GB2162583A - Improved cascaded power plant using low and medium temperature source fluid - Google Patents
Improved cascaded power plant using low and medium temperature source fluid Download PDFInfo
- Publication number
- GB2162583A GB2162583A GB08517887A GB8517887A GB2162583A GB 2162583 A GB2162583 A GB 2162583A GB 08517887 A GB08517887 A GB 08517887A GB 8517887 A GB8517887 A GB 8517887A GB 2162583 A GB2162583 A GB 2162583A
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- Prior art keywords
- fluid
- power plant
- operating
- vaporizer
- heat
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
- H01R12/00—Structural associations of a plurality of mutually-insulated electrical connecting elements, specially adapted for printed circuits, e.g. printed circuit boards [PCB], flat or ribbon cables, or like generally planar structures, e.g. terminal strips, terminal blocks; Coupling devices specially adapted for printed circuits, flat or ribbon cables, or like generally planar structures; Terminals specially adapted for contact with, or insertion into, printed circuits, flat or ribbon cables, or like generally planar structures
- H01R12/70—Coupling devices
- H01R12/82—Coupling devices connected with low or zero insertion force
- H01R12/85—Coupling devices connected with low or zero insertion force contact pressure producing means, contacts activated after insertion of printed circuits or like structures
- H01R12/89—Coupling devices connected with low or zero insertion force contact pressure producing means, contacts activated after insertion of printed circuits or like structures acting manually by moving connector housing parts linearly, e.g. slider
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
- H01R12/00—Structural associations of a plurality of mutually-insulated electrical connecting elements, specially adapted for printed circuits, e.g. printed circuit boards [PCB], flat or ribbon cables, or like generally planar structures, e.g. terminal strips, terminal blocks; Coupling devices specially adapted for printed circuits, flat or ribbon cables, or like generally planar structures; Terminals specially adapted for contact with, or insertion into, printed circuits, flat or ribbon cables, or like generally planar structures
- H01R12/70—Coupling devices
- H01R12/71—Coupling devices for rigid printing circuits or like structures
- H01R12/72—Coupling devices for rigid printing circuits or like structures coupling with the edge of the rigid printed circuits or like structures
- H01R12/721—Coupling devices for rigid printing circuits or like structures coupling with the edge of the rigid printed circuits or like structures cooperating directly with the edge of the rigid printed circuits
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- Engine Equipment That Uses Special Cycles (AREA)
Abstract
A plurality of independent, closed Rankine cycle power plants, (12A, 12B, 12C) having respective vaporizers (13A, 13B, 13C), are powered from heat in a medium or low temperature fluid e.g. geothermal fluid or liquid waste which flows serially through the vaporizers and then to respective preheaters (19A, 19B, 19C) of the power plants, which are connected in parallel. The fluid heats the plants' working fluid to the evaporization temperature, in the pre heaters and supplies the latent heat of vaporization to the working fluid in the vaporizers. As compared to a conventional cascaded power plant, the temperature drop of the fluid can be increased without reducing the efficiency. Alternatively, the temperature drop can be maintained but the efficiency can be increased. In either case, the power produced by the power plant increased. <IMAGE>
Description
SPECIFICATION
Improved cascaded power plant using low and medium temperature source fluid
This invention relates to an improved cascaded power plant using low and medium temperature source fluid.
Low and medium temperature source fluids, hereinafter termed source fluids of the type described, are those fluids with a temperature wests than about 350"F, such as geothermal fluids obtained from many production wells, and industrial liquids produced by various industrial processes. The East Mesa Development Project located in the Imperial Valley of Southern California near Holtville presently has six wells capable of producing about 4 million pounds per hour of geothermal fluid at about 324"F. Such geothermal fluid is an example of source fluid of the type described.
