CA1130152A - Generation of steam from low temperature waste heat - Google Patents
Generation of steam from low temperature waste heatInfo
- Publication number
- CA1130152A CA1130152A CA352,512A CA352512A CA1130152A CA 1130152 A CA1130152 A CA 1130152A CA 352512 A CA352512 A CA 352512A CA 1130152 A CA1130152 A CA 1130152A
- Authority
- CA
- Canada
- Prior art keywords
- pressure
- steam
- stage
- water
- stages
- 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.)
- Expired
Links
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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
Abstract
ABSTRACT OF THE DISCLOSURE
A process for generating steam with sensible low-temper-ature waste heat wherein preheated feed water is expanded in a succession of pressure stages after picking up the sensible heat from the fluid carrying the waste heat, and the vapor generated in each stage by the expansion is saturated, compres-sed to the pressure of the next higher pressure stage and the admitted thereto, i.e. combined with the steam of this next higher stage. The system allows waste heat recovery from low temperature heat carriers where this waste heat was discarded in the past.
A process for generating steam with sensible low-temper-ature waste heat wherein preheated feed water is expanded in a succession of pressure stages after picking up the sensible heat from the fluid carrying the waste heat, and the vapor generated in each stage by the expansion is saturated, compres-sed to the pressure of the next higher pressure stage and the admitted thereto, i.e. combined with the steam of this next higher stage. The system allows waste heat recovery from low temperature heat carriers where this waste heat was discarded in the past.
Description
~3~sæ
STEAM-GE~ERATING PROCESS
SPECIFXCATION
Field of the Invention My present invention relates to a method of generating steam utilizing sensible low-temperature waste heat of a fluid~
.
Backqround of the Invention In various industrial, chemical, metallurgical and heating processes, waste heat carrying fluids at a temperature of above 150 C can be effectively subjected to waste heat recovexy, e.g.
in so-called waste heat boilers, to produce low pressure steam.
e steam can be used as process steam for a variety o* purposes and as a heat-axchange fluid for plant heating and other purpos-` es.
H~wever, when a fluid is obtained at a lower temperature level as a carrier of the waste heat, the waste heat has not been effectively recovered in mos~ instances and because this small amount of thermal energy is not readily recoverable e.g.
` because there are few consumers of such low temperature heat, the waste heat is discharged and represents an energy loss.
Experience has shown that direct use of fluids at temper-aturPs below 150C as heating sources is difficult and seldom practical.
Obviously the low temperature fluids which still contain significant sensible heat can represent a valuable energy source if this heat caln be recovered in a practical manner and i~a readily usable fashion.
~.
, - :
.. . ~ .... . , ~
~3~
.
Objects of the_Invention It is an object of the present invention to provide a steam-generating method which operates with a high d~greee of efficiency and allows recovery of low temp~ature sensible waste heat and, more specifically, is capable of producing steam at a temperature above the temperature of the waste heat fluid.
Another object of the invention is to provide a waste heat recovery system that operates with good efficiency even with low temperature waste heat carriers.
.
lo ~ummary of the Invention .
I have found that it is possible to effectively recover ~- sensible heat from a waste heat carrier, namely, a fluid at re-latively low temperature (say b~low 150C~ and yet generate . , ; steam at a temperature above that of the fluid so that the generated steam can be u~ilized in any one of numerous applic-.
ations in a plant or the like, by-heat exchange with the fluid at an elevated pressure of a feed wa~er.
`~ m ereafter, the feed water is subjected to expansion in -a succesqion of pressure stages, i.e. to flash evaporation in ~0 a number of stages in succession, at different pressure levels so that in each stage, saturated steam is generated. The sat-urated steam from each stage is then compressed to~ the pres~
~` sure of the next higher stage and fed into this stage or com-bined with the steam thereof at the higher pressure to which - the steam has been compressed~
By this process, all of the steam is eventually brought to the final desired steam pre~sure, i.e. the pressure at which the generated steam is utilized or supplied to a consumer thereoP.
STEAM-GE~ERATING PROCESS
SPECIFXCATION
Field of the Invention My present invention relates to a method of generating steam utilizing sensible low-temperature waste heat of a fluid~
.
Backqround of the Invention In various industrial, chemical, metallurgical and heating processes, waste heat carrying fluids at a temperature of above 150 C can be effectively subjected to waste heat recovexy, e.g.
in so-called waste heat boilers, to produce low pressure steam.
e steam can be used as process steam for a variety o* purposes and as a heat-axchange fluid for plant heating and other purpos-` es.
H~wever, when a fluid is obtained at a lower temperature level as a carrier of the waste heat, the waste heat has not been effectively recovered in mos~ instances and because this small amount of thermal energy is not readily recoverable e.g.
` because there are few consumers of such low temperature heat, the waste heat is discharged and represents an energy loss.
Experience has shown that direct use of fluids at temper-aturPs below 150C as heating sources is difficult and seldom practical.
Obviously the low temperature fluids which still contain significant sensible heat can represent a valuable energy source if this heat caln be recovered in a practical manner and i~a readily usable fashion.
~.
, - :
.. . ~ .... . , ~
~3~
.
Objects of the_Invention It is an object of the present invention to provide a steam-generating method which operates with a high d~greee of efficiency and allows recovery of low temp~ature sensible waste heat and, more specifically, is capable of producing steam at a temperature above the temperature of the waste heat fluid.
Another object of the invention is to provide a waste heat recovery system that operates with good efficiency even with low temperature waste heat carriers.
.
lo ~ummary of the Invention .
I have found that it is possible to effectively recover ~- sensible heat from a waste heat carrier, namely, a fluid at re-latively low temperature (say b~low 150C~ and yet generate . , ; steam at a temperature above that of the fluid so that the generated steam can be u~ilized in any one of numerous applic-.
ations in a plant or the like, by-heat exchange with the fluid at an elevated pressure of a feed wa~er.
