EP2382424A1 - Dispositif pour le conditionnement de fluides à grande échelle - Google Patents

Dispositif pour le conditionnement de fluides à grande échelle

Info

Publication number
EP2382424A1
EP2382424A1 EP10701625A EP10701625A EP2382424A1 EP 2382424 A1 EP2382424 A1 EP 2382424A1 EP 10701625 A EP10701625 A EP 10701625A EP 10701625 A EP10701625 A EP 10701625A EP 2382424 A1 EP2382424 A1 EP 2382424A1
Authority
EP
European Patent Office
Prior art keywords
devices
container
heat exchanger
medium
conditioning
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10701625A
Other languages
German (de)
English (en)
Inventor
Frank Triesch
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.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP2382424A1 publication Critical patent/EP2382424A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/04—Air intakes for gas-turbine plants or jet-propulsion plants
    • F02C7/05—Air intakes for gas-turbine plants or jet-propulsion plants having provisions for obviating the penetration of damaging objects or particles
    • F02C7/052—Air intakes for gas-turbine plants or jet-propulsion plants having provisions for obviating the penetration of damaging objects or particles with dust-separation devices

Definitions

  • the present invention relates generally to large scale media conditioning apparatus according to the preamble of claim 1 and a system of a plurality of such apparatus.
  • the present invention also relates to devices for conditioning combustion air, which is supplied to gas turbines.
  • the combustion air of gas turbines is cleaned in so-called filter houses of solid and liquid particles in order to pressurize the working machine with the cleanest possible air.
  • filter houses of solid and liquid particles in order to pressurize the working machine with the cleanest possible air.
  • mist eliminators in such an air filter house, mist eliminators, bird screens and usually one or two filter stages are installed. Since the filters as well as the compressors of the gas turbine tend to freeze under given outside air conditions - high relative humidity and temperatures around the freezing point - the air is additionally preheated during this season.
  • heat exchangers, infrared radiators or hot air or rare exhaust manifolds are installed in a filter house, which preheat the intake air indirectly or directly.
  • Such a device 1 is shown purely schematically in Fig.
  • a high flow velocity causes a high pressure loss.
  • Unevenly inflated air filters pollute faster.
  • a small number of air filters also leads to faster pollution and a sharp increase in pressure loss.
  • Em high pressure loss in the filter house causes corresponding performance losses of the gas turbine. Possibly.
  • the polluted filters must be replaced during operation of the gas turbine under unfavorable conditions.
  • a one- or two-stage air filtration leads to an increased dirt entry into the compressor of the gas turbine. This dirt settles on the compressor blades (Fouhng) and also leads to increasing performance and efficiency losses.
  • the direct cooling is possible by the evaporation or injection of water into the intake tract and the associated adiabatic cooling effect.
  • the intake air can be cooled with heat exchangers, which are acted upon by naturally or artificially cooled heat transfer media.
  • heat exchangers which are acted upon by naturally or artificially cooled heat transfer media.
  • combustion air for gas turbines hybrid.
  • the combustion air is either heated dry or moistened, or simultaneously heated and humidified with a hybrid cooler (DE 10 2004 050 182 Al). It is also known to combine these process steps in a filter house.
  • the combustion air of the gas turbine can first coarse filtered in a first filter stage, then conditioned in a hybrid cooler and then finely and finely filtered in two other filter stages.
  • the low air velocity required by the hybrid coolers to prevent gassing results in low pressure loss of the hybrid filter house despite coupling with three-stage air filtration.
  • the result is about twice as large suction surface and about three times as large filter house, as is conventional practice. This is associated with a correspondingly higher weight, which makes conversions to the new method more difficult and requires corresponding substructures.
  • Larger gas turbines would require more than 10 of the listed hybrid coolers. Difficulties arise to unite them in an air filter house. So a maximum of 3 hybrid coolers can be stacked on top of each other, without changing the statics of the radiator housing.
  • the object of the invention is therefore to provide a device for large-scale media conditioning, which largely prefabricated industrially and can be easily adapted to different applications and sites.
  • the transport and assembly costs should be kept low.
  • the device should in particular be particularly easily coupled to a system of such devices.
  • the inventive apparatus for large-scale conditioning in particular cleaning, humidification, drying, cooling, heating and / or pressure increase of liquid and / or gaseous media, has at least one conditioning device (eg filters, humidifiers, heat exchangers, dryers, etc.) and a container, which forms the housing of the device and a flow channel for the medium, so that a cross section of the container is substantially flowed through by the medium, wherein the container for the storage, transport and / or for the function of the device is self-supporting and stackable.
  • these devices for large-scale media conditioning can be stored particularly easily, transported and combined into systems, without the need for special preparations, such as trusses during transport or structural engineering precautions during storage.
  • the disadvantages of known device are eliminated, which consisted of several individual modules and had to be assembled only at the construction site.
  • the device can be prefabricated from standardized segments at the factory, transported to the construction site and there modular assembled and arranged in a very short time as desired.
  • the devices become standardizable in this way.
  • the production can be industrial.
  • the delivery times are shortened.
  • the costs are reduced.
  • the devices always have identical dimensions and a uniform attractive appearance. They can be arranged in different space-saving constellations. If necessary, individual Devices can also be quickly replaced with new ones, so that no long downtimes arise.
  • the container is formed substantially closed at least in a circumferential direction. Then, the container forms a through-flow channel for the medium in one direction, thus providing the medium itself little flow resistance. However, it may alternatively also be provided that the flow channel consciously changes direction, for example, is guided by two adjacent sides of a rectangular container. This can e.g. be advantageous if the installation of the container or the arrangement of many devices to a system of media passage in one direction is not possible.
  • the container is in terms of its length, width and height as a container, in particular according to DIN ISO 668 formed.
  • a container in particular according to DIN ISO 668 formed.
  • Such containers have been standard for many years and there is much experience in their transportation, storage and stacking. In particular, these containers are designed for heavy loads, which must necessarily carry such a container in a device for large-scale media conditioning.