Conventionally, electricity is produced from source fluids of the type described using a closed
Rankine cycle heat engine of which the operating fluid is an organic fluid (e.g. Freon), such system being termed a power plant of the type described. A source fluid of the type described is applied to a vaporizer of a power plant of the type described containing liquid organic fluid whereby the latter is converted into a vapour. The vapour is expanded in a turbo-generator which converts some of the heat in the vapour to work and produces heat depleted organic vapour which is condensed in a condenser.
The condensed organic fluid is returned to the vaporizer, and the cycle repeats.
The condenser rejects the remaining heat in the heat depleted vapour into ambient air, if an air cooled condenser is involved, or into cooling water, if a water cooled condenser is used. Typically, the vaporizer is operated at a pressure which produces saturated or only slightly superheated vapour because the pressures involved are relatively low and the design of the heat exchanger which constitutes the vaporizer, the piping for conveying the vapour, and the turbine, are simplified. In order to maximize power output of a power plant of the type described, the temperature drop of the source fluid across the entire heat exchanger system of the power plant, and the evaporization temperature in the vaporizer must be optimized.
The conventional cascaded power plant utilizes a plurality of closed Rankine cycle power plant modules each having an associated heat exchanger, the source fluid being serially applied to the heat exchangers of each module. Whatever system is used, maximizing the net power produced by the system is of paramount importance. One technique for increasing the power is to extract more heat from the source fluid by increasing its temperature drop. With either a single stage or cascaded system, however, increasing the amount of heat extracted from the source fluid by increasing the temperature drop of the source fluid across the heat exchanger system has the effect of decreasing the efficiency of the power plant because the mean temperature of the source fluid is reduced.This results in a reduction of the evaporization temperature of the operating fluid in the heat exchanger, thus reducing the Carnot efficiency of the power plant.
In an effort to increase the efficiency of a power plant of the type described, and to extract more power from the source fluid, it has been proposed to operate at super critical temperatures and pressures. In each case, the temperature of the vaporized organic fluid produced bathe heat exchanger system is higher than in the abovedescribed typical Rankine cycle power plant. While this approach is effective to increase the efficiency of the power plant and to increase its work output, the gains are offset by the higher cycle pump power consumption, as well as increased cost and complexity of the power plant of which the pressure vessels must be designed to operate at pressures in the range of 500--600 psia.
It is therefore the general object of the present invention to provide a new and improved power plant of the type described which can be operated more efficiently than a conventional low pressure power plant.
The brief invention provides a method for operating a plurality of independent, closed Rankine cycle power plant modules, each of which has a vaporizer, comprising the steps of serially applying a medium or low temperature source fluid to the vaporizers of the power plants for producing heat depleted source fluid, providing a preheater for each vaporizer, and applying said heat depleted source fluid to all of the preheaters in parallel. The heat depleted source fluid thus serves to heat the operating fluid to the evaporization temperature, while the source fluid applied to the vaporizers supplies the latent heat of vaporization to the operating fluid of the power plant.
The present invention is advantageous, as.
compared to a conventional cascaded power plant of the type described, because the temperature drop of the source fluid can be increased without reducing the efficiency. Alternatively, the temperature drop can be maintained but the efficiency can be increased. In either case, the power produced by the power plant according to the present invention is increased.
An embodiment of the present invention is shown in the accompanying drawings wherein:
Fig. 1 is a graph of temperature versus heat input for a heat exchanger in a power plant of the type described showing the relationship between the temperature drop of the source fluid and the evaporization temperature of the operating fluid;
Fig. 2 is block diagram of a cascaded power plant according to the present invention;
Fig. 3 is a graph similar to Fig. 1 showing the temperatures at various locations in the block diagram of Fig. 2; and
Fig. 4 is a graph similar to Fig. 3 for a conventionally cascaded power plant having the same heat exchanger area as the power plant of which the operation is shown in Fig. 3.
Fig. 5 is a second embodiment of a cascaded power plant according to the present invention showing a plurality of modular energy converters arranged in multiple levels.