`~ m ereafter, the feed water is subjected to expansion in -a succesqion of pressure stages, i.e. to flash evaporation in ~0 a number of stages in succession, at different pressure levels so that in each stage, saturated steam is generated. The sat-urated steam from each stage is then compressed to~ the pres~
~` sure of the next higher stage and fed into this stage or com-bined with the steam thereof at the higher pressure to which - the steam has been compressed~
By this process, all of the steam is eventually brought to the final desired steam pre~sure, i.e. the pressure at which the generated steam is utilized or supplied to a consumer thereoP.
2-"~ ', ,~
The present invention is thus based upon a reversal o~ the approach taken in the regenerative praheating of feed water for steam power installations. In such systems, steam is work ex-panded to successive pressure ]evels and condensed in contact with feed water which is to be heated whereby the latent heat of condensation is transformed into a temperature rise of the feed water. In the system of the present invention, the tem-perature of the feed water and the thermal energy stored there-in is converted to latent heat of evaporization with contribu-tion to the energy of evaporization by the transformation ofp~tential energy of the ~eed water under pressure to kinetic energy, thereby providing steam whic~ ultimately is at a higher temperature than the waste heat carrier utilized to preheat the feed water.
In the system of the present invention, the waste heat fluid continuously drops in temperature as heat is transferred to the pressurized feed water and for a given mean temperature between the upper and lower temperature during the heat transfer, heat transfer ef~iciency is found to be relatively high, i~e.there is little if any loss during the heat transfer to the feed water.
It is thus possible to recover efficiency heat from heat car-riers at temperatures below 150~C and to produce low pressure ~- steam which, as a working fluid, can be supplied to or utilized in a low pressure steam netw~rk at a given pressure and temper-ature, the latter being above th~t of the fluid.
Most e~fective utilization of the low temperature waste `-; heat provides that two or more w~te heat revovery units of the type described, operating independently of one another, are provided.
. ;.
The present invention is thus based upon a reversal o~ the approach taken in the regenerative praheating of feed water for steam power installations. In such systems, steam is work ex-panded to successive pressure ]evels and condensed in contact with feed water which is to be heated whereby the latent heat of condensation is transformed into a temperature rise of the feed water. In the system of the present invention, the tem-perature of the feed water and the thermal energy stored there-in is converted to latent heat of evaporization with contribu-tion to the energy of evaporization by the transformation ofp~tential energy of the ~eed water under pressure to kinetic energy, thereby providing steam whic~ ultimately is at a higher temperature than the waste heat carrier utilized to preheat the feed water.
In the system of the present invention, the waste heat fluid continuously drops in temperature as heat is transferred to the pressurized feed water and for a given mean temperature between the upper and lower temperature during the heat transfer, heat transfer ef~iciency is found to be relatively high, i~e.there is little if any loss during the heat transfer to the feed water.
It is thus possible to recover efficiency heat from heat car-riers at temperatures below 150~C and to produce low pressure ~- steam which, as a working fluid, can be supplied to or utilized in a low pressure steam netw~rk at a given pressure and temper-ature, the latter being above th~t of the fluid.
Most e~fective utilization of the low temperature waste `-; heat provides that two or more w~te heat revovery units of the type described, operating independently of one another, are provided.
. ;.
-3 -Nhen two or more such waste heat recovery systems are pro-vid~d, it is possible to discontinue the operation of one and even utilize it for waste heat recovery from another fluid, while the other remains effective for the recovery of waste heat from the ~irst heat carrying fluid.
The system of the present invention, aside from providing an economical and versative recovery of thermal energy, also eliminated problems with discharging the heat carrying fluid into the environment. In the past, although the thermal energy of low tem~erature fluids could not be ree~v~red efficiently, there nevertheless was a problem involved in discharging this 1uid which was usually subjected to water cooling before being releas-ed into the environment.
With the system of the present invention, however, a suf-ficient amount of heat can be extracted from the heat carrier so that it can be discharged into the atmosphere without the high expense and complexity of water cooling.
....
Another surprising ~eature, however, of the instant inven-tion is that a plant for waste heat recovery by the principles of this invention has a long useful life, because wasta heat utilization portion is separated from the portion traversed ~y the original heat-carrying fluid and wear, corrosion and main-; tenance costs are sharply limited. -According to another feature of the invention, any water which does not evaporate upon the expansion in a r spective stage is broug;~k ta an elevated pressure and a~ter further heat ~j exchange with the heat-carrying fluid is again expanded~
This process technique has been found to be sufficiently ef-fective for the use of a waste heat in the cooling ffl a pres- ;
sureless fluid~
'"' ',
The system of the present invention, aside from providing an economical and versative recovery of thermal energy, also eliminated problems with discharging the heat carrying fluid into the environment. In the past, although the thermal energy of low tem~erature fluids could not be ree~v~red efficiently, there nevertheless was a problem involved in discharging this 1uid which was usually subjected to water cooling before being releas-ed into the environment.
With the system of the present invention, however, a suf-ficient amount of heat can be extracted from the heat carrier so that it can be discharged into the atmosphere without the high expense and complexity of water cooling.
....
Another surprising ~eature, however, of the instant inven-tion is that a plant for waste heat recovery by the principles of this invention has a long useful life, because wasta heat utilization portion is separated from the portion traversed ~y the original heat-carrying fluid and wear, corrosion and main-; tenance costs are sharply limited. -According to another feature of the invention, any water which does not evaporate upon the expansion in a r spective stage is broug;~k ta an elevated pressure and a~ter further heat ~j exchange with the heat-carrying fluid is again expanded~
This process technique has been found to be sufficiently ef-fective for the use of a waste heat in the cooling ffl a pres- ;
sureless fluid~
'"' ',
-4- ~ `
~. . .-: ' .:
~,a ~f~,g Ir~
A portion of the water is circulated continuously and the amount of water is replenished by the equivalent to the amount which evaporates. The ratio between the amount of water which is evaporated to the amount which is circulated in liquid form is 1:8 for example. Preferably the pressure is so chosen that during the heat exchange no vaporization occurs and the pre-heated feed water can be recycled to the highest pressure stage.
miS eliminatès the possibility that vapor block will form along the fluid paths.