  • the container with respect to its corner fittings as a container, in particular according to DIN ISO 1161, formed.
  • the advantages of the container can also be advantageously used for large-scale media conditioning, wherein the stability of the container despite providing a flow channel is still given to the extent that a self-supporting and stackable storage and transport are guaranteed.
  • one or more stiffening elements are provided in the container for protection against internal and / or external pressure, particularly many devices can be stacked on top of each other and also during transport must be less carefully with the devices um-. to be gone.
  • the stiffening elements are formed by one or more angular, in particular triangular, expiring elements, wherein in particular one side of the elements is arranged on each side of the container and the elements of adjacent sides of the container adjoin one another. This makes it particularly simple and inexpensive to achieve a particularly effective stiffening.
  • At least one heat exchanger is provided. Then the medium can be subjected to heat or heat can be removed. Furthermore, at least one secondary medium transfer device is advantageously provided. Then, for example, the heat of the medium can be delivered to a secondary medium for further use. It is preferably provided that at least one heat exchanger and / or a secondary media transformer, in particular combined are designed as hybrid heat exchanger. At the same time, the secondary media transmitter can simultaneously also assume the function of the heat exchanger by virtue of the secondary medium circulating heat / cold / energy, for which it is circulated through the secondary media transmitter and if necessary supplemented and reheated and / or cooled or regenerated.
  • the secondary medium is in mass transfer with the main medium (for example, it itself evaporates / vaporizes into the medium to be conditioned or absorbs moisture or dust or the like from the medium to be conditioned).
  • a secondary media transformer or a hybrid heat exchanger can be operated with a secondary medium, for which a secondary media circuit is formed, wherein preferably in a secondary media circuit one or more secondary media task and / or recording devices, and in particular further at least one secondary media pump and a heat exchanger, a drain and / or a make-up valve are arranged.
  • a secondary media receiving device is designed as a collecting trough and in particular provided with a walk-in cover, in particular with a grating. Then this element of the secondary fluid circuit can be integrated into the device in a particularly space-saving manner.
  • At least one mixing valve or the like advantageously a three-way valve is arranged, preferably two, in particular three three-way valves, and / or that for switching between countercurrent and direct current between the secondary medium circuit and air flow of an air conditioning a flow switch in the secondary media circuit and / / or a switch of the air flow is provided.
  • a mixing valve can be switched to internal recuperation for the secondary fluid circuit additionally in operation.
  • two three-way valves a switchover between DC and countercurrent operation between secondary medium circuit and air flow can be provided.
  • three three-way valves allow both switching and internal recuperation.
  • the three-way valves can also be provided pure flow switch.
  • the conditioning device for internal recuperation has at least one row of tubes which is connected to the wetting medium circuit of the conditioning device and / or has at least one row of tubes which is connected to a bypass in the secondary medium cycle, and / or has a separate Rekuperationsniklauf.
  • the conditioning device for internal recuperation is connected to the secondary fluid circuit of a heat exchanger whose primary fluid circuit is connected to the wetting medium circuit of the conditioning device.
  • one or more coarse protection devices are provided on the inlet side in the device, in particular for protection against large impurities which, for example, provide protection against driftwood and / or birds and / or also against special weather influences, such as rain, snow or hail.
  • At least one filter device in particular two or three filter stages arranged in series in the flow direction of the medium, in particular uniform or different filter methods (for example a combination of surface filter and adsorption filter or absorption filter alone etc.) are provided.
  • the filter device is preferably arranged in one of the surrounding walls of the container lying in the direction of flow or walls inside the container which terminate completely in the flow path.
  • the filters of the respective filter devices are expediently arranged one above the other in one or more rows, in particular in four rows.
  • one or more devices increasing the pressure of the flowing medium are arranged in the device, in particular in one of the surrounding walls of the container lying in the direction of flow or walls within the container which completely close the flow path.
  • Such devices increasing the pressure of the flowing medium may be, for example, fans, compressors and / or pumps.
  • a plurality can also be provided, e.g. instead of a big fan several small ones.
  • a device for preventing icing is also provided.
  • the conditioning devices in particular the filters of the filter devices, the heat exchangers, the secondary media transmitters and / or the hybrid heat exchangers or anti-icing devices or the pressure-increasing devices are particularly advantageously arranged in respective receptacles, which are in particular designed to additionally stiffen the container. This also improves the conditions of storage and transportation. At the same time, but also the requirement for the container in terms of Stiffness can be reduced. In other words, that the container of the device can either be made self-supporting and stackable out of itself or these properties only in interaction with the other devices of the device for large-scale media conditioning, such as. eg the conditioning device (s). It is essential, therefore, that the container of the present device according to the invention does not have to be self-supporting and stackable by itself.
  • the container may have at least one laterally arranged antechamber in which no media conditioning takes place, which is connected via at least one sealable breakthrough to a space in which the media conditioning takes place.
  • the closability ensures that media conditioning is not disturbed. This vestibule is then not flowed through by the medium, so that this part of the cross section of the container does not form a flow channel.
  • at least one vestibule has at least one riser.
  • the antechambers of stacked devices can be easily reached.
  • at least one elevator preferably arranged on a ladder, which is designed in particular to accommodate a plurality of filter elements, in particular according to the number of filter units in the filter means behind or behind each other arranged filter rows.
  • the devices can be particularly comfortable wait.
  • the filter elements of course, other elements of the device and its devices can be easily transported by the elevator.
  • the apparatus, a heat exchanger, a secondary media supply device or a hybrid heat exchanger and / or an anti-icing device can be acted upon with antifreeze in a particularly expedient manner.
  • this makes sense especially when a liquid medium is passed through the device.
  • Preference is given to devices for measuring the humidity and / or the temperature and / or the pressure and the level or conductivity and / or other quality parameters to be set of the gaseous and / or liquid medium to be conditioned and / or a secondary medium before, on and / or after provided for the individual conditioning stages.