The problem with the prior art, which is solved by the present invention, is illustrated in Fig. 1 to which
reference is now made. The graph shows the
variation in temperature of source fluid as a function
of the rate of heat applied to a heat exchanger in a
single-stage power plant of the type described.
Curve A represents the cooling of source fluid in a
heat exchanger from temperature tn at the
entrance to the heat exchanger, to temperature Tout,
at the outlet of the heat exchanger, where TinTouti = Del T1. In a known way, the
evaporization temperature Tevapi of the operating
fluid, the variation of which is indicated by curve B,
is determined by the temperature of the operating
fluid entering the heat exchanger. Tcond, and Del T1.
The ratio a/b, is termed the percentage of preheat
for the heat exchanger, which is the ratio of the
amount of heat per unit time required to raise the
operating fluid from the condenser temperature to
the vaporization point (remaining in liquid form), to
the total amount of heat per unit time required to
evaporate the operating fluid. For source fluids of
the type described, this ratio may range from 25% to
55%.
The difference between temperature Tppi of the
source fluid at the break-point of curve B, and Tevap is
termed the pinch-point temperature; and this
temperature is conventionally in the range F12 F.
It can be shown that reducing the pinch-point
temperature to increase the evaporation
temperature has the effect of increasing the
efficiency of the system, because the Carnot
efficiency is proportional to the ratio of the
difference between the evaporation and the
condenser temperatures to the evaporization
temperature in absolute units. However, it can be
shown that increasing the Carnot efficiency in this
manner will occur at the expense of a
disproportionately large increase in surface area of
the heat exchanger.
To increase the power output of a power plant
using an operating fluid according to curve B and a
source fluid cooled according to curve A, increasing
the temperature drop of the source fluid may be
appropriate. In such case, the source fluid is cooled
according to curve C from Tin to Tout; and the
operating fluid will then be described by curve D.
That is to say, TeVap2 will be lower than Tevapi.
Moreover, it can be shown that while the heat
extracted from the source fluid increases as the
cooling of the source fluid increases, the efficiency
of the system will decrease. Whether the power
output increases will depend upon the rate at which
cooling of the source fluid occurs in the heat
exchanger. The problem of increasing the power
output is addressed and solved by the present
invention.
Referring now to Fig. 2, there is shown a power
plant 10 according to the present invention. This
power plant 10 comprises a plurality of independent
closed, Rankine cycle organic fluid power plant
modules 1 2A, 12B and 1 2C. Three such power plant
modules are shown, but the invention is applicable
to two or more independent power plant modules.
Each of these modules is identical and as a consequence, only the module 12A is described in detail. This module includes a vaporizer 13A containing an organic liquid, and to which a low or medium temperature source fluid from source 11 is applied via an inlet 14A. The organic liquid contained within the vaporizer 13A is vaporized to produce essentially saturated or slightly superheated vapour which is applied to a turbine 1 6A of a turbo-generator 15A. The vapour expands in the turbine 1 6A, and some of the heat of the vapour is converted into work as a generator 17A produces electrical power. The vapour exhausted from the turbine 16A is applied to a condenser 18A wherein the vapour is condensed into liquid by the application to the condenser of cooling water.
Alternatively, an air cooled condenser can be used.
By means of a pump (not shown), condensate from the condenser 18A is transferred into a preheater 1 9A which may be a physical part of, or separate from the vaporizer 13A. Heat depleted source fluid, obtained from the outlet from the vaporizer of the third module, is applied to the preheater 19A at an inlet 20A to the preheater, and the cooled source fluid is transferred at an outlet 21A. If the source fluid is geothermal, the cooled fluid may be transferred to a rejection well, or, if the source fluid is an industrial chemical, the cooled fluid may be transferred back to the process.