According to another feature of the invention, the water is subjected to heat exchange in at least two pressure stages with cooled fluid from another pressure stage or with uncooled fluid atah~her pressure, This process is primarily designed for fluids which are obtained under pressure. By contrast with the previously de-; scribed process, in this case the water is brought into heat `~ eæchange ~n at least two~ advantageously all, pressure stages with the heat-carrying fluid so that the waste heat directly evaporizes the water of the several stages.
In this aspect of the invention it is preferred to feed to the highest pressure stage only a quantity of water equal to the vapor generated in all of the pressure_stages-According to the invention, the steam generated in each pressure stage is compressed to the pressure of the next higher pressure sta~e. In order to keep the power required for com-pression as low as possible, the steam prior to compression is saturated. ~is can be effected in one embodiment of the in-vention by spraying water into the steam compartment of a par-ticular s~age. The sprayed water can be water at an elevated pressure in ~he system ahead of a point at which this water is subjected to multistage expansion.
~: `
~. . .-: ' .:
~,a ~f~,g Ir~
A portion of the water is circulated continuously and the amount of water is replenished by the equivalent to the amount which evaporates. The ratio between the amount of water which is evaporated to the amount which is circulated in liquid form is 1:8 for example. Preferably the pressure is so chosen that during the heat exchange no vaporization occurs and the pre-heated feed water can be recycled to the highest pressure stage.
miS eliminatès the possibility that vapor block will form along the fluid paths.
According to another feature of the invention, the water is subjected to heat exchange in at least two pressure stages with cooled fluid from another pressure stage or with uncooled fluid atah~her pressure, This process is primarily designed for fluids which are obtained under pressure. By contrast with the previously de-; scribed process, in this case the water is brought into heat `~ eæchange ~n at least two~ advantageously all, pressure stages with the heat-carrying fluid so that the waste heat directly evaporizes the water of the several stages.
In this aspect of the invention it is preferred to feed to the highest pressure stage only a quantity of water equal to the vapor generated in all of the pressure_stages-According to the invention, the steam generated in each pressure stage is compressed to the pressure of the next higher pressure sta~e. In order to keep the power required for com-pression as low as possible, the steam prior to compression is saturated. ~is can be effected in one embodiment of the in-vention by spraying water into the steam compartment of a par-ticular s~age. The sprayed water can be water at an elevated pressure in ~he system ahead of a point at which this water is subjected to multistage expansion.
~: `
- 5 ~- .
' 3~5~
-It has been found to be advantageous to compress the steam from all o~ the expansion stage's in individual compressor stages all of which are driven by a common shaft from a single motive source. For example, the turbine drive can be a gas turbine or a diesel engine. When the heat of the diesel engine, for ex-ample, is also utilized for the generation of s~eam and/or for preheating the feed water of at least one pressure stage, the efficiency of the process can be further improved.
An apparatus ~or carrying out the ma~hod o~ the present in-vention thus can comprise a plurality of expansion stages, evap-orators or boilers with the feed water being supplied to a first boiler and the latter having a steam outlet.
Advantageously, each boil~r can also be connected to the next boller below the steam compartment by a ~eed passage which ~` admits the water to tbe next boiler for expan~ion therein to a lower pressure. m e steam compartments of each boiler are con-nected through a respective compressor sta~e with the steam of the next compartment in the manner described, with all of the compressor stages being driven by a common shaft. Means is pro-vided for recovering the engine heat, e.g. by connecting the cooling water system of the engine to at least one of the boilers whereby engine cooling water is drawn from a boiler at appropri-ate pressure and temperature and the heated engine water is de- ~ -livered to a boiler at higher temperature. Furthermore, the ;
exhaust gas of t:he engine can be passed in heat exahange with feed water or steam to further increase the efficiency.
While the system of the present invention is used preferably to generate low pressure steam for any ultimate purpose, it is also applicable to other vaporization fluids and can be provided in a closed system as a heat pump operable with varying waste heat, temperature and heat consum~tion levels. -~ 6- ~
According to a first broad aspect of the present invention there is provided a method of generating steam from sensible low temperature waste heat of a carrier fluid. The method comprises the steps of heating feed water under pressure by passing it in heat exchange with the fluid. The heated feed water is expanded in a succes-sion of pressure stages to successively lower pressures thereby producing steam in each of the stages. The steam of at least each pressure stage is compressed with a pressure lower than the highest pressure stage to the pressure of the next higher pressure stage. Finally, there is provided the step of combining the compressed steam from each pressure stage at a pressure lower than the highest pressure stage with steam from the next higher pressure stage.
According to a further broad aspect of the present ~', invention there is provided an apparatus for generating steam. The apparatus comprises a plurality of pressure stages including a first high pressure stage and a last low pressure stage. Means is provided for heating a feed water under pressure in heat exchange with a waste heat carrying fluid. Means is provided for expanding the heated ; water in succession in the stages from the first stage to the last stage. A respective compressor stage is provided ` between each succeeding pair of pressure stages for com-pressing steam from each stage of lower pressure to the pressure of the next stage at higher pressure and combining .. ..
the compressed steam with the steam of the next stage of higher pressure.
~ ''' :' ~ - 6a -;" ' ; . ':.
., .
3ID~3~5;;
Brief Descri~tion of the Drawin~
The above and other objects, features and advantages of the present invention will become more readily apparent from the following de~cription, reference being made to the ac-companying drawing in which:
FIG. 1 is a diagram illustrating principles of the in-vention and from which elements not important to a discussion of these principles have been omitted;
FIG. 2 is a T - s diagram illu-strating these principles; ;, 10 FIG- 3 is a flow diagram of a best mode embodiment for carrying out the invention in practi~e; and FIG. ~ is a flow diagram representing a modification of the system of FIG. 3.
