Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F22—STEAM GENERATION
  • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
  • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
  • F22B3/04—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure-reducing chambers, e.g. in accumulators
  • F22B3/045—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure-reducing chambers, e.g. in accumulators the drop in pressure being achieved by compressors, e.g. with steam jet pumps
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10S203/00—Distillation: processes, separatory
  • Y10S203/16—Combination
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10S203/00—Distillation: processes, separatory
  • Y10S203/21—Acrylic acid or ester

Definitions

• the invention relates to a process for generating steam from 3.0 to 6.0 bar and from 140 ° C to 165 ° C from liquid heat transfer media of low temperature level by evaporation and compression.
• Heat sources such as B. product streams and auxiliary materials to be cooled or product vapor vapors to be condensed are flowed through by boiler feed water in heat exchanger tubes in parallel or in succession to produce steam. Steam of various pressure levels is used partly as drive dam p f for turbines and engines, partly as heating steam. Condensates occur at different pressures and temperatures. Because the chemical plants are not continuous are driven to the design load and thus part-load operation, if not even briefly shutdown, various pressure levels are selected in the steam network, which still ensure reliable steam supply over long distances and at a sufficient temperature, ie slightly overheated.
• a medium pressure level of approx. 15 to 25 bar and a low pressure level of 3 to 6 bar there is usually a medium pressure level of approx. 15 to 25 bar and a low pressure level of 3 to 6 bar.
• Steam from the medium pressure stage can be used, among other things, as heating steam for the temperature range around 200 ° C, as motive steam for steam jet compressors or as drive steam for process steam turbines.
• Steam of the low pressure level is generally only used as heating steam. Its pressure of 3 to 6 bar and its temperature, slightly above the saturated steam temperature, still allow that. Transport and use over long distances. For some reason there is not enough low pressure steam available. Available, one is forced to reduce steam from the medium-pressure network to the pressure of the low-pressure steam network by means of throttling devices and possibly to inject condensate for steam cooling or for saturation. In this way, high-quality energy, ie steam with high thermodynamic quality, is inevitably reduced.
• the invention is based on the object of eliminating the existing disadvantages of generating steam from 3.0 to 6.0 bar in chemical process plants and at the same time bringing resulting vapor of low thermodynamic quality to a higher energy level.
• the advantages achieved by the invention are, in particular, that the heat content of liquid heat transfer medium in the temperature level down to 80 ° C for generating steam from 3.0 to 6.0 bar is achieved with simple and very effective means. A temperature increase of approx. 50 ° C is achieved. The use of drive energy and motive steam reaches a minimal value.
• the combination of mechanical and thermodynamic vapor compression is particularly flexible. With the help of an intake throttle on the mechanical compressor, its final pressure can be kept constant with changing steam quantities. This means that the suction pressure of the steam jet compressors remains constant and there is no need for additional motive steam because the pressure ratio also remains constant. As a result of overheating of the steam leaving the last stage of the mechanical compressor of approximately 25 ° C., favorable conditions result for the steam jet compressors.
• the mechanical compressor usually a multi-stage one, can have several entries, it can also be evaporated at different suction pressures, ie at different temperatures.
• the use of a multi-stage turbocompressor enables multiple steam flows, even of different pressure and temperature levels, with simple To bring medium and energy optimally to a uniform pressure and temperature level.
• this uniform pressure level for the combined amounts of steam enables the energetically optimal further compression of partial quantities by using several steam jets. Since the steam jets are operated with propellant steam of the same state and also work at the same final pressure, this solution is also advantageous from an operational point of view in terms of part-load behavior by switching individual steam lamps on or off.
• a low temperature level means a temperature range from 80 to 115 ° C., preferably from 90 to 105 ° C.
• the liquid heat transfer medium is preferably evaporated at a low temperature level and low pressure, in the case of water as heat transfer medium at a subatmospheric pressure from 0.5 bar, preferably from 0.7 bar.
• the pressure increase by means of the steam jet compressor is preferably 1.5 to 1.8 times.
• Mechanical compression should preferably be understood to mean compression by means of a multi-stage turbocompressor.
• known types of compressor such. B. screw compressor can be used.
• Thermodynamic compression means compression by means of motive steam in a steam jet compressor.
• the steam sucked in by the multi-stage mechanical compressor is gradually cooled by condensate injection.
• the liquid heat transfer medium is hot condensate, by means of vapors or other heat sources, such as. B. exhaust gases or vapors, heated feed water and / or a mixture of the two.
• Liquid heat transfer media are usually water, which means that according to the invention the steam is usually water vapor.
• the invention is not limited to water vapor, but suction steam and motive steam should be of the same basic liquid.
• the essence of the invention is not changed if a fluid other than water is selected or can be used as the heat transfer medium.
• Indirect heating medium for feed water can be any other substance with a sufficient temperature level.
• expansion steam of the same or higher pressure is added to the mechanically compressed steam.
• the flash steam is e.g. B. obtained by relaxing condensate under higher pressure. If you want to reduce the overheating of the steam from the steam jet compressors, a corresponding amount of condensate is supplied to the steam from 3.0 to 6.0 bar in a known manner.
• feed water is evaporated at a vacuum of 0.84 bar and 94 ° C.
• steam is generated from several condensate collection tanks, which are under pressures of up to 2.9 bar, by relaxing to 0.84 bar. A total of 12,500 kg / h of saturated steam are generated by vapor evaporation and expansion.
• This total steam in the amount of 12,500 kg / h is compressed by a multi-stage turbo compressor up to 2.45 bar.
• the turbocompressor is driven by a Geaer.pressure steam turbine, the exhaust steam of which is produced at 16 bar and 205 ° C.
• the steam superheated by the respective compression in the individual stages is cooled between the stages by condensate injection. This means that the drive energy is also directly converted into steam.
• This injection of condensate increases the amount of steam by a further 735 kg / h to a total of 13,235 kg / h. After the last compressor stage, the superheat of the compressed steam is 22 ° C.
• the steam jet compressors deliver a total of 32 055 kg / h of slightly superheated steam at 3.8 bar and 154 ° C. Since a slight temperature reduction is still possible in the present case, an additional 500 kg / h of condensate of 95 ° C are injected into the superheated steam and thereby converted again into steam. According to the process of the invention, a total of 32,555 kg / h of heating steam of 3.8 bar and 145 ° C, i.e. slightly overheated, won.
• the work required for the above-mentioned pressure increase of the pre-compressed steam in a total steam quantity of 14 335 kg / h is 450 kW.
• the combination according to the invention enables an advantageous utilization of waste heat from a low temperature level in connection with the thermally advantageous use of medium pressure steam.
• the combination of mechanical and thermodynamic steam compression for the production of superheated low-pressure steam proves better in terms of energy and investment than any other combination known to date.

Landscapes

• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
• Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
• Processing Of Solid Wastes (AREA)
• Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)
• Sorption Type Refrigeration Machines (AREA)

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Publications (2)

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Citations (5)

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• 1981
  • 1981-03-18 DE DE19813110520 patent/DE3110520A1/de not_active Ceased
• 1982
  • 1982-03-03 EP EP82101632A patent/EP0061031B1/fr not_active Expired
  • 1982-03-03 DE DE8282101632T patent/DE3260287D1/de not_active Expired
  • 1982-03-03 AT AT82101632T patent/ATE8174T1/de not_active IP Right Cessation
  • 1982-03-17 JP JP57040973A patent/JPS57172102A/ja active Pending
  • 1982-03-17 US US06/359,152 patent/US4438730A/en not_active Expired - Fee Related
  • 1982-03-17 ES ES510518A patent/ES510518A0/es active Granted

Patent Citations (5)

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