As shown in Fig. 2, the source fluid which leaves the vaporizer 1 3A at an outlet 22A is applied to an inlet 148 of a vaporizer 13B of the power plant module 12B; and the source fluid which leaves the vaporizer 13B at an outlet 22B is applied to an inlet 14C of a vaporizer 13C of the module 12C. The source fluid which leaves the vaporizer 1 3C at 22C is, hereinafter, termed heat-depleted source fluid because of the heat extracted in each of the vaporizers 13A, 13B and 13C. This heat depleted fluid is applied to each of the preheaters 19A, 19B and 19C, in parallel.That is to say, the present invention provides for serially applying a low or medium temperature source fluid from the source 11 to the vaporizers 13A, 138 and 13C of the power plants, 12A, 12B, for producing heat-depleted source fluid which appears at the outlet 22C of the vaporizer 13C; and, the heat-depleted source fluid is applied to each preheater 19A, 19B, and 19C in parallel. The source fluid which leaves the preheaters is conveyed to a rejection well if the source fluid is geothermal.
Fig. 3 shows a typical temperature-heat diagram for a power plant similar to that shown in Fig. 2
capable of operating with geothermal fluid
produced by the East Mesa Field described above.
The values of temperature and flow rates are based
on the current capability of the East Mesa Field and
are for the purpose of comparing the power
produced by a power plant according to the present
invention and a conventional cascaded power plant
using heat exchangers with the same total area.
Approximately 3.7 million pounds per hour of
geothermal fluid is available for serial input to the vaporizers 13A, 13B and 13C; about half of the heat
depleted geothermal fluid which leaves the vaporizer 13C is applied to the preheater 19A, about 5 is applied to the preheater 19B, and the balance to the preheater 19C. It is assumed that the condenser conditions are such that the temperature of the organic fluid which leaves the condenser of each module of the power plant is 1OOaF, that the temperature of the heat-depleted geothermal fluid leaving the vaporizer 13C is 175at, and that the heatdepleted geothermal fluid is further cooled on passing through each preheater to 1 3OaF.
Geothermal fluid enters the vaporizer 13A at 324"F and is cooled by transit through the vaporizer to a temperature of 247at. The organic liquid contained within the vaporizer 1 3A is heated from 1 68aF to 268"F which is the evaporation temperature for the power plant module 12A. This provides a pinch point temperature of about 8"F. The temperature of the geothermal fluid which leaves the vaporizer 13C to 175"F and the geothermal fluid is cooled from this temperature to 1300F in each of the preheaters 19A, 19B, and 19C.Thus, for the power plant module 12A, the geothermal fluid is cooled from 175"F to 130"F while the organic liquid in the preheater is warmed from 1 OO"F to 168at.
The evaporation temperature in the power plant 128 is 203 Fwhich, of course, is less than the evaporation temperature in the power plant 12A.
Thus, the operating pressure of the power plant 12B is less than the operating pressure in the power plant 12A. Similarly, the evaporation temperature in the power plant 1 2C is 168"C which is the lowest temperature of the three power plants.
It can be shown that the overall log-mean temperature difference (LMTD) for the heat exchangers of the modules 12A, 1 2B and 12C is about 23ref, about 19at, and about 16at, respectively.
Furthermore, it can be shown that the Carnot efficiencyforthe power plant illustrated in Fig. 3 is about 18.5%. A conventional three-stage cascaded power plant having heat exchangers of substantially the same area as the power plant of Fig. 3 will have a temperature-heat diagram like that shown in Fig. 4.
In such conventional power plant, the geothermal fluid is cooled from 324"F to 1300F in one serial pass through the heat exchangers. In the three modules, the evaporation temperature will be 272"F, 178"F, and 129at, respectively. The geothermal fluid will have a temperature of 225"F entering the heat exchanger of the second module, and a temperature of 168"F entering the third module. In such case, it can be shown that the LMTD of each module of such a cascaded system is about23aF, 19at, and 17at, respectively.This establishes that the surface area of the heat exchangers in the conventional system is almost identical to the surface area of the heat exchangers of the power plant according to the present invention. However, the Carnot efficiency of the conventionally cascaded power plant is only about 16.7%. Thus, a power plant according to the present invention, with the same sized heat exchangers as in a conventional cascaded power plant will produce over 10% more power without a significant increase in cost.