; S~ec_fic De~r3E~ on ~.
:- From FIG. 1 it will be apparent that a line 19 can deliver feed water to a boiler system in.which the water is circulated by a pump 17 and a line 18, the boiler. system comprising four boilers or evaporators 2, 3, 4, 5, each of which has a lower or sump zone receiving the water and an upper vapor zone into which the water evaporates.
These boilers are separated by valves 7, 8 and 9 which ~ -, admit the water at the pressure of one.,boiler into the boiler ,` of the next e~ansion phase. A valve 6 co~rols the feed of ::~
, the water to t:he first boiler too. ~:;
'~ ~ heat exchange 14 enables the recirculating water to be rl .
.' passed in indi.rect heat exchange with awaste heat carrying fluid : ~:
in line 15.
~7~
: :~
. ~ . . .. ..
~,. ~ , - . . - - ~. ;
.
~3~
Each of the pressure stages can be provided with a steam--saturating spray head (not shown) which can be of the type described in connection with FIG. 3 and is connected to a re-spective stage of a compressor 32 driven by a motor M.
Each low pressure stage of the compressor feeds to the next higher pressure stage and 1he low tempe~ature steam is recovered at 23.
m e feed water under pressure is delivered at l9 in an amount equal to the quantity of water converted to steam as withdrawn at 23.
The water, heated by the heat carrying fluid, is initially introduced into boiler 2 in which a portion of the water evap-or~tes. The remaining partially cooled water is delivered through valve 7 to boiler 2 from which it enters the second boiler 3 and exp~nds therein to again generate vapor. The pro-cess is continued in the remaining two boilers 4 and 5 and the cooled water is recirculated by pump 17 through the heat exchange 14, the pump 17 raising the pressure of the water to that of feedline l9 before the water enters the heat exchanger 17- Pressure stage 2 is thus at the highest pressure and pres-sure stage 5 is at the lowest pressure.
The steam withdrawn from boiler 5 is compressed to the pressure of the ~team in boiler 4 and mixed therewith in the compressor~ T~le steam mixture at this pressure is compressed ~! to the pressure of the steam from boiler 3 and so on, until the product steam is obtained at 23 at a higher pressure than pre-vails in stage 2.
m is operation will be more readily understood from a con-sideration of the T - s diagram of FIG. 2.
~.
L3~52 Water is heated in the heat exchanger 14 pxogressively from state s5 to state sl, thereby cooling the heat carrying fluid in the ideal case from the temperature Tl to a temper-ature T5.
By expansion of the water in stage 2, the state s2 is reached with the steam being compressed from the pressure d2 to the final pressure at line 23 which is dl. By further stepwase expansion of the feed water, the states s3, s4 and s5 are reach-ed with the pres~ure o~ ea~h stage being built up to that of the next stage as shown at the right-hand side of the diagram. As is also clear from this diagram, all o~ the vapor is ultimately at tha final pressure state dl at which it can be introduced into the low-pressure steam network.
To reduce the compressor load an intervening coolinç~ can be effected (see FIG. 3) in which case the pressure buildup will correspond to the sequence d4, d3', d2', dl' as illustrated in FI~. 1.
FIG. 3 shows schematically a practical and best mode embodi-ment of the invention in which parts functionally equivalent to those of FIG- 1 have been given the same reference numerals. In addition this embodiment illustrates a specific example of the invention.
FIG. 3 represents a system which can be used wherever a high pressure steam network and a low pressure steam network are available in an industrial plant, more specifically, for . :~, , .
the recovery of waste heat using feed water which is a condens-ate of the high pressure steam system. In this embodiment, therefore, the feed water picks up the waste heat from line 15 and is drawn from the condensate du~t system o~ a steam netwoxk, the waste heat being transformed in~o low pressure steam which ~-is supplied at 23 to the low pressure steam network.
' :~
- :, _9_ ... .
A in the system of FIG. 1, the pressure stages 2, 3, 4 and 5 serve to allow expansion Of E\reheated feed water to suc-cessive lower pxessures and the production of saturated steam in each stage. The saturated steam ~rom each lower stage 5, 4, 3 being compressed in a respective compressor stage 10, 11, 12 to the pressure of the next higher stage 4, 3, 2 and being fed by the respective ~ompressor theretoO An additional compressor stage 13 is provided between the expansion stages 1 and 2 and all of the compressor stages are driven by a common shaft 37.
The heated water is introduced into the first boiler 1 and expands therein and passes through valves 6, 7, ~, 9, in succession, to the other pressure stages 2 - S for expansion and vapor generation in each sta~e.
The water from boiler 5, brought to the pressure line 19 by pump 17, is passed via line 18 through the heat exchanger 14 where it is heated with the hPat-carrying fluid of line 15.
When the latter is not a condensate, condensate from either of the steam networks can be used as the feed water 19 to which pressure the recirculated water is raised by the pump 17.
The compressor 10 - 13 has its shaft 37 driven by a diesel engine ~4. A cooling water feedline 26 for the cooling system of this invention draws water at the appropriate temperature and pressure from the steam boiler 4, whereupon this water is par~ly heated and vaporized in the heat exchanger 30 to produce ~team which is fed via line 31 to the product steam line 23. The other part o~ the cooling water serves to cool the engine 24 and is returned as preheated feed water via line 25 and valve 27 to t~e boiler 3. me heat required to vaporize the water from line 26 converted to steam in line 31 is obtained from the exhaust gas discharged at 29 from the engine 24~ :
' --10--5~
Obviously the temperatuxe and ~ressure in boiler 3 will be higher than the temperature and pressure in boiler 4 $rom which the engine cooling water is dra~wn. m e heat exchanger 30 thus allows the exhaust gas heat of the engine to be recovered while the recirculation via pump 38 of the engine coolant as part of the feed water system allows engine `heat to be recovered and - converted to low pressure steam. Since the boiler 3 is at a lower pressure than the s~eam network to which line 23 is con-nected, valve 27 is an expansion valve allowing the cooling water to expand to the lower pressure.