  • At least one control or regulating and / or monitoring device in particular for cleaning, humidification, drying, cooling and / or heating or anti-icing and / or increasing the pressure of the gaseous and / or liquid medium or a secondary medium to be conditioned intended. Then the media conditioning can be regulated and monitored very easily.
  • Independent protection is claimed for a system of several devices according to the invention, wherein a plurality of devices are arranged one above the other and / or next to each other, which are preferably sealed to one another at the separation points, wherein in particular two to nine devices are stacked tower-like. By sealing, no already conditioned medium can escape from the system or unconditioned medium can enter the system.
  • the devices are at least mechanically interconnected. Alternatively, it may also be sufficient that the devices are mutually fixed in their position due to their own weight.
  • a plurality of preferably juxtaposed devices in particular tower-like stacks with devices, preferably supplemented with corresponding lower and / or upper covers or lateral walls, form a closed region around an inlet and / or outlet opening.
  • the pipelines are hydraulically connected to one another, in particular for the make-up and / or emptying of the secondary media transformers and / or hybrid heat exchangers of the individual devices via collectors.
  • the leadership of the secondary media can be uniform and thus jointly controllable.
  • the flow and return headers in particular the heat exchanger and / or hybrid heat exchanger of the individual devices are preferably hydraulically connected together in the Tichelmann system.
  • the pipes are routed from the heat generator to the heat consumer and back in the ring installation so that the sum of the lengths of the supply line and the return line is approximately the same for each heat consumer. Heat consumers with short flow have a long return line and vice versa. The point is that all heat consumers are exposed to about the same pressure losses and thus equal volume flows, i. set the same heat flows in the heat consumers, even if no control valves are used. This causes a uniform heating of more distant heat consumers.
  • control or regulating and / or monitoring devices of the individual devices with electrical current, light or media-conducting cables, preferably with bus systems, in particular electrically, optically or hydraulically connected to each other.
  • devices of a system in particular one or more, for example tower-like stack-forming devices are connected on the media side via a collector, a funnel and / or a channel at least with a respective upstream and / or downstream device.
  • one or more devices may also be provided with upstream and / or downstream devices, such as gas turbines, buildings and the like. be connected.
  • the device according to the invention and / or the system according to the invention at least one gas turbine, a fan, an air compressor, a building or similar units or devices upstream and / or downstream and the heat transfer media of the heat exchanger, hybrid heat exchanger and / or facilities to prevent icing are energized, especially with (Ab) heat or cold or electrical energy from this unit or this device or its environment act or lead energy, in particular (Ab) heat or - cold from the media stream to be conditioned in this unit or this device or its environment back.
  • the device according to the invention and / or the inventive system at least one gas turbine, a fan, an air compressor, a building or similar units or devices upstream and / or downstream and the secondary media circuits of the secondary media transformer, hybrid heat exchanger and / or Devices for preventing icing or other conditioning devices can be acted upon by substances / media or energy from this unit or this device or its surroundings or lead substances / media or energy from the media stream to be conditioned into this unit or this device or its surroundings , among other things, for its reprocessing.
  • the conditioning device for internal recuperation in at least one row of tubes by the conditioning device provides a wetting effect. is guided medium, and / or that in at least one row of pipes the secondary medium cycle via a bypass taken secondary medium is performed, and / or separate secondary medium is guided in a separate Rekuperations- medium circulation, and / or a secondary medium is guided, which is removed from a heat exchanger, whose primary circuit is operated with the wetting medium of the conditioning as the primary medium.
  • This preferred embodiment can also be used advantageously in a countercurrent operation.
  • hybrid cooler in the hybrid cooling operation in the DC, i. to be flowed through correctly in cross-direct current.
  • it since it is an advantage of hybrid coolers that they can be operated dry below a certain outside air temperature, which saves significant amounts of cooling water over wet cooling towers, and this with countercurrent, i. is correctly more effective in cross-countercurrent, it may be advantageous to provide a possibility to switch the flow direction on the water side and / or on the air side. However, this can be superfluous if in the transitional period and in winter up to about 3 Kelvin higher cooling water outlet temperatures are required or tolerable.
  • hybrid coolers in which in addition to the cooling water cooling also the use of moist air takes place, so for example.
  • the hybrid DC mode of operation (cross / DC mode) is an option since, in addition to the higher air humidity, lower air outlet temperatures on the hybrid cooler are also achieved on an adiabatic basis. In this case, this results in lower air inlet temperatures at the gas turbine and, as a consequence, higher gas turbine outputs.
  • the internal recuperation also works in a hybrid air humidifier that is not used for cooling water cooling.
  • cooling water is circulated in direct current (cross / direct current) from the warm air inlet to the cold air outlet in the hybrid cooler bundle, the incoming warm ambient air is convectively pre-cooled.
  • the temperature level in the heat exchanger sink both on the air as well as on the cooling water and wetting water side and subsequently the air and the cooling water outlet temperature compared to a simply flowed through hybrid radiator humidifier. This increases the performance of the gas turbine in addition to a system with simply adiabatically humidified intake air.
  • cooling water is circulated in the hybrid cooler bundle in countercurrent (cross / countercurrent) from the cold air outlet to the warm air inlet, the outflowing cold ambient air is reheated convectively.
  • the temperature level in the heat exchanger rise both on the air side and on the side of the cooling water and, as a consequence, the air and the cooling water outlet temperature with respect to a hybrid radiator humidifier flowed through simply.
  • the relative humidity at the hybrid cooler outlet decreases, which may be a desirable criterion on the side which uses this air, provided that the humidity can not be influenced more easily by other criteria.
  • the wetting water of a hybrid cooler humidifier is always close to the wet bulb temperature and thus even colder than the cooling water in the hybrid cooler bundle, it may be useful to include the wetting water in the internal recuperation.
  • the wetting water is passed through at least one of the rows of tubes of the hybrid cooler, e.g. to pre-cool the incoming warm ambient air noticeably.
  • the temperature level in the heat exchanger on both the air and on the cooling water side and consequently the air and the cooling water outlet temperature decrease in comparison with a hybrid radiator with a single flow through it.