A second embodiment of the invention is shown in Fig. 5 wherein a plurality of modular energy
converters like those shown in Fig. 2 are organized
so as to permit a power plant of almost any capacity to be constructed by selecting a suitable number of converters. Power plant 100 shown in Fig. 5 thus
comprises a plurality of modules arranged in a
plurality of levels. Three levels are shown in the
drawing, but both the number of levels, and the number of modules in each level are selected in accordance with the required capacity of the power
plant. Thus, as an example only, the power plant shown in Fig. 5 comprises nine modules arranged in three levels ofthree modules each.
Each module 1O1A--C in level 1, each module 102A-C in level 2, and each module 103A-C in
level 3, comprises a vaporizer, a preheater, an organic fluid turbo-generator (not shown), and a condenser (not shown) organized in the manner shown in Fig. 2. Thus, in the module 101A, for example, an organic fluid, such as Freon or the like, is heated and transferred to a vaporizer 105A where vaporization takes place. The vaporized organic fluid is piped to the turbo-generator where expansion takes place driving an electrical generator which produces power, and heat-depleted vapour which is condensed in the condenser of the module and returned to the preheater.
According to the present invention, geothermal source fluid from a well (not shown) is applied in parallel via a header 106 to each vaporizer in the level 1 modules, collected at the exit of these modules, and then applied in parallel via a header 107 to the vaporizers in the level 2 modules, etc. The heat-depleted geothermal fluid is collected in a header 108 at the outlet of the level 3 vaporizers and applied, in parallel to all of the preheaters. Thus, each column of the three vertically aligned modules shown in Fig. 5 corresponds to the arrangement shown in Fig. 2. A power plant organized like that shown in Fig. 5 is particularly useful when the source of geothermal fluid produces fluid in sufficient volume to supply multiple power plants arranged like that shown in Fig. 2.
It is believed that the advantages and improved results furnished by the method and apparatus of the present invention are apparent from the foregoing description of the preferred embodiment of the invention. Various changes and modifications may be made however within the scope of the invention as defined in the appended claims.
Claims (18)
1. A method for operating a plurality of
independent closed cycle power plant modules each
having a vaporizer comprising the steps of:
(a) serially applying a medium or low temperature source fluid of the type described to the vaporizers
of the power plants for producing heat-depleted
source fluid;
(b) providing a preheater for each vaporizer; and
(c) applying said heat-depleted source fluid to all ofthe preheaters in parallel.
2. A method according to claim 1 wherein the
source fluid is geothermal.
3. A method according to claim 1 including the step of operating the power plants at different temperatures.
4. A method according to claim 3 including the step of operating the power plants at different pressures.
5. A method according to claim 2 including the step of using an organic fluid as the operating fluid for the power plants.
6. A method according to claim 5 including using the same type of operating fluid in each module.
7. A method according to claim 1 including the steps of operating the modules on a sub-critical
Rankine cycle.
8. A power plant of the type having a plurality of independent, closed cycle power plant modules each of which has a vaporizer to which a medium or low temperature fluid is serially applied for producing heat depleted fluid, characterised by a preheater for each vaporizer, and means for applying said heat depleted fluid to all of the preheaters in parallel.
9. A method according to claim 4 wherein an organic fluid constitutes the operating fluid of the power piants.
10. A power plant according to claim 8 wherein said fluid is geothermal.
11. A power plant operating on a source of low or medium temperature fluid of the type described comprising:
(a) a plurality of closed Rankine cycle power plant modules each having a vaporizer associated therewith responsive to said source fluid for converting the operating fluid of the power plant modules to vapour;
(b) means for serially applying said source fluid to
the vaporizers of the power plants for producing
heat depleted source fluid;
(c) a preheater associated with each vaporizer for
preheating operating fluid which is vaporized in the
associated vaporizer; and
(d) means for applying said heat-depleted source fluid to all of the preheaters in parallel.
12. A power plant according to claim 11 wherein
said source is geothermal fluid.
13. A power plant according to claim 11 wherein each power plant module includes:
(a) a turbo-generator responsive to vaporized operating fluid produced by the associated vaporizer of the power plant for generating power and producing heat-depleted operating fluid; and
(b) a condenser for condensing said heat-depleted operating fluid and producing liquid condensate which is applied to the preheater associated with said associated vaporizer.
14. A geothermal power plant according to claim 13 wherein the condenser is water cooled.
15. A method according to claim 1 including the step of arranging the modules into a plurality of levels, and applying the source fluid in parallel to the vaporizers of all of the modules in a given level.
16. A power plant according to claim 11 including means for applying said source fluid in parallel to a plurality of said vaporizers which define a level.
17. A method for operating a plurality of independent, closed cycle power plant modules substantially as hereinbefore described with reference to the accompanying drawings.
18. A power plant substantially as described with reference to, and as shown in, Fig. 2 or Fig. 5 of the accompanying drawings.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US63103384A | 1984-07-16 | 1984-07-16 | |
| US06/631,058 US4578953A (en) | 1984-07-16 | 1984-07-16 | Cascaded power plant using low and medium temperature source fluid |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8517887D0 GB8517887D0 (en) | 1985-08-21 |
| GB2162583A true GB2162583A (en) | 1986-02-05 |
| GB2162583B GB2162583B (en) | 1988-05-11 |
Family
ID=27091289
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08517887A Expired GB2162583B (en) | 1984-07-16 | 1985-07-16 | Improved cascaded power plant using low and medium temperature source fluid |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2162583B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AP170A (en) * | 1989-06-12 | 1992-02-01 | Ormat Turbines 1965 Ltd | Method of and means for using a two-phase fluid for generating power in a ranking cycle power plant. |
| WO2009056341A3 (en) * | 2007-11-02 | 2010-08-12 | GMK Gesellschaft für Motoren und Kraftanlagen mbH | Device for generating power |
| CN102192118A (en) * | 2010-03-17 | 2011-09-21 | 财团法人工业技术研究院 | Stepped low-step temperature difference power generating system |
| IT201900006589A1 (en) | 2019-05-07 | 2020-11-07 | Turboden Spa | OPTIMIZED ORGANIC CASCADE RANKINE CYCLE |
| WO2021240379A1 (en) * | 2020-05-29 | 2021-12-02 | Turboden S.p.A. | Cascade organic rankine cycle plant |
-
1985
- 1985-07-16 GB GB08517887A patent/GB2162583B/en not_active Expired
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AP170A (en) * | 1989-06-12 | 1992-02-01 | Ormat Turbines 1965 Ltd | Method of and means for using a two-phase fluid for generating power in a ranking cycle power plant. |
| WO2009056341A3 (en) * | 2007-11-02 | 2010-08-12 | GMK Gesellschaft für Motoren und Kraftanlagen mbH | Device for generating power |
| EP2217793B1 (en) | 2007-11-02 | 2018-03-21 | GMK Gesellschaft für Motoren und Kraftanlagen mbH | Device for generating power |
| CN102192118A (en) * | 2010-03-17 | 2011-09-21 | 财团法人工业技术研究院 | Stepped low-step temperature difference power generating system |
| IT201900006589A1 (en) | 2019-05-07 | 2020-11-07 | Turboden Spa | OPTIMIZED ORGANIC CASCADE RANKINE CYCLE |
| WO2021240379A1 (en) * | 2020-05-29 | 2021-12-02 | Turboden S.p.A. | Cascade organic rankine cycle plant |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2162583B (en) | 1988-05-11 |
| GB8517887D0 (en) | 1985-08-21 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19960716 |