`~` A line 20 branched from the feed water inlet 19, represe~t~
ing a condensate line as mentioned earlier, feeds a pump 21 wich forces water through the spray heads 22 in the boilers 2, 3, and 4 to saturate the heated steam therein.
In the embodiment of FIG. 4, the heat transfer to the water to be expanded in each stage differs from the heat trans- ~-fer of FIG. 3 in that separate heating coils 33 through 36 from - heat exchangers within each of t~e boilers 2 - 5 and heat-carry-ing fluid 15 is passed through these heat exchangers in series ~ ........................................................................ .
thereby being continuously cooled. The quantity of feed water ; supplied at line 19 to the first boiler 2 is equal of course to the quantity of steam delivered at 23 under standard conditions.
~` With a heating fluid whose temperature is reduced from 150C
to 80C in the apparatus of FIG. 3 with four-stage compression ~; and a stage efficiency of 0.85 and with heat transfer in the ~ o heat exchanger 14 with a mean ~emperature difference of 10 K, ~; a ratio of usable heat (measured as heat obtained upon condens-ate ~f the st:eam generated) to work o compression 8~2 is ob-tained. Wi~l à 40% efficiency of the prime mover ti.e~ 40% of ~` 30 the diesel f~lel energy is converted to useful work), l52 the contribution to the useful energy output-o~ the primary energy source is only 30%. Without heat recovery from the prime mover, this beco~.nes 33% while the generation of an equivalent amount o steam in a conventional steam boiler will require 100% of a primary energy source, i.en an equival-ent fuel.
: -
' 3~5~
-It has been found to be advantageous to compress the steam from all o~ the expansion stage's in individual compressor stages all of which are driven by a common shaft from a single motive source. For example, the turbine drive can be a gas turbine or a diesel engine. When the heat of the diesel engine, for ex-ample, is also utilized for the generation of s~eam and/or for preheating the feed water of at least one pressure stage, the efficiency of the process can be further improved.
An apparatus ~or carrying out the ma~hod o~ the present in-vention thus can comprise a plurality of expansion stages, evap-orators or boilers with the feed water being supplied to a first boiler and the latter having a steam outlet.
Advantageously, each boil~r can also be connected to the next boller below the steam compartment by a ~eed passage which ~` admits the water to tbe next boiler for expan~ion therein to a lower pressure. m e steam compartments of each boiler are con-nected through a respective compressor sta~e with the steam of the next compartment in the manner described, with all of the compressor stages being driven by a common shaft. Means is pro-vided for recovering the engine heat, e.g. by connecting the cooling water system of the engine to at least one of the boilers whereby engine cooling water is drawn from a boiler at appropri-ate pressure and temperature and the heated engine water is de- ~ -livered to a boiler at higher temperature. Furthermore, the ;
exhaust gas of t:he engine can be passed in heat exahange with feed water or steam to further increase the efficiency.
While the system of the present invention is used preferably to generate low pressure steam for any ultimate purpose, it is also applicable to other vaporization fluids and can be provided in a closed system as a heat pump operable with varying waste heat, temperature and heat consum~tion levels. -~ 6- ~
According to a first broad aspect of the present invention there is provided a method of generating steam from sensible low temperature waste heat of a carrier fluid. The method comprises the steps of heating feed water under pressure by passing it in heat exchange with the fluid. The heated feed water is expanded in a succes-sion of pressure stages to successively lower pressures thereby producing steam in each of the stages. The steam of at least each pressure stage is compressed with a pressure lower than the highest pressure stage to the pressure of the next higher pressure stage. Finally, there is provided the step of combining the compressed steam from each pressure stage at a pressure lower than the highest pressure stage with steam from the next higher pressure stage.
According to a further broad aspect of the present ~', invention there is provided an apparatus for generating steam. The apparatus comprises a plurality of pressure stages including a first high pressure stage and a last low pressure stage. Means is provided for heating a feed water under pressure in heat exchange with a waste heat carrying fluid. Means is provided for expanding the heated ; water in succession in the stages from the first stage to the last stage. A respective compressor stage is provided ` between each succeeding pair of pressure stages for com-pressing steam from each stage of lower pressure to the pressure of the next stage at higher pressure and combining .. ..
the compressed steam with the steam of the next stage of higher pressure.
~ ''' :' ~ - 6a -;" ' ; . ':.
., .
3ID~3~5;;
Brief Descri~tion of the Drawin~
The above and other objects, features and advantages of the present invention will become more readily apparent from the following de~cription, reference being made to the ac-companying drawing in which:
FIG. 1 is a diagram illustrating principles of the in-vention and from which elements not important to a discussion of these principles have been omitted;
FIG. 2 is a T - s diagram illu-strating these principles; ;, 10 FIG- 3 is a flow diagram of a best mode embodiment for carrying out the invention in practi~e; and FIG. ~ is a flow diagram representing a modification of the system of FIG. 3.
; S~ec_fic De~r3E~ on ~.
:- From FIG. 1 it will be apparent that a line 19 can deliver feed water to a boiler system in.which the water is circulated by a pump 17 and a line 18, the boiler. system comprising four boilers or evaporators 2, 3, 4, 5, each of which has a lower or sump zone receiving the water and an upper vapor zone into which the water evaporates.
These boilers are separated by valves 7, 8 and 9 which ~ -, admit the water at the pressure of one.,boiler into the boiler ,` of the next e~ansion phase. A valve 6 co~rols the feed of ::~
, the water to t:he first boiler too. ~:;
'~ ~ heat exchange 14 enables the recirculating water to be rl .