  • the wetting water is used for wetting the hybrid cooler bundle from the outside. Due to the adiabatic cooling, the wet bulb temperature in the wetting water is reached very quickly, so that the internal recuperation has a total lowering temperature.
  • wetting water on the outside of the hybrid cooler bundle is loaded with air polluting particles, it may be more appropriate to direct the wetting water through wetting water cooling water through an easy to clean heat exchanger and not directly through the hybrid cooler bundle to noticeably pre-cool the incoming warm cooling water , If the external heat exchanger becomes dirty, it can be cleaned more easily than the hybrid cooler.
  • recuperation temperature can be decoupled from the cooling water temperature and achieve a higher degree of recuperation.
  • FIG. 2 shows a device according to the invention in a front view
  • FIG. 3 shows the device according to the invention according to FIG. 2 in a first side view of the section along the axis A-A, FIG.
  • FIG. 4 shows the device according to the invention according to FIG. 2 in a second side view on the section along the axis BB
  • FIG. 5a, b shows an inventive system of devices according to the invention according to FIG. 2 in a first embodiment
  • FIG. 6a, b shows an inventive system 2
  • FIG. 8a, b shows a system according to the invention of devices according to the invention according to FIG. 2 in a fourth embodiment
  • FIG 9a, b show a system according to the invention from devices according to the invention according to FIG. 2 in a fifth embodiment
  • FIG. 10 shows a system according to the invention from devices according to the invention according to FIG. 2 in a sixth embodiment
  • Fig. 15 is a block diagram of the temperature characteristics for the embodiment of FIG. 12d and
  • FIG. 16 shows an overview of the temperature profiles for the embodiment according to FIG. 12c.
  • the device 20 is shown purely schematically in a preferred embodiment, frontally and in two side views.
  • This device 20 is a large-scale device 20 for conditioning the combustion tion of gas turbines (not shown, similar to FIG. 1).
  • the device 20 comprises a container 21, wherein the container 21 along its length in the circumferential direction with closed side walls 22, 23, 24, 25 is formed.
  • the container 21 is designed as a 40 'container 21, ie it has the essential structural details of such a container and thus also its dimensions (height 2591 mm, width 2438 mm, length 12192 mm).
  • the two side walls 26, 27 along the length of the container 21 are substantially open in such a way that they form a flow channel 28 for the combustion air (arrows indicate in all directions the direction of the flow of the combustion air), whereby the longitudinal cross-section of the Container 21 is essentially traversed by the combustion air.
  • the device 20 is flowed through in a transverse direction, whereby the filter surface advantageously increased and thus the flow resistance and the number of required devices 20 are reduced.
  • the device 20 further comprises three filter rows 31, 32, 33, and a heat exchanger 34, which is designed as a hybrid heat exchanger 34 and disposed between the first 31 and second filter row 32.
  • a rain deflector with bird screen 35 is arranged before the first filter row 31, a rain deflector with bird screen 35 is arranged.
  • a trough 36 is arranged, which is covered with a walk-in grating 37.
  • the filter rows 31, 32, 33 have a multiplicity of filter elements 38 which are arranged in suitable holding devices 39 in the filter rows in the manner of a matrix (in the present case 17 ⁇ 4 filter elements 38). By adapting these holding devices 39 and different filter makes can be used or retrofitted as desired at any time.
  • the hybrid heat exchanger 34 is used for cooling (or preheating), has a flow 34a and a return 34b and is fed with a heat transfer medium (cooling medium in the case of the present cooling) and wetting water as secondary media, wherein the wetting water through the hybrid heat exchanger 34 as in a graduation works, including corresponding water ducts (not shown) are provided.
  • the heat transfer medium is passed through substantially horizontally along the length of the container 21 extending ribbed tubes 40, which communicate with each other hydraulically. These finned tubes 40 are flown by the combustion air flow and extract heat from the combustion air or heat them up.
  • the humidified combustion air is humidified via the wetting water and cooled adiabatically in addition or with a time lag.
  • the wetting water is collected in the tub 36 and returned from there by means of a seed pump 41 in a make-up line 42 and redistributed via water distribution channels (not shown) on the hybrid heat exchanger 34.
  • a conductivity meter 43, a Abschlämmventil 44 and a make-up valve 45 are further provided, wherein spent wetting water is drained via the Abschlämmventil 44 and fresh water is replenished via the make-up valve 45 when the conductivity of the wetting water rises above a predetermined value and thus its indicating heavy pollution.
  • the make-up also takes place when the level in the water drip pan 36 has dropped due to evaporation. If there is a risk of frost, the water collecting basin 36 is emptied in the same way.
  • the pipelines (not shown) are connected to each other for emptying and feeding the individual devices 20 via collectors (not shown).
  • the device 20 has a continuous operating step 46 to allow the operator maintenance, and the vestibule 29 has at the height of the first filter row 31 each doors 47 (floor safety doors) in the bottom 24 and in the roof 22, whereby the vestibules 29 one above the other stacked devices 20 are accessible together.
  • a riser 48 is provided in the vestibule 29, on which also a lift (not shown) can be arranged.
  • the ladders 48 of stacked devices 20 serve the personnel to climb the respective level.
  • the lift can be designed so that it can be moved over the ladders 48 of stacked devices 20 across.
  • a plurality of fresh filter elements 38 can be simultaneously transported up to their destination level upwards, or polluted filter elements 38 can be lowered down at the same time, conveniently and at great speed.
  • From the vestibule 29 lead airtight doors (only schematically indicated with a cross) to the respective filter rows 31, 32, 33 before and after the hybrid heat exchanger 34.
  • the exchange of the filter elements 38 takes place by the soiled elements 38 removed from front to back and then the new elements 38 are reinstalled from back to front.
  • the hybrid heat exchanger 34 can be cleaned from the front side.
  • the space behind the hybrid heat exchanger 34 can be reached in order to clean or adjust the water distribution of the wetting water on the rear side, if necessary via the continuous operating step 46.
