wherein a cleaning element (12) is mounted on the threaded spindle (3) in such a way that the cleaning element (12) is displaced in the axial direction along the guide grooves (22) via rotation of the threaded spindle (3),
    characterized in that a second cylinder tube (1) is arranged coaxially with the first cylinder tube (2), and wherein
    the outer surface of the first cylinder tube (2) has a helix (21) extending in a spiral in the axial direction.
  2. Heat exchanger according to one of the preceding claims, wherein the cleaning element (12) is designed as a substantially hollow cylindrical cleaning element (12), wherein the inner surface of the cleaning element (12) has an internal thread (121) corresponding to the thread of the threaded spindle (3), and wherein the outer surface of the cleaning element (12) has external grooves (122) corresponding to the guide grooves (22) of the inner surface of the first cylinder tube (2).
  3. Heat exchanger according to claim 2, in which the cleaning element (12) has, in the otherwise substantially cylindrical circumference, recesses (123) extending parallel to the axial direction.
  4. Heat exchanger according to claim 3, in which the recesses (123) in the cleaning element (12) are arranged equidistantly in the circumferential direction.
  5. Heat exchanger according to one of claims 2-4, in which the internal thread (121) of the cleaning element (12) has a diameter which increases in the axial direction.
  6. Heat exchanger according to one of the preceding claims, wherein a deposition storage (7) for contaminants cleaned off by means of the cleaning element (12) is connected, in particular in a thermally decoupled manner, to the intermediate space between the threaded spindle (3) and the inner surface of the first cylinder tube (2).
  7. Heat exchanger according to Claim 6, in which a heating element (9) is present and arranged in such a way that contaminants present in the deposition storage (7) can be heated.
  8. Heat exchanger according to one of the preceding claims, in which a position measuring means (6) is present and arranged in such a way that the position of the cleaning element (12) can be measured in the axial direction.
  9. Heat exchanger according to one of the preceding claims, wherein a drive motor (4) is present for driving the threaded spindle (3), and wherein a particle barrier (11) is present between the drive motor (4) and the intermediate space between the threaded spindle (3) and the inner surface of the first cylinder tube (2).
  10. Heat exchanger according to one of the preceding claims, wherein the threaded spindle (3) has a trapezoidal profile as a thread profile.
  11. Heat exchanger according to one of claims 1 to 9, wherein the threaded spindle (3') has a cross-thread as a thread.
  12. Heat exchanger according to claim 11, in which a sliding block (32), which is connected to the cleaning element (12), is mounted so as to slide in the thread groove of the cross-thread of the threaded spindle (3').
  13. Heat exchanger system having a plurality of serially connected heat exchangers according to one of claims 1 to 12.
  14. Use of a heat exchanger according to one of claims 1-12 for liquefying a gas, in which
    a second cylinder tube (1) is arranged coaxially with the first cylinder tube (2), a coolant flows between the first and the second cylinder tube,
    a working medium which contains the gas to be liquefied flows between the first cylinder tube (2) and the threaded spindle (3), and
    wherein the cooling medium flows at a lower temperature than the working medium, wherein the pressure and temperature of the cooling medium and the pressure of the working medium are adjusted in such a way that the gas to be liquefied in the working medium liquefies as a result of the heat exchange with the cooling medium.
  15. Use according to claim 14, wherein the same medium as the gas to be liquefied is used as the cooling medium, wherein the pressure of the cooling medium is selected to be lower than that of the working medium.
EP16747730.6A 2015-08-11 2016-08-02 Heat exchanger Active EP3334995B1 (en)

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EP3567333A1 (en) 2018-05-09 2019-11-13 Linde Aktiengesellschaft Drive device for a cleaning device for a heat exchanger
EP3567329A1 (en) 2018-05-09 2019-11-13 Linde Aktiengesellschaft Condensate extraction device and heat exchanger
EP3566794A1 (en) 2018-05-09 2019-11-13 Linde Aktiengesellschaft Lubricant, use of a lubricant and heat exchanger
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US20190009306A1 (en) 2019-01-10
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DK3334995T3 (en) 2021-01-18
CA2992959C (en) 2023-10-17
SA518390886B1 (en) 2021-09-08
CN107923721A (en) 2018-04-17
ES2843527T3 (en) 2021-07-19
CN107923721B (en) 2020-05-22
KR20180038537A (en) 2018-04-16
JP2018525600A (en) 2018-09-06
HUE053288T2 (en) 2021-06-28
RU2715128C2 (en) 2020-02-25
RU2018102560A (en) 2019-09-12
JP6890579B2 (en) 2021-06-18
PT3334995T (en) 2021-01-22
EP3334995A1 (en) 2018-06-20
CA2992959A1 (en) 2017-02-16
PL3334995T3 (en) 2021-04-19
WO2017025173A1 (en) 2017-02-16
US10780460B2 (en) 2020-09-22

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