.' passed in indi.rect heat exchange with awaste heat carrying fluid : ~:
in line 15.
~7~
: :~
. ~ . . .. ..
~,. ~ , - . . - - ~. ;
.
~3~
Each of the pressure stages can be provided with a steam--saturating spray head (not shown) which can be of the type described in connection with FIG. 3 and is connected to a re-spective stage of a compressor 32 driven by a motor M.
Each low pressure stage of the compressor feeds to the next higher pressure stage and 1he low tempe~ature steam is recovered at 23.
m e feed water under pressure is delivered at l9 in an amount equal to the quantity of water converted to steam as withdrawn at 23.
The water, heated by the heat carrying fluid, is initially introduced into boiler 2 in which a portion of the water evap-or~tes. The remaining partially cooled water is delivered through valve 7 to boiler 2 from which it enters the second boiler 3 and exp~nds therein to again generate vapor. The pro-cess is continued in the remaining two boilers 4 and 5 and the cooled water is recirculated by pump 17 through the heat exchange 14, the pump 17 raising the pressure of the water to that of feedline l9 before the water enters the heat exchanger 17- Pressure stage 2 is thus at the highest pressure and pres-sure stage 5 is at the lowest pressure.
The steam withdrawn from boiler 5 is compressed to the pressure of the ~team in boiler 4 and mixed therewith in the compressor~ T~le steam mixture at this pressure is compressed ~! to the pressure of the steam from boiler 3 and so on, until the product steam is obtained at 23 at a higher pressure than pre-vails in stage 2.
m is operation will be more readily understood from a con-sideration of the T - s diagram of FIG. 2.
~.
L3~52 Water is heated in the heat exchanger 14 pxogressively from state s5 to state sl, thereby cooling the heat carrying fluid in the ideal case from the temperature Tl to a temper-ature T5.
By expansion of the water in stage 2, the state s2 is reached with the steam being compressed from the pressure d2 to the final pressure at line 23 which is dl. By further stepwase expansion of the feed water, the states s3, s4 and s5 are reach-ed with the pres~ure o~ ea~h stage being built up to that of the next stage as shown at the right-hand side of the diagram. As is also clear from this diagram, all o~ the vapor is ultimately at tha final pressure state dl at which it can be introduced into the low-pressure steam network.
To reduce the compressor load an intervening coolinç~ can be effected (see FIG. 3) in which case the pressure buildup will correspond to the sequence d4, d3', d2', dl' as illustrated in FI~. 1.
FIG. 3 shows schematically a practical and best mode embodi-ment of the invention in which parts functionally equivalent to those of FIG- 1 have been given the same reference numerals. In addition this embodiment illustrates a specific example of the invention.
FIG. 3 represents a system which can be used wherever a high pressure steam network and a low pressure steam network are available in an industrial plant, more specifically, for . :~, , .
the recovery of waste heat using feed water which is a condens-ate of the high pressure steam system. In this embodiment, therefore, the feed water picks up the waste heat from line 15 and is drawn from the condensate du~t system o~ a steam netwoxk, the waste heat being transformed in~o low pressure steam which ~-is supplied at 23 to the low pressure steam network.
' :~
- :, _9_ ... .
A in the system of FIG. 1, the pressure stages 2, 3, 4 and 5 serve to allow expansion Of E\reheated feed water to suc-cessive lower pxessures and the production of saturated steam in each stage. The saturated steam ~rom each lower stage 5, 4, 3 being compressed in a respective compressor stage 10, 11, 12 to the pressure of the next higher stage 4, 3, 2 and being fed by the respective ~ompressor theretoO An additional compressor stage 13 is provided between the expansion stages 1 and 2 and all of the compressor stages are driven by a common shaft 37.
The heated water is introduced into the first boiler 1 and expands therein and passes through valves 6, 7, ~, 9, in succession, to the other pressure stages 2 - S for expansion and vapor generation in each sta~e.
The water from boiler 5, brought to the pressure line 19 by pump 17, is passed via line 18 through the heat exchanger 14 where it is heated with the hPat-carrying fluid of line 15.
When the latter is not a condensate, condensate from either of the steam networks can be used as the feed water 19 to which pressure the recirculated water is raised by the pump 17.
The compressor 10 - 13 has its shaft 37 driven by a diesel engine ~4. A cooling water feedline 26 for the cooling system of this invention draws water at the appropriate temperature and pressure from the steam boiler 4, whereupon this water is par~ly heated and vaporized in the heat exchanger 30 to produce ~team which is fed via line 31 to the product steam line 23. The other part o~ the cooling water serves to cool the engine 24 and is returned as preheated feed water via line 25 and valve 27 to t~e boiler 3. me heat required to vaporize the water from line 26 converted to steam in line 31 is obtained from the exhaust gas discharged at 29 from the engine 24~ :
' --10--5~
Obviously the temperatuxe and ~ressure in boiler 3 will be higher than the temperature and pressure in boiler 4 $rom which the engine cooling water is dra~wn. m e heat exchanger 30 thus allows the exhaust gas heat of the engine to be recovered while the recirculation via pump 38 of the engine coolant as part of the feed water system allows engine `heat to be recovered and - converted to low pressure steam. Since the boiler 3 is at a lower pressure than the s~eam network to which line 23 is con-nected, valve 27 is an expansion valve allowing the cooling water to expand to the lower pressure.
`~` A line 20 branched from the feed water inlet 19, represe~t~
ing a condensate line as mentioned earlier, feeds a pump 21 wich forces water through the spray heads 22 in the boilers 2, 3, and 4 to saturate the heated steam therein.