  • a return collector 49 and a flow collector (not shown) with the corresponding inlet and outlet nozzles for the heat transfer medium are arranged.
  • the collector 49 all Devices 20 in the flow 34a and in the return 34b connected to each other.
  • all hybrid heat exchanger 34 for the anti-icing with an antifreeze-containing heat transfer medium is applied.
  • the lubricating oil is preferably used.
  • the return 34b of the upper device 20 is recycled via a separate collector. This allows a uniform loading of all devices 20 in the Tichelmann system (known from the heating technology rule to connect all consumers on supply and return lines with the same length) and a complete ventilation of all elements of the hybrid heat exchanger 34th
  • the hybrid heat exchanger 34 additionally fulfills the function of a mist eliminator and coalescer.
  • these conditioning devices can be retrofitted to further improve the Abscheidefunktion of mist and drops even physically in the direction of passage of the combustion air after the hybrid heat exchanger 34, which in most cases, however, will not be necessary because hybrid heat exchanger 34 verifiably work without swirling.
  • the device 20 has a control box 50.
  • Differential pressure gauges (not shown) are installed for measuring the differential pressure of the individual filter rows 31, 32, 33 and possibly also of the hybrid heat exchanger 34. The degree of contamination can be deduced from the differential pressure measured values and measures for exchanging the filter elements 38 can be planned in the event of a sharp increase.
  • To measure the air temperature and the relative humidity before and after the hybrid heat exchanger 34 also corresponding measuring devices (not shown) are also installed. If the air temperature in front of the gas turbine sinks below 5 ° C., the humidification of the combustion air goes out of operation, above about 7,5 0 C back into operation.
  • the device 20 now conditions large-scale combustion air for a gas turbine, wherein the air passes through the rain deflector and the bird screen 35 and is cleaned via the first filter row 31. Thereafter, it flows through the hybrid heat exchanger 34 which supplies heat to the air by means of the cooling circuit 37 or moisturizes it via the wetting water and cools it additionally or with a time delay. The thus conditioned combustion air is again cleaned in the two successive filter rows 32, 33 and fed to the gas turbine in a suitable manner.
  • the container 21 of the device 20 is designed so that up to 9 devices 20 can be stacked on top of one another both during transport by ship and in the warehouse in the port or at the installation site.
  • the transport can be done inexpensively with standard means of transport without additional packaging overseas. That the container 21 is self-supporting and stackable, can be achieved either by the fact that the container itself is so formed, to which even special stiffening elements can be provided.
  • Ches- wise here offer triangular stiffening plates, which are almost rectangular and each having a catheter which extends parallel to the container sides 23, 25 and is connected to a container side. The much shorter catheter is connected to the long catheter of the next stiffening element, so that there is a frame-shaped stiffening, which is very easy to produce.
  • the container 21 can only reach its rigidity by virtue of the fact that the holding devices 39 for the filter elements 38, if appropriate in cooperation with the filter elements 38, additionally stiffen it.
  • the number of necessary crane strokes is reduced from four to two, wherein the devices 20 are self-supporting and therefore do not require as the hybrid radiator previously a special crossbar for their own lifting.
  • the result is a reduction in the outer dimensions of the filter container 21 in the depth of about 2.4 m and a reduction in mass in a 4O 'container with about 8.2 t, each about half compared to a separate solution, as it is known so far.
  • Such filter container 21 can be standardized in this way.
  • the production can be industrial.
  • the delivery times are shortened.
  • the costs are reduced.
  • the devices 20 always have identical dimensions and a uniform attractive appearance. They can be arranged in different space-saving constellations. If necessary, individual devices 20 can also be quickly replaced with new ones, so that no long downtimes occur.
  • a gooseneck tunnel (not shown) is arranged in the bottom 24 of the container 21 in order to further reduce the space requirement in the Vertikacht during transport of the device 20.
  • the container 21 rests as a container with the gooseneck tunnel on the truck and is thus deeper.
  • the hybrid heat exchanger 34 then stands in the middle on the gooseneck tunnel, which occupies about 3.15 m of the container length and about 1.05 m of the width and has a height of, for example, 17 cm. It may also be due to the cramped space through the Goosenecktunnel 2 wells (not shown) are arranged in front of and behind the hybrid heat exchanger 34, instead of a tub 36.
  • FIGS. 5 to 10 show purely schematically each device arranged in a special arrangement, in a plan view (with "a ”) and a side view (labeled" b ").
  • the pipes Ie again illustrate the air flow.
  • the same or similar elements are provided with the same or similar reference numerals and their function and their interaction will not be discussed again.
  • FIGS. 5 a and 5 b A first preferred embodiment of the system 100 according to the invention is shown purely schematically in FIGS. 5 a and 5 b as an arrangement of three stacks 101, 102, 103, the stacks 101, 102, 103 each comprising three devices 20. These stacks 101, 102, 103 are arranged in a hoof-shaped manner around a wall 104 which has a passage passage 105 for the conditioned combustion air to a gas turbine (not shown).
  • the flow path to the passage opening 105 of all devices 20 is substantially equal
  • an intake manifold 106 is further provided for the combustion air
  • one opening 107 sealed in the passage opening 105 opens and the other opening 108 is approximately in the middle of the horseshoe enclosed space, as the drawn circle indicates.
  • the intake manifold 106 is disposed at the level of the middle plane of the devices 20, as is apparent from Fig. 5b.
  • the space between the devices 20 is bounded upwardly by a metal sheet or the like (not shown) and downwardly from the bottom 109 airtight. It can be seen, moreover, that the devices 20 are arranged with their anterooms 29 one above the other and in the same direction.
  • this system 100 has a footprint of approximately 250 m 2 and a lateral perspective expansion surface of approximately 116 m 2 .
  • the airtightness of the devices 20 with each other is easy to produce, for example, by the interposition of a sealing strip (not shown) when stacked. Such a sealing strip also ensures the airtightness to the bottom 109 and the wall 104 and towards the cover plate.
  • the individual devices 20 can be lashed to one another and to the environment by means of tension straps. To be customized, depending on the installation arrangement, only the air duct at the back of the devices 20 to the intake manifold 106 of the gas turbine.
  • the devices 20 are completely pre-assembled and can be put into operation for connection with each other after a few simple steps. Neither ladders nor operating platforms are to be retrofitted on site.
  • a second preferred embodiment of the system 110 according to the invention is shown purely schematically in FIG. 6 a and FIG. 6 b as a first plate-shaped arrangement of three stacks 101, 102, 103, wherein the stacks 101, 102, 103 each again comprise three devices 20.
  • the arrangement encloses a substantially semicircular space, so that the intake manifold 106 with the passage opening 105 of the wall 104 can complete.
  • this system 1 10 has a footprint of approximately 375 m 2 and a lateral perspective expanse area of approximately 107 m 2 .
  • a third preferred embodiment of the system 120 according to the invention is shown purely schematically in FIGS.
  • this system 120 therefore has a footprint of approximately 293 m 2 and a lateral perspective expanse area of approximately 98 m 2 .
  • a fourth preferred embodiment of the system 130 according to the invention is shown purely schematically in FIGS.
  • this system 130 has a footprint of approximately 214 m 2 and a lateral perspective expansion surface of approximately 82 m 2 .
  • FIG. 9a and 9b a fifth preferred embodiment of the inventive system 140 in Figures 9a and 9b is shown purely schematically as a funnel-shaped arrangement with a stack 102 ", the stack 102" comprising eight devices 20 to almost compensate for the missing side stacks.
  • four funnel surfaces 141, 142 are provided which are formed of a thin sheet of stiffening ribs and sealingly extend from the front opening 108 of the suction nozzle 106 to the side surfaces of the stack 102 ", but the antechambers 29 do not interfere with the forming funnel
  • the arrangement also encloses a substantially semicircular space
  • this system 140 has a footprint of approximately 96 m 2 and a lateral perspective extension area of approximately 164 m 2 .
  • a fan wall of many smaller individual fans could be provided in the device 20, which are then arranged, for example, in the filter element receptacles 39.
  • the combustion air can be additionally compressed, so that there is an increase in pressure.
  • the resulting device can also be used specifically as a conditioner for the heat transfer medium of the hybrid heat exchanger 34.
  • One or preferably several such devices with such fans in the stack to one another. arranged system similar to that shown in Figures 5 to 9 would thus be able to form a very effective cooling system or a cooling tower for the heat transfer medium.
  • the systems 100, 110, 120, 130, 140 can furthermore advantageously be provided with air guiding devices 150, 151, which is shown purely schematically as in FIG. It can be seen that the devices 20 have downstream air guiding devices 150, 151 in the direction of air flow.
  • These louvers 150, 151 are also formed as a 40 'container and have a frame-like structure with circumferential flanges 152, only walls 153 are provided where no air should enter or exit. Via the missing walls, openings 154 are formed, via which the louvers 150, 151 communicate with one another.
  • In the final louvers 151 one or more air outlet openings 155 are provided, through which the air (indicated by the arrows) of a gas turbine (not shown) is supplied.
  • means (not shown) for smoothing the air flow may be provided in the interior of the louvers 150, 151, so that, for example, no cornering can result in air stagnation. These means can be realized for example by curved sheets.
  • the spoilers 150, 151 are also designed to be self-supporting and stackable due to their container container.
  • the louvers 150, 151 are particularly easy to each other, with the devices 20 and with other facilities, such as channels and Wetterhutzen coupled, in turn, sealing means can be interposed .
  • silencers may be provided in the air duct in one or more air guiding devices 150, 151, wherein these silencers may advantageously also be provided directly in or on the device 20.
  • FIGS. 11a to 11g, 12a to 12e, 13a to 13d and 14a to 14d four different preferred embodiments of air conditioning devices 200, 220, 240, 260 are shown purely schematically in different operating modes, all of which are advantageously used in the device 20 according to the invention can be.
  • the same elements are denoted by the same reference numerals and their function is explained below uniformly.
  • the air conditioning device 200, 200 ' accordinging to the first preferred embodiment of FIG. 1 Ia to 1 Ie has a hybrid cooler 201 and a heat exchanger 202, wherein through the hybrid cooler 201, an air flow 203 is passed, which is to be conditioned.
  • the heat exchanger 202 is connected to a primary fluid circuit 204 and the secondary fluid circuit 205 circulates between hybrid radiator 201 and heat exchanger 202.
  • a wetting agent circuit 206 is provided in the hybrid radiator 201, wherein the secondary fluid circuit 205 via the pump 207 and the wetting medium circuit. run 206 via the pump 208 are operable.
  • the air flow 203 can thus both over the
  • Secondary fluid circuit 205 a dry cooling / dry preheating and be subjected to wet cooling via the wetting medium circuit 206.
  • the air conditioning device 200 is driven in a hybrid cooling mode (combined wet and dry cooling) in countercurrent flow between secondary medium circuit 205 and air flow 203.
  • the air conditioning device 200 is driven in the cocurrent between secondary medium circuit 205 and air flow 203 in hybrid cooling mode (combined wet and dry cooling).
  • hybrid cooling mode combined wet and dry cooling
  • the pump 207 of the secondary fluid circuit 205 with respect to the hybrid cooler 201 is arranged in opposite directions.
  • the air conditioning device 200 is driven in dry cooling mode (excluding dry cooling without wet cooling) in countercurrent between secondary medium circuit 205 and air flow 203.
  • the pump 208 of the wetting medium circuit 206 is out of operation.
  • the air conditioning device 200 is driven in the wetting mode (exclusive wet cooling).
  • the pump 207 of the secondary medium cycle is out of operation and also the primary circuit of the heat exchanger 202 is not in operation.
  • the air conditioning device 200 In the fifth operating mode according to FIG. He, the air conditioning device 200 'is moved in the DC mode between secondary medium circuit 205 and air flow 203 in the hybrid cooling mode, as in the second operating mode according to FIG. In addition, an independent Rekuperationsnikank 209 is provided, which is operated by means of the pump 210. This will further increase performance. Here, therefore, the rows of tubes of the Rekeperationsmedien Vietnamese- run 209 are performed separately from the remaining rows of tubes of the hybrid cooler 201. In the sixth operating mode according to Fig. Hf, the air conditioning device 200 "is moved in the double cooling mode between secondary medium circuit 205 and air flow 203 as in the second operating mode according to Fig. Ib In addition, it is provided that the wetting agent from the wetting agent circuit 206 before wetting is used over the rows of tubes 21 1 is performed, which are separated from the remaining rows of tubes of the secondary fluid circuit 205th
  • the air conditioning device 200 is driven in cocurrent cooling mode between secondary fluid circuit 205 and air flow 203.
  • the wetting agent may be expelled from the wetting agent circuit 206 before used for wetting is passed through a further heat exchanger 212 and there releases its heat to the secondary medium of the secondary medium circuit 205 in countercurrent.
  • the air conditioning device 220, 220 'according to the second preferred embodiment according to FIGS. 12 a to 12 e additionally has a three-way valve 221 which provides a bypass flow 222 in the secondary media circuit 205.
  • the air conditioning device 220 is driven in countercurrent between secondary medium circuit 205 and air flow 203 in the hybrid cooling mode.
  • cooled secondary medium 222 is fed to the hybrid cooler 201 via the internal recuperation bypass.
  • the air conditioning device 220 is driven in the hybrid cooling mode in the DC flow between the secondary medium circuit 205 and the air flow 203.
  • cooled secondary medium 222 is fed to the hybrid cooler 201 via the internal recuperation bypass.
  • the air conditioning device 220 is driven in the wetting mode.
  • secondary medium 222 is circulated in the hybrid cooler 201 via the bypass in countercurrent to the air flow 203 for internal recuperation.
  • Fig. 12c and also below lines without flow in the respective operating mode are shown in dashed lines.
  • the air conditioning device 220 is driven in the wetting mode.
  • secondary medium 222 is circulated in the hybrid cooler 201 via the bypass in direct current to the air flow 203 for internal recuperation.
  • the air conditioning device 220 ' is moved in the DC mode between secondary medium circuit 205 and air flow 203 in the hybrid cooling mode, as in the second operating mode according to FIG. 12b.
  • cooled secondary medium 222 is fed to the hybrid cooler 201 via the bypass for internal recuperation, wherein the cooled secondary medium via two rows of tubes 223 is performed separately in the air conditioning and then mixed with the actual secondary fluid circuit 205. This additionally increases the performance.
  • the rows of tubes 223 of the Rekuperationsmedienniklaufs are not carried out separately from the other rows of tubes of the hybrid cooler 201.
  • the air conditioning device 240 additionally has a further three-way valve 241, which provides a further bypass in the secondary medium circuit 205.
  • the pump 207 of the secondary medium cycle is arranged between the heat exchanger 202 and the three-way valve 221.
  • the air conditioning device 240 In the first operating mode according to FIG. 13 a, the air conditioning device 240 is driven in countercurrent between secondary medium circuit 205 and air flow 203 in the dry cooling mode. For this purpose, the two three-way valves 221, 241 are switched to flow.
  • the air conditioning device 240 is in the co-cooling mode between secondary medium circuit 205 and air flow in the hybrid cooling mode 203 driven.
  • the two three-way valves 221, 241 act as a changeover switch for the secondary fluid circuit.
  • the air conditioning device 240 is driven in the wetting mode.
  • secondary medium 205 is circulated in countercurrent to the air flow 203 in the hybrid cooler 201 via the heat exchanger 202 for internal recuperation, wherein the primary fluid circuit of the heat exchanger 202 is out of operation.
  • the air conditioning device 240 is driven in the wetting mode.
  • secondary medium is circulated by means of acting as a switch three-way valves 221, 241 in direct current to the air flow 203 in the hybrid cooler 201 via the heat exchanger 202 for internal recuperation, wherein the primary fluid circuit is out of operation.
  • the air conditioning device 260 additionally has a third three-way valve 261 which provides a further bypass in the secondary media circuit 205.
  • the pump 207 of the secondary fluid circuit is disposed between the heat exchanger 202 and the three-way valve 221, and the bypass provided via the third three-way valve 261 has a connection between the pump 207 and the heat exchanger 202.
  • the air conditioning device 260 is driven in countercurrent between secondary medium circuit 205 and air flow 203 in the hybrid cooling mode.
  • the two three-way valves 221, 241 are switched to flow.
  • secondary media 262 is circulated in the hybrid cooler 201 via the bypass provided for internal recuperation.
  • the air conditioning device 260 is driven in the hybrid cooling mode by means of the three-way valves 221, 241 acting as a changeover switch in the DC flow between the secondary medium circuit 205 and the air flow 203. Additionally, secondary medium 262 in the hybrid cooler 201 is circulated through the internal recuperation bypass provided by the third three-way valve 261.
  • the air conditioning device 260 is driven in the wetting mode.
  • secondary medium 262 is circulated countercurrently to the air flow 203 in the hybrid radiator 201 via the internal recuperation bypass provided by the third three-way valve 261.
  • the air conditioning device 260 is driven in the wetting mode.
  • secondary medium 262 is circulated by means of acting as a changeover three-way valves 221, 241 in direct current to the air flow 203 in the hybrid cooler 201 via the means of the third three-way valve 261 provided bypass for internal recuperation.
  • FIG. 15 shows the temperature profile when the air conditioning device 220 is operated in direct current according to FIG. 12d.
  • the air of the entering into the hybrid cooler 201 air flow 203 has a temperature of about 33.3 0 C.
  • the secondary medium emerging from the hybrid cooler 201 has a temperature of about 18.4 ° C.
  • this secondary medium eg. Cooling water
  • the refrigerant flowing in the hybrid radiator 201 secondary medium heated initially under the influence of the same air flowing current 203 easily, and then in turn to cool under the influence by adiabatic cooling by means of wetting 206 18.4 0 C (upper dashed arcuate curve in Fig. 15) , Thereby, the temperature of the air flow of 33.3 0 C to about 17.2 0 C are cooled (solid line in Fig. 15).