In the embodiment of FIG. 4, the heat transfer to the water to be expanded in each stage differs from the heat trans- ~-fer of FIG. 3 in that separate heating coils 33 through 36 from - heat exchangers within each of t~e boilers 2 - 5 and heat-carry-ing fluid 15 is passed through these heat exchangers in series ~ ........................................................................ .
thereby being continuously cooled. The quantity of feed water ; supplied at line 19 to the first boiler 2 is equal of course to the quantity of steam delivered at 23 under standard conditions.
~` With a heating fluid whose temperature is reduced from 150C
to 80C in the apparatus of FIG. 3 with four-stage compression ~; and a stage efficiency of 0.85 and with heat transfer in the ~ o heat exchanger 14 with a mean ~emperature difference of 10 K, ~; a ratio of usable heat (measured as heat obtained upon condens-ate ~f the st:eam generated) to work o compression 8~2 is ob-tained. Wi~l à 40% efficiency of the prime mover ti.e~ 40% of ~` 30 the diesel f~lel energy is converted to useful work), l52 the contribution to the useful energy output-o~ the primary energy source is only 30%. Without heat recovery from the prime mover, this beco~.nes 33% while the generation of an equivalent amount o steam in a conventional steam boiler will require 100% of a primary energy source, i.en an equival-ent fuel.
: -
Claims (12)
1. A method of generating steam from sensible low temper-ature waste heat of a carrier fluid, comprising the steps of:
(a) heating feed water under pressure by passing it in heat exchange with said fluid;
(b) expanding the heated feed water in a succession of pressure stages to successively lower pressures thereby produc-ing steam in each of said stages;
(c) compressing the steam of at least each pressure stage with a pressure lower than the highest pressure stage to the pressure of the next higher pressure stage; and (d) combining the compressed steam from each pressure stage at a pressure lower than the highest pressure stage with steam from the next higher pressure stage.
(a) heating feed water under pressure by passing it in heat exchange with said fluid;
(b) expanding the heated feed water in a succession of pressure stages to successively lower pressures thereby produc-ing steam in each of said stages;
(c) compressing the steam of at least each pressure stage with a pressure lower than the highest pressure stage to the pressure of the next higher pressure stage; and (d) combining the compressed steam from each pressure stage at a pressure lower than the highest pressure stage with steam from the next higher pressure stage.
2. The method defined in claim 1, further comprising the step of withdrawing water from the stage of lowest pressure and pressurizing same, the pressurized water from said lowest pressure stage being heated in heat exchange with said fluid and thereafter expanded.
3. The method defined in claim 1 wherein water of at least two pressure stages is heated in heat exchange with uncooled fluid or fluid cooled in a pressure stage operating at higher pressure.
4. The method defined in claim 3 wherein a quantity of water is fed to the highest pressure stage which is equivalent at standard temperature and pressure to the quantity of steam generated.
5. The method defined in claim 1, further comprising the step of saturating the steam in at least some of said pressure stages by spraying water into same.
6. The method defined in claim 1 wherein the compression of the steam from the pressure stages is effected in respective compressor stages, said method further comprising the step of driving all of said compressor stages with a common shaft from a prime mover operated with a fuel, and recovering heat from the combustion of fuel for said prime mover and producing steam therewith.
7. An apparatus for generating steam comprising:
a plurality of pressure stages including a first high pres-sure stage and a last low pressure stage means for heating a feed water under pressure in heat exchange with a waste heat carrying fluid means for expanding said heated water in succession in said stages from the first stage to the last stage; and a respective compressor stage between each succeeding pair of pressure stages for compressing steam from each stage of lower pressure to the pressure of the next stage at higher pressure and combining the compressed steam with the steam of the next stage of higher pressure.
a plurality of pressure stages including a first high pres-sure stage and a last low pressure stage means for heating a feed water under pressure in heat exchange with a waste heat carrying fluid means for expanding said heated water in succession in said stages from the first stage to the last stage; and a respective compressor stage between each succeeding pair of pressure stages for compressing steam from each stage of lower pressure to the pressure of the next stage at higher pressure and combining the compressed steam with the steam of the next stage of higher pressure.
8. The apparatus defined in claim 7 wherein each of said pressure stages has a liquid compartment, said apparatus further comprising a respective valve connecting each liquid compart-ment of a higher pressure stage with the liquid compartment of the next lower pressure stage.
9. The apparatus defined in claim 8 wherein each of said liquid compartments is provided with a respective heat ex-changer, said fluid traversing said heat exchangers in series.
10. The apparatus defined in claim 8, further comprising a pump connected to said last pressure stage for recirculating water to said first pressure stage and pressuring the recircul-ated water, and a heat exchanger between said pump and said first pressure stage for heating said water in indirect heat exchange with said fluid.
11. The apparatus defined in claim 8 wherein said compres-sor stages are all driven by a common shaft, said apparatus further comprising a fuel-fired prime mover connected to said shaft, and means for generating steam from heat produced by the fuel of said prime mover.