  • the temperature of the air stream 203 can be cooled by the adiabatic cooling in the wetting operation, only to about 18.9 0 C.
  • a gas turbine can be supplied with an approximately 1.7 0 K cooler air. Although this air is almost saturated, however, this plays no role, for example, for gas turbines.
  • FIG. 16 shows the temperature profile when the air conditioning device 220 is operated countercurrently, as shown in FIG. 12c.
  • the air of the entering into the hybrid cooler 201 air flow 203 in turn has a temperature of about 33.3 0 C.
  • the light emerging from the hybrid radiator 201 secondary medium has a temperature of about 20.6 0 C.
  • this secondary medium eg. Cooling water
  • this secondary medium is fed by means of the three-way valve 221 back to the hybrid radiator 201, then is situated at the input side of the hybrid radiator also secondary medium with about 20.6 0 C (cf., upper straight dashed curve in FIG. 16).
  • the refrigerant flowing in the hybrid radiator 201 secondary medium is cooled initially under the influence of counter-current air stream 203 slightly, to then warm up again under the influence of the incoming hot air stream 203 to approximately 20.6 0 C (lower dashed arcuate curve in Fig. 16) , Thereby, the temperature of the air flow of 33.3 0 C to about 19.4 0 C are cooled (solid line in Fig. 16).
  • the temperature of the air stream 203 can be cooled by the adiabatic cooling in the wetting operation to about 18.9 0 C.
  • the temperature of the air flow 203 is warmer by about 0.5 0 K, but also dryer.
  • This air 203 may be advantageous for air conditioning and the like. Be used when high humidity and thus possible steam formation are undesirable.
  • the air conditioning device 200, 220, 240, 260 can be operated in a wide variety of ways, whereby it is optimally adaptable to given requirements.
  • the transport of the secondary medium 222; 262 can also take place by means of other means already known, for example, in particular with regulated jet pumps or separate, in particular, regulated mixing pumps (both not shown separately).
  • regulated jet pumps or separate, in particular, regulated mixing pumps (both not shown separately).
  • regulated mixing pumps both not shown separately.
  • hybrid coolers for example, otherwise wetted heat exchanger, and finned tube heat exchangers can be used before, in or after which, for example, with nozzles or perforated / porous hoses or surfaces wetting medium is applied.
  • the present invention provides apparatuses 20 for large-scale media conditioning and methods for their operation, the elements of which are optimally combined in one block, prefabricated largely industrially and easily adapted to the various applications and sites can be adjusted.
  • the invention has been described essentially with reference to the conditioning of combustion air for gas turbines, it is clear that it can be used advantageously for any type of conditioning, ie also for secondary-medium cooling alone.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

La présente invention concerne des dispositifs (20) pour le conditionnement de fluides à grande échelle et des systèmes composés de plusieurs de ces dispositifs (20), ainsi qu'un procédé de fonctionnement de ceux-ci. De manière optimale, les éléments des dispositifs (20) selon l'invention sont réunis en un bloc qui peut être préfabriqué industriellement dans une grande mesure et qui peut facilement être adapté aux différentes situations d'utilisation et aux différents sites d'installation.
EP10701625A 2009-01-26 2010-01-26 Dispositif pour le conditionnement de fluides à grande échelle Withdrawn EP2382424A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910006198 DE102009006198A1 (de) 2009-01-26 2009-01-26 Vorrichtung zur großtechnischen Medienkonditionierung
PCT/EP2010/000438 WO2010084023A1 (fr) 2009-01-26 2010-01-26 Dispositif pour le conditionnement de fluides à grande échelle

Publications (1)

Publication Number Publication Date
EP2382424A1 true EP2382424A1 (fr) 2011-11-02

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EP (1) EP2382424A1 (fr)
DE (1) DE102009006198A1 (fr)
WO (1) WO2010084023A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102010005845A1 (de) 2010-01-26 2011-07-28 Triesch, Frank, Dr. Ing., 04328 Vorrichtung zur großtechnischen Medienkonditionierung
CN111526934B (zh) * 2017-11-21 2022-02-18 瓦锡兰芬兰有限公司 将动力设备的废气洗涤器系统安装在海洋船舶中的方法和用于湿法洗涤海洋船舶中的动力设备的废气的废气洗涤器系统

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Publication number Priority date Publication date Assignee Title
DD105504A1 (fr) * 1973-02-23 1974-04-20
US4003728A (en) * 1974-10-09 1977-01-18 Eric Rath Method and apparatus for controlling the storage condition of perishable commodities in long-distance transport vehicles
DE4407806C2 (de) 1994-03-09 1996-11-21 Frank Dr Ing Triesch Anordnung zur Temperierung eines Raums
FI105591B (fi) * 1999-06-07 2000-09-15 Tamglass Ltd Oy Lasilevyjen karkaisuosastoon liittyvä ilmantuottoyksikkö ja menetelmä sen valmistamiseksi
EP1257349B1 (fr) * 2000-02-23 2008-08-13 Schlom, Leslie Echangeur thermique de refroidissement ou d'un prerefroidisseur pour le conditionnement d'air d'admission d'une turbine
DE10146954A1 (de) * 2001-09-24 2003-05-15 Rotring Engineering Gmbh Luftfiltersystem
US6546743B1 (en) * 2002-07-02 2003-04-15 Marcus Ray Sullivan Mobile cooling apparatus
DE20301652U1 (de) * 2003-02-03 2003-04-10 Tiegel, Dieter, 01454 Ullersdorf Lüftungsgerät
DE102004050182B4 (de) 2004-10-14 2009-10-22 Triesch, Frank, Dr. Ing. Verfahren zur Luftkonditionierung

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Title
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See also references of WO2010084023A1 *

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WO2010084023A1 (fr) 2010-07-29
WO2010084023A4 (fr) 2010-10-21

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