12. The apparatus defined in claim 11 wherein said prime mover is a diesel engine having a water-cooling system, the last--mentioned means including means for ciruclating water from one of said pressure stages through said cooling system and back into another of said pressure stages, exhaust gas from said diesel en gine being passed in heat exchange with a portion of water from one of said pressure stages for transforming same to steam.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19792920661 DE2920661A1 (en) | 1979-05-22 | 1979-05-22 | METHOD FOR PRODUCING STEAM |
| DEP2920661.9 | 1979-05-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1130152A true CA1130152A (en) | 1982-08-24 |
Family
ID=6071385
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA352,512A Expired CA1130152A (en) | 1979-05-22 | 1980-05-22 | Generation of steam from low temperature waste heat |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US4299193A (en) |
| EP (1) | EP0019297A3 (en) |
| CA (1) | CA1130152A (en) |
| DE (1) | DE2920661A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3110520A1 (en) * | 1981-03-18 | 1982-10-07 | Ticona Polymerwerke Gmbh, 6092 Kelsterbach | METHOD FOR PRODUCING STEAM |
| JPS5968504A (en) * | 1982-10-13 | 1984-04-18 | Hitachi Ltd | Heat recovery system of gas turbine cooling medium |
| DE3240745A1 (en) * | 1982-11-04 | 1984-05-10 | Kraftwerk Union AG, 4330 Mülheim | METHOD AND SYSTEM FOR RECOVERING HYDROCARBONS FROM OIL-BASED SAND OR STONE |
| EP0114173A1 (en) * | 1983-01-25 | 1984-08-01 | Mitsui Engineering and Shipbuilding Co, Ltd. | Method of and system for utilizing thermal energy accumulator |
| CS247740B1 (en) * | 1984-04-24 | 1987-01-15 | Ivan Petrovsky | Hot water into heating and technological steam transformation circuit connection |
| WO1992014094A1 (en) * | 1991-02-08 | 1992-08-20 | Siemens Aktiengesellschaft | Process plant |
| DE10155217B4 (en) * | 2001-11-09 | 2009-04-23 | BDF IP Holdings Ltd., Vancouver | Fuel cell system and method for operating the fuel cell system |
| US9567883B2 (en) | 2015-01-15 | 2017-02-14 | Vac-Tron Equipment, Llc | System to generate pressurized air for hydro-excavation |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE529464C (en) * | 1927-02-26 | 1931-07-13 | Philipp Mueller G M B H | Process for obtaining steam, heat and distillate from boiler sludge water |
| DE955718C (en) * | 1950-12-13 | 1957-01-10 | Helmuth Speyerer Dr Ing | Method for operating a heat pump with gradual relaxation and suction |
| US3106192A (en) * | 1960-05-13 | 1963-10-08 | Schmidt Sche Heissdampf Ges | Waste heat utilization |
| FR1377275A (en) * | 1963-01-03 | 1964-11-06 | Flue gas heat recovery device for reheating the combustion air by an intermediate steam production system | |
| US3420212A (en) * | 1967-03-27 | 1969-01-07 | Steinmueller Gmbh L & C | Circuit for a regenerative preheating |
| US4024903A (en) * | 1974-05-20 | 1977-05-24 | Nippon Kokan Kabushiki Kaisha | Evaporative cooling method by natural circulation of cooling water |
| US4026352A (en) * | 1974-09-04 | 1977-05-31 | Sergei Mikhailovich Andoniev | Device for evaporative cooling of metallurgical units |
| DE2530503C2 (en) * | 1975-07-09 | 1986-06-19 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München | Heat pump system |
| FR2352247A1 (en) * | 1976-05-18 | 1977-12-16 | Cem Comp Electro Mec | METHOD AND DEVICE FOR EXCHANGING HEAT BETWEEN FLUIDS |
| US4184325A (en) * | 1976-12-10 | 1980-01-22 | Sulzer Brothers Limited | Plant and process for recovering waste heat |
| GB1591108A (en) * | 1977-01-21 | 1981-06-17 | Green & Son Ltd | Boilers |
| US4188916A (en) * | 1978-05-15 | 1980-02-19 | Deltak Corporation | Waste heat boiler for abstraction of heat energy from gaseous effluent containing corrosive chemical contaminants |
| US4282070A (en) * | 1978-05-30 | 1981-08-04 | Dan Egosi | Energy conversion method with water recovery |
-
1979
- 1979-05-22 DE DE19792920661 patent/DE2920661A1/en not_active Withdrawn
-
1980
- 1980-05-20 EP EP80102791A patent/EP0019297A3/en not_active Withdrawn
- 1980-05-21 US US06/152,033 patent/US4299193A/en not_active Expired - Lifetime
- 1980-05-22 CA CA352,512A patent/CA1130152A/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| DE2920661A1 (en) | 1980-12-04 |
| EP0019297A3 (en) | 1981-11-11 |
| EP0019297A2 (en) | 1980-11-26 |
| US4299193A (en) | 1981-11-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4461154A (en) | Method and apparatus for compressing gas | |
| EP0812378B1 (en) | Preheated injection turbine cycle | |
| KR940002718B1 (en) | Direct fired power cycle | |
| US4660511A (en) | Flue gas heat recovery system | |
| CN1123683C (en) | Gas/steam generating equipment | |
| US6964168B1 (en) | Advanced heat recovery and energy conversion systems for power generation and pollution emissions reduction, and methods of using same | |
| US4232522A (en) | Method and apparatus for utilizing waste heat from a flowing heat vehicle medium | |
| EP0952316B1 (en) | Gas turbine inlet air cooling method for combined cycle power plants | |
| US6484501B1 (en) | Method of heat transformation for generating heating media with operationally necessary temperature from partly cold and partly hot heat loss of liquid-cooled internal combustion piston engines and device for executing the method | |
| CN101978139B (en) | Generating power from medium temperature heat sources | |
| US4379734A (en) | Multistage evaporator | |
| CA1140888A (en) | Energy conversion method and system | |
| CA1081974A (en) | Plant and process for recovering waste heat | |
| US4248039A (en) | Regenerative parallel compound dual fluid heat engine | |
| US4420373A (en) | Energy conversion method and system | |
| JPH07174003A (en) | Improving method of whole generation of available energy in energy utilizer and liquid-cooled thermal power engine carrying out improving method | |
| US20020053196A1 (en) | Gas pipeline compressor stations with kalina cycles | |
| JPS63277808A (en) | Thermodynamic cycle method using mixture as working fluid | |
| GB2033017A (en) | Internal combustion engine plant | |
| JPS60184932A (en) | Power generation method | |
| US4239603A (en) | Fuel-efficient generation of ejecting steam | |
| CA1130152A (en) | Generation of steam from low temperature waste heat | |
| JPH02181002A (en) | Double flow turbine plant | |
| US6588196B1 (en) | Gas and steam turbine system | |
| US4328675A (en) | Method of recovering power in a counterpressure-steam system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |