Technical Field
[0001] The present disclosure generally refers to power generation from waste heat and more
particularly to using an organic Rankine cycle (ORC) for converting waste heat of
multiple waste heat sources to electric power.
Background
[0002] The efficiency of generating power with, e.g., a combustion engine can be increased,
for example, by additionally generating power from waste heat of the combustion engine,
such as the heat of exhaust gas. Similarly, the generation of power from waste heat
is used in combined cycle power generation, which combines the generation of power
from steam or combustion turbines with at least one additional stage deriving power
from waste heat of the steam or combustion turbine using, e.g. an ORC.
[0003] Herein the term "combined cycle" is to be understood to include the combination of
an ORC with combustion based power generating systems, such as combustion engines,
e.g. gas or liquid fuel genset, as well as the combination of an ORC with steam or
combustion turbine based power generating systems.
[0004] To efficiently generate energy from low-temperature waste heat, ORC technology has
been developed. ORC uses a working medium that changes into gas phase at the available
temperature of the waste heat and is used to drive an ORC turbine. In general, there
are two types of ORC:
[0005] Indirect ORC uses an intermediate liquid cycle to transfer the waste heat to the
working medium, whereby the working medium circulates in a closed cycle of an ORC
unit. These types of system are referred to as closed loop ORC systems.
[0007] The present disclosure is directed, at least in part, to improving or overcoming
one or more aspects of prior systems.
[0008] A direct organic Rankine cycle system allowing a specific circulation speed control
is provided by the present invention as defined in claim 1, a corresponding method
is defined in claim 13. Further developments are given in the dependent claims.
Summary of the Disclosure
[0009] According to an aspect of the present disclosure, a direct organic Rankine cycle
system for generating power using a working medium may comprise a boiler sub-system
comprising a pump and a boiler, the pump configured to pump the working medium through
the boiler; a vapor separator connected to a working medium outlet of the boiler and
configured for separating a gaseous phase of the working medium; an organic Rankine
turbine module fluidly connected to the vapor separator, the organic Rankine turbine
module comprising a turbine driven by the separated working medium gaseous phase;
a control system configured to control the pump for adjust the circulation speed of
the working medium through the boiler such that at least 15%, 20 %, 30 %, 40 %, or
50% of the working medium are maintained in the liquid phase when exiting the boiler.
[0010] According to another aspect of the present disclosure, a biomass combined cycle power
generating system may comprise a pyrolysis reactor generating pyrolysis oil and pyrolysis
gas from biomass; a pyrolysis oil engine for generating power from the pyrolysis oil,
thereby producing waste heat; a pyrolysis gas engine for generating power from the
pyrolysis gas, thereby producing waste heat; and a direct organic rankine cycle system
(e.g. as indicated above) comprising two boiler sub-systems for generating power from
the waste heat of the pyrolysis oil engine and the pyrolysis gas engine, wherein the
waste heat is supplied to a respective boiler of the boiler sub-systems.
[0011] The control system may be connected with a temperature sensor for receiving temperature
data of the working medium and configured for receiving a load parameter of a genset,
which provides waste heat to the boiler sub-system, and wherein the control system
may be further configured for deriving a pump speed control parameter for controlling
the speed of the pump from the load parameter and the temperature parameter, in particular
using a load/temperature depending flow curve tables associated with the boiler sub-system.
[0012] In some embodiments, a boiler may be configured for heating the working medium with
waste heat of exhaust gas of a combustion and/or waste heat of a high temperature
cooling cycle of a combustion engine. The boiler may be operable as a Lamont boiler.
The boiler may comprise a super-heating system connected with a gaseous phase outlet
of the vapor separator. The super-heating system may be configured for super-heating
the separated working medium gaseous phase and providing the super-heated separated
working medium gaseous phase to the organic Rankine turbine module.
[0013] In some embodiments, the working medium may be selected from the group of organic
working media comprising saturated and unsaturated hydrocarbons, fluorated hydrocarbons,
silicon oils such as siloxane, ammonia, and ammonia-water mixture.
[0014] In some embodiments, the boiler sub-system and the vapor separator may be part of
a modular heat rejection system of the direct organic Rankine cycle system, and the
modular heat rejection system may comprise a plurality of boiler sub-systems and the
pumps of the boiler sub-systems are controlled by the control system such that at
least 15%, 20 %, 30 %, 40 %, or 50% of the working medium are maintained in the liquid
phase when exiting the respective boiler.
[0015] In some embodiments of the biomass combined cycle power generating system, the waste
heat may include at least one of heat of exhaust gas and heat of a coolant system
of the pyrolysis oil engine and at least one of heat of exhaust gas and heat of a
coolant system of the pyrolysis gas engine.
[0016] According to an aspect of the present disclosure, a method for operating a direct
Rankine cycle, the method may comprise circulating an organic working medium through
a boiler at a circulation speed such that at least 15%, 20 %, 30 %, 40 %, or 50% of
the organic working medium are maintained in the liquid phase when exiting the boiler.
[0017] The method may further comprise heating the working medium in the boiler using waste
heat such as heat of an exhaust gas or a cooling circuit of an combustion engine;
separating a working medium gas phase and a working medium liquid phase from the heated
working medium, eventually additionally super-heating the separated working medium
gas phase; deriving power from the separated working medium gas phase; regenerating
a working medium liquid phase of the working medium after power generation; and returning
a mix of the regenerated working medium liquid phase and the separated working medium
liquid phase to the boiler.
[0018] The method may further comprise receiving information on a load parameter of a genset,
which provides waste heat to the boiler sub-system; receiving temperature data of
the working medium; and deriving a pump speed control parameter from the load parameter
and the temperature parameter for controlling the circulation speed.
[0019] In general, using direct ORC systems as disclosed herein, which are based on, e.g.,
heat from the exhaust gas or a charge air cooling system of a combustion engine, may
result in a gain in efficiency of, e.g., about 10% in addition to the efficiency of
the conventional combustion engine(s) generated power.
[0020] In view of the large expense of an ORC system, combining several heat sources within
a modular concept for the heat rejection cycle of the working medium may reduce the
cost for implementing ORC based generation of power from waste heat.
[0021] In addition, various types of heat sources such as high temperature charge air cooling
systems can alternatively or additionally be used to preheat the working medium.
[0022] In view of the fact that heating the working medium directly has to be performed
in a manner that does not affect the working medium itself, e.g. causes polymerization,
a control concept is disclosed herein for controlling direct ORC. The control concept
may avoid or at least reduce the amount of overheating of the working medium and,
thereby, provide long term use of the working medium.
[0023] Other features and aspects of this disclosure will be apparent from the following
description and the accompanying drawings.
Brief Description of the Drawings
[0024]
Fig. 1 is a schematic overview of a combined system including a direct ORC system
using the waste heat of three gensets;
Fig. 2 is a schematic overview of a combined system for a pyrolysis-based power plant
including a direct ORC system using waste heat from a gas genset and a liquid genset;
Fig. 3 is a schematic illustration of a direct ORC system with a modular heat rejection
system and an ORC turbine module;
Fig. 4 is a schematic diagram illustrating a direct ORC system with a modular heat
rejection system comprising three heat rejection modules;
Fig. 5 is a schematic illustration of a direct ORC system including a super-heating
zone;
Fig. 6 is a schematic illustration of a direct ORC system including pre-heating of
a working medium before being supplied to the modular heat rejection system and a
super-heating zone; and
Fig. 7 is a schematic illustration of an air system and a cooling system of a genset.
Detailed Description
[0025] The following is a detailed description of exemplary embodiments of the present disclosure.
The exemplary embodiments described therein and illustrated in the drawings are intended
to teach the principles of the present disclosure, enabling those of ordinary skill
in the art to implement and use the present disclosure in many different environments
and for many different applications. Therefore, the exemplary embodiments are not
intended to be, and should not be considered as, a limiting description of the scope
of patent protection. Rather, the scope of patent protection shall be defined by the
appended claims.
[0026] The present disclosure may be based in part on the realization that to increase the
efficiency of a power plant, e.g. a biomass based power plant, the waste heat of various
gensets or various types of waste heat of one or more genset may be turned into electric
power via a common organic Rankine cycle.
[0027] Combining multiple waste heat sources via a modular heat rejection cycle as disclosed
herein may be based on a common vapor separator and a common ORC turbine module with
a turbine and a regenerator.
[0028] The common vapor separator may be connectable to the common ORC turbine module to
provide the gas phase of the working medium to the turbine and to receive the working
medium after regeneration of the working medium with the regenerator of the ORC turbine
module.
[0029] To allow using heat of a plurality of waste heat sources, the common vapor separator
may be configured such that a plurality of parallel heat rejection cycles share the
common vapor separator. For example, each heat rejection cycle may comprise its own
pump and boiler and provide a heating cycle that begins and ends at the common vapor
separator. As each heat rejection cycle may have its own pump, the flow within the
heat rejection cycles may be adjusted as described herein for protecting the working
medium.
[0030] For example, to avoid overheating and, thereby, decomposing of the working medium,
a control concept as described herein may adjust the circulation rate within the heat
rejection cycle to a value of 1.3 to 1.5. Thereby, a value of 1.0 is defined as a
circulation rate that results in heating the working medium such that 100% of the
working medium changes into the gas phase, i.e. the complete amount of working medium
that passes through a boiler is evaporated. Accordingly, a value above 1.0 indicates
that more working medium is circulated. As an example, for a value of 1.30, 130 %
of the amount of working medium, which correspond to the value of 1.00, are circulated.
This corresponds to operating the heat rejection cycles under the Lamont principle.
For example, the boiler may be considered to be operated as a Lamont boiler.
[0031] As an example, the control strategy as described herein may operate the heat rejection
cycles under the condition that at least 30% of the working medium that passes through
a boiler is maintained in the liquid phase. Then, an energy buffer may be provided
in form of the not yet evaporated working medium such that in case the temperature
is further increased the liquid phase can receive that energy.
[0032] Specifically, the control concept may control the pump speed within the heat rejection
cycles to a value that may provide a time of the working medium within the heat rejection
cycle that results in a preset ratio of the fluid and gas phase of the working medium
at the exit of the boiler.
[0033] In the following and with reference to Figs. 1 to 7, various embodiments of direct
ORC systems and their implementation in combined power generating systems are disclosed.
[0034] As illustrated in Fig. 1, multiple gensets 10 may provide waste heat to a direct
ORC system 20. Specifically, a single genset 10 may provide different types of waste
heat to direct ORC system 20 such as heat of exhaust gas, heat of a coolant of a charge-air
cooling system, e.g. a high-temperature charge-air coolant cycle and/or a low-temperature
charge-air coolant cycle, and heat of jacket water.
[0035] While in principle for a fuel combustion engine, as an example of gensets 10, about
50% of the energy input in form of fuel may be transferred into mechanical output,
using waste heat, e.g., of the exhaust gas and/or the charge-air coolant system for
a secondary power generation based on an ORC system may result in an increase of e.g.
additional 10% of the engine generated power, i.e. in this example additional 5 %
of the energy input may be transferred into electricity.
[0036] The general concept of applying ORC to multiple gensets 10 is described in the following
in connection with Fig.2.
[0037] Fig. 2 shows a flow chart for a pyrolysis-based power plant 100 as an example of
a power system using biomass integrated liquidation. Pyrolysis-based power plant 100
may be adapted to include an ORC system using waste heat.
[0038] Pyrolysis-based power plant 100 may include a pyrolysis reactor 110 that is provided
with biomass 111 such as wood or agricultural waste (e.g. stalks of wheat or corn,
grass, wood, wood shavings, grapes, and sugar cane). Using, for example, flash-pyrolysis,
pyrolysis reactor 110 may generate pyrolysis gas 112A, pyrolysis oil 112B, and char
114. Flash-pyrolysis is a specific type of conventional slow pyrolysis that is performed
with the task to maximize te liquid fraction (here pyrolysis oil).
[0039] Pyrolysis gas 112A and pyrolysis oil 112B may be provided to conditioning units 120A,
120B. The PCT application
PCT/EP2010/002114 of Caterpillar Motoren GmbH & Co. KG filed on 1. April 2010 discloses an exemplary
method for preparing (conditioning) pyrolysis oil for an internal combustion engine.
The conditioning of the pyrolysis gas may include, for example, cleaning, cooling,
and compressing the pyrolysis gas.
[0040] Conditioned pyrolysis gas 112A and conditioned pyrolysis oil 112B may be used as
fuel for a gas genset 130A and a liquid genset 130B, respectively.
[0041] Gensets 130A and 130B may each provide an electricity output 132A, 132B, respectively.
Gas genset 130A may be, for example, a conventional gas engine adapted to run with
pyrolysis gas. Liquid genset 130B may be, for example, a conventional diesel engine
adapted to run with pyrolysis oil.
[0042] In addition, gas genset 130A and liquid genset 130B may generate one or more types
of waste heat outputs 134A and 134B, respectively. Waste heat outputs 134A and 134B
may be provided to an organic Rankine system 140 that uses the waste heat outputs
134A and 134B to additionally provide an electricity output 142.
[0043] Organic Rankine system 140 may be based on a direct ORC system, examples of which
are described in the following connection with Figs. 3 to 6. Specifically, direct
ORC systems may be based on a modular concept.
[0044] Referring to Fig. 3, an exemplary direct ORC system 200 of a modular concept may
include an ORC turbine module 210 and a modular heat rejection system 230.
[0045] Direct ORC system 200 may be configured such that in a closed cycle, a working medium
passes through ORC turbine module 210 and modular heat rejection system 230. Accordingly,
the heating of the working medium is performed directly within modular heat rejection
system 230 from one ore more waste heat types of one or more gensets (see also Fig.
7).
[0046] The ORC working medium is of organic nature instead of water (water steam). Examples
of the working medium include saturated and unsaturated hydrocarbons, fluorated hydrocarbons,
silicon oils such as siloxane, ammonia, and ammonia-water mixture. The type of working
medium defines inter alia the temperature range in which the ORC may be performed.
Silicone base fluids may, for example, be applied with pyrolysis-based power plant
100.
[0047] Referring again to Fig. 3, ORC turbine module 210 may include a turbine 212 for driving
a generator 214. ORC turbine module 210 may further include a regeneration unit 216
and a condenser unit 218.
[0048] Regeneration unit 216 may transfer heat of the working medium being still in the
gaseous phase after having driven turbine 212 to regenerated working medium in the
liquid phase.
[0049] Condenser unit 218 may be connected to a water cycle 220 and further cool down and
condense the working medium until it is in the liquid phase again.
[0050] ORC turbine module 210 may further include one or more control valves 226 and one
or more pumps 228.
[0051] ORC turbine module 210 may further include a working medium inlet 222 and a working
medium outlet 224 for a fluid connection between a working medium cycle section within
in ORC turbine module 210 and a working medium cycle section within modular heat rejection
system 230.
[0052] Modular heat rejection system 230 may include a common vapor separator 232 with an
inlet 252 and a plurality of boiler sub-systems 234.
[0053] For connecting the working medium cycle section within in ORC turbine module 210
and the working medium cycle section within modular heat rejection system 230, working
medium outlet 224 of ORC turbine module 210 may be fluidly connected to inlet 252
of vapor separator 232.
[0054] Vapor separator 232 may be configured for separating a gaseous phase from a liquid
phase of working medium that was heated in boiler sub-systems 234.
[0055] Before being supplied to boiler sub-systems 234, the working medium returned from
ORC turbine module 210 may be mixed with the separated liquid working medium having
passed boiler sub-systems 234.
[0056] Each boiler sub-system 234 may include a pump 236 and a boiler 238. Boiler 238 may
be configured for transferring heat of a waste heat output of a genset such as exhaust
gas 237 or cooling water of an increased temperature onto the working medium. One
or more boiler sub-system 234 may be operated according to the Lamont principle. Then,
boiler 238 of boiler sub-systems 234 may be considered a Lamont boiler.
[0057] Operating boiler sub-systems 234 according to the Lamont principle may provide a
fast response time with respect to changes in the heat transfer conditions within
respective boiler sub-systems 234. This may be based on a low pipe wall temperature
and good alpha-values associated with the heat transfer. Lamont boiler may further
be based on small size pipes, which may also positively affect the response time.
These advantages may in particular apply to the concept of adjusting the circulation
rate within the heat rejection cycle to a value of 1.3 to 1.5.
[0058] In the exemplary embodiment shown in Fig. 3, boiler sub-systems 234 may be fluidly
connected to vapor separator 232 via one or more boiler sub-system connection lines
240.
[0059] For boiler sub-systems 234 shown in detail in Fig. 3, a separator outlet 242 of vapor
separator 232 may be connected to a pump 236 boiler sub-systems 234 via boiler sub-system
connection line 240. Pump 236 may be connected to a boiler inlet 244 of boiler 238.
A boiler outlet 246 of boiler 238 may be connected to a separator inlet 248 of vapor
separator 232.
[0060] A gas phase outlet 250 of vapor separator 232 may be connected via a connection line
254 to working medium inlet 222 of ORC turbine module 210 such that the gaseous phase
working medium may be provided to turbine 212 for driving generator 214, thereby closing
the working medium cycle.
[0061] During operation, exhaust gas at a temperature of e.g. 310°C and a mass of e.g. 75000-112000
kg/h may be supplied through boiler 238. Pump 236 may pump the working medium through
boiler 238 such that the working medium partially changes into the gas phase and a
mixture of working medium in the gaseous phase and the liquid phase is generated.
The exhaust gas may exit boiler 238 at a temperature of about 180°C.
[0062] As an example of the temperature development of the working medium, the working medium
may exit ORC turbine module 210 at a temperature of about 170°C and may be heated
in boiler 238 to a temperature of about 250°C in a mixed state of the working medium
being partially in a gaseous phase and partially in a liquid phase. After the separation
in vapor separator 232, the gaseous working medium enters the ORC turbine module 210
at a temperature of about 250°C.
[0063] The mixture of gas phase and liquid phase of the heated working medium may be supplied
to and separated in vapor separator 232 so that only the gas phase may be provided
to ORC turbine module 210.
[0064] During operation of ORC turbine module 210, turbine 212 may drive generator 214 by
the gaseous working medium, which thereby expends and decreases in temperature. Downstream
of turbine 212, working medium may pass regeneration unit 216, in which heat of the
still gaseous working medium may be transferred to the liquid working medium, which
has been generated in condenser 218 from the gaseous phase of the working medium using
water cycle 220.
[0065] As indicated in Fig. 3, additional boiler sub-systems 234 may be fluidly connected
to vapor separator 232. Specifically, distributing the working medium to additional
boiler sub-systems 234 may be performed via boiler sub-system connection line 240
(see also Fig. 4).
[0066] For a direct ORC system with three boiler sub-systems 234, Fig. 4 illustrates the
flow of the working medium within boiler sub-systems 234. Moreover, Fig. 4 illustrates
the control of pumps 236 of boiler sub-systems 234.
[0067] Specifically, beginning at outlet 224 of ORC turbine module 210, regenerated working
medium may be provided to vapor separator 232, specifically through inlet 252, and
mixed in vapor separator 232 with the working medium originating from the separation
process of vapor separator 232. Alternatively, or in addition, the regenerated working
medium and the separated working medium may be mixed external to vapor separator 232.
[0068] Referring again to Fig. 4, at outlet 242, working medium may exit vapor separator
232 along boiler sub-system connection line 240, which may distribute the working
medium to three boiler sub-systems 234, each including at least one pump 236 and at
least one boiler 238.
[0069] Pumps 236 may be controlled via a control unit 305 to adjust the circulation speed
of the working medium through boilers 238 such that at least 15%, 20%, 30%, 40%, or
50% of the working medium are maintained in the liquid phase when exiting boiler 238.
For that purpose, control unit 305 may receive information of physical parameters
(such as temperature and pressure) of the working medium after the heating process
in boilers 238. For example, respective sensors may be provided at outlets 246. Alternatively
or in addition, control unit may receive information on the current performance and/or
future performance of the gensets.
[0070] As an example, in some embodiments, a load /temperature depending flow curve table
may provided in control unit 305. The load refers to the load of the genset of which
the waste heat is used in the respective boiler sub-system. The temperature refers
to the temperature of the working medium measured within the working medium loop of
that respective boiler sub-system. Fig. 4 shows schematically a temperature measurement
line 307 connecting control unit 305 with a temperature sensor 308 installed downstream
of boiler 238. In Fig. 4, only one temperature measurement line 307 is shown exemplarily.
In general, temperature measurement lines may be provided for one or more boiler sub-systems.
[0071] The load /temperature depending flow curve may be used to control the speed of pump
236 within a predefined range of throughput through boiler 238. Accordingly, control
unit 305 may assess the parameter load of the genset and temperature of the working
medium and derives there from a control parameter for controlling the pump speed.
The control output parameter may be limited such that the speed of pump 236 may only
be adjustable within a range of, e.g., 70-100%.
[0072] Control unit 305 may comprise a memory unit for providing load /temperature depending
flow curve tables for each of the boiler sub-systems. Control system may further be
connected via control lines 306 to pumps 236 of each of the boiler sub-systems.
[0073] In general, control unit 305 may allow adjusting individually the circulation speed
for each boiler and associated waste heat source such that the working medium is protected,
e.g., from thermal decomposition.
[0074] For example, increases the temperature of the working medium towards a preset temperature
limit, the pump speed may be increased as well. Similarly, is the load of the genset
increased, an increase of, e.g., the exhaust gas temperature may be expected and,
accordingly, the pump speed can be increased to avoid, limit or at least slow down
the increase of temperature of the working medium.
[0075] Referring again to Fig. 4, waste heat from, for example, three gensets such as combustion
engines, e.g. diesel or gas engines, may be transferred onto the working medium in
boilers 238. The heated working medium may then be combined and provided to inlet
248 of vapor separator 232.
[0076] Vapor separator 232 may separate the gaseous phase of the working medium from the
liquid phase and provide the gaseous phase via outlet 250 and line 254 to inlet 222
of ORC turbine module 210.
[0077] An embodiment of a boiler for modular heat rejection system 230 is described in connection
with Fig. 5. Specifically, heat rejection system 230 may include a boiler 438 that
includes a superheating zone 460.
[0078] In the embodiment shown in Fig. 5, ORC turbine module 210 as well as the heat transfer
in boiler sub-systems 234 onto the liquid phase working medium may work essentially
as described in connection with Figs. 3 and 4.
[0079] The embodiment shown in Fig. 5 distinguishes from the system shown in Fig. 3 downstream
of gaseous phase outlet 250 of vapor separator 232. Instead of being directly connected
to ORC turbine module 210, gaseous phase outlet 250 may be connected to an inlet 462
of superheating zone 460 of boiler 438. In Fig. 5, several reference signs for features,
which essentially maintain unchanged with respect to the embodiment of Fig. 3, were
nor reproduced to increase clarity of the illustration.
[0080] In superheating zone 460, the gaseous phase working medium is superheated by the
waste heat of e.g. exhaust gas 237 entering boiler 438. Superheated gaseous phase
working medium may exit superheating zone 460 at outlet 464, which may then be fluidly
connected to inlet 222 of ORC turbine module 210, such that the gaseous phase working
medium may be provided at a higher temperature to increase the efficiency of turbine
212.
[0081] As indicated in Fig. 5, additional boiler sub-systems 234 may include boilers 438
with superheating zones 460. Accordingly, gaseous phase may be distributed to additional
superheating zones as indicated by line 466. In that case, superheated gaseous phase
working medium exiting additional superheating zones 460 at outlet 464 may be combined
with superheated working medium from other superheating zones as indicated by line
468.
[0082] Similarly, as indicated in Figs. 3 and 4, additional boiler sub-systems 234 may be
provided such that heat working medium is combined before entering vapor separator
232 at inlet 248.
[0083] An embodiment of a direct ORC system using intensified preheating of the working
medium is described in connection with Fig. 6. In Fig. 6, several reference signs
for features, which essentially maintain unchanged with respect to the embodiment
of Figs. 3 and 4, were nor reproduced to increase clarity of the illustration.
[0084] Fig. 6 shows a direct ORC system that includes an ORC turbine module 510 and a boiler
sub-system 534 including a superheating zone as described in connection with Fig.
5.
[0085] In addition to the preheating discussed already in connection with Fig. 3 and regeneration
unit 216, the embodiment of Fig. 6 shows two types of preheating of the regenerated
working medium: a heat transfer unit 570 interacting with ORC turbine module 510 and
a preheating zone 580 of boiler sub-system 534. One or more of those types of preheating
may be performed to adapt the temperature of the working medium coming from ORC turbine
module 510 to the temperature of the separated liquid phase working medium provided
by vapor separator 232.
[0086] In the section of the working medium cycle with ORC turbine module 510, preheating
with a low temperature heat source such as, for example, a high-temperature or low-temperature
cooling circuit of a combustion engine (see also Fig. 7) may be implemented.
[0087] Specifically, heat transfer unit 570 may receive heat from a coolant medium 571 of
a coolant cycle of a genset, e.g. a combustion engine, and transfer that heat to the
regenerated working medium exiting pump 228. For that purpose, heat transfer unit
570 may be fluidly connected with pump 228 and regeneration unit 216.
[0088] The working medium exiting condenser at a temperature of, e.g., about 50°C may be
heated in heat transfer unit 570 to a temperature of, e.g., about 120°C. Thereafter,
the working medium may be further heated by regeneration unit 216 to a temperature
of, e.g., about 190°C.
[0089] In the section of the working medium cycle within boiler sub-systems 534, preheating
may be performed using, e.g., the low-temperature section of at least one boiler 538
of boiler sub-systems 524. Specifically, before entering vapor separator 232, the
working medium may pass preheating zone 580. E.g., outlet 224 of ORC turbine module
510 may be fluidly connected with inlet 582 of preheating zone 580. The preheated
working medium may leave preheating zone 580 at outlet 584 at a temperature of, e.g.,
about 260°C.
[0090] Outlet 584 may be fluidly connected to inlet 252 of vapor separator 232 in which
the preheated working medium is mixed with the separated liquid phase working medium
being also at a temperature of, e.g, 260°C.
[0091] As described in connection with Figs. 3 and 4, boiler 538 may provide a heating cycle
of the liquid working medium controlled by pump 236 such that the circulation speed
of the working medium may provide the working medium to vapor separator 232 in a gas
liquid mixed state.
[0092] As described in connection with Fig. 5, the separated gas phase may be provided to
superheating zone 460 of boiler 538 to further heat the gaseous phase working medium,
for example, to a temperature of, e.g., 270°C before providing the super-heated gaseous
phase working medium to turbine 212.
[0093] Exemplarily, waste heat sources of a genset for the direct organic Rankine cycle
systems disclosed herein are illustrated in Fig. 7 based on a schematic medium-sized
diesel or gas engine.
[0094] Specifically, Fig. 7 shows an exemplary air system and cooling systems of a conventional
combustion engine 700 such as gas engine 130A or liquid fuel engine 130B used in pyrolysis-based
power plant 100 described in connection with Fig. 2. In Fig. 7, dual line arrows refer
to the air system, e.g. stream of the charge air and exhaust gas, and single line
arrows refer to the cooling systems, e.g. the stream of a coolant medium, usually
water.
[0095] Engine 700 may comprise a turbocharger system 710 (single or double stage), a high
temperature cooling circle 720, and a low temperature cooling circle 730.
[0096] Assuming an initial temperature of the charge air of 25°C, the compression of the
charge air in turbocharger system 710 may increase the temperature of the charge air
from 25°C to 225°C. High temperature cooling circle 720 may reduce the temperature
of the charge air from 225°C to 90°C and low temperature cooling circle may reduce
the temperature of the charge air further from 90°C to 45°C such that engine 700 is
charged with air at a temperature of about 45°C.
[0097] After the combustion process, exhaust gas at a temperature of several hundred degrees
may exit the combustion chamber and may be used to drive turbocharger system 710.
After turbocharger system 710, the temperature of the exhaust gas may be reduced to
about 310°C.
[0098] In general, heat can be recovered from coolant medium 571 of high temperature cooling
circle 720 and/or low temperature cooling circle 730 as well as from high temperature
exhaust gas 237 before or after turbocharger system 710.
[0099] As an example, boiler 238 is indicated to use the waste heat of exhaust gas 237 after
turbocharger system 710 and heat transfer unit 570 is indicated to use the waste heat
of coolant medium 571 of high temperature cooling circle 720 and/or low temperature
cooling circle 730.
Industrial Applicability
[0100] The term "genset" as used herein comprises inter alia internal combustion engines
and steam or combustion turbine based power generating systems.
[0101] The term "internal combustion engine" as used herein is not specifically restricted
and comprises any engine, in which a fuel combustion process is performed. Examples
of fuel include gas or liquid fuel such as diesel, marine diesel, and pyrolysis oil.
Examples of internal combustion engines for the herein disclosed configuration of
a two-stage turbocharged system include medium speed internal combustion diesel engines,
like inline and V-type engines of the series M20, M25, M32, M43 manufactured by Caterpillar
Motoren GmbH & Co. KG, Kiel, Germany, operated in a range of 500 to 1000 rpm as well
as high speed gas engines, e.g. provided by Caterpillar Motoren GmbH & Co. KG, Kiel
[0102] The herein disclosed types of preheating and super-heating may be included in an
ORC system alone or in combination/sub-combination.
[0103] The modular ORC systems disclosed herein may allow increasing the over all efficiency
(e.g. the generated power) of diesel, gas, biomass power plants as well as reducing
the operation costs.
[0104] Although the preferred embodiments of this invention have been described herein,
improvements and modifications may be incorporated without departing from the scope
of the following claims.
1. A direct organic Rankine cycle system (200) for generating power using a working medium,
the direct organic Rankine cycle system (200) comprising:
a boiler sub-system (234) comprising a pump (236) and a boiler (238), the pump (236)
configured to pump the working medium through the boiler (238);
a vapor separator (232) connected to a working medium outlet (246) of the boiler (238)
and configured for separating a gaseous phase of the working medium;
an organic Rankine turbine module (210, 410) fluidly connected to the vapor separator
(232), the organic Rankine turbine module (210, 410) comprising a turbine (212) driven
by the separated working medium gaseous phase;
a control system (305) configured to control the pump (236) for adjusting the circulation
speed of the working medium through the boiler (238) such that at least 15%, 20 %,
30 %, 40 %, or 50% of the working medium are maintained in the liquid phase when exiting
the boiler (238), wherein the control system (305) is connected with a temperature
sensor (308) for receiving temperature data of the working medium and configured for
receiving a load parameter of a genset, which provides waste heat to the boiler sub-system
(234), and wherein the control system (305) is further configured for deriving a pump
speed control parameter for controlling the speed of the pump (236) from the load
parameter and the temperature parameter.
2. The direct organic Rankine cycle system (200) according to claim 1, wherein the pump
speed control parameter is derived using a load/temperature depending flow curve table
associated with the boiler sub-system (234).
3. The direct organic Rankine cycle system (200) according to claim 1 or 2, wherein the
boiler (238) is configured for heating the working medium with waste heat of exhaust
gas of a combustion engine (130A, 130B) and/or waste heat of a high temperature cooling
cycle of a combustion engine (130A, 130B).
4. The direct organic Rankine cycle system (200) according to any one of the preceding
claims, wherein the boiler (238) comprises a super-heating system connected with a
gaseous phase outlet of the vapor separator, the super-heating system (460) configured
for super-heating the separated working medium gaseous phase and providing the super-heated
separated working medium gaseous phase to the organic Rankine turbine module.
5. The direct organic Rankine cycle system (200) according to any one of the preceding
claims, wherein the boiler (238) is operatable as a Lamont boiler.
6. The direct organic Rankin cycle system (200) according to any one of the preceding
claims, wherein the working medium is selected from the group of organic working media
comprising saturated and unsaturated hydrocarbons, fluorated hydrocarbons, silicon
oils such as siloxane, ammonia, and ammonia-water mixture.
7. The direct organic Rankine cycle system (200) according to any one of the preceding
claims, wherein the boiler sub-system (234) is one of a plurality of boiler sub-systems
each having a boiler, and each boiler is fluidly connected to the vapor separator
(232) and configured for heating the working medium with waste heat.
8. The direct organic Rankine cycle system (200) according to claim 7, wherein the boiler
sub-systems comprise an inlet (252) for regenerated working medium provided by the
organic Rankine turbine module (210, 410) for mixing the regenerated working medium
with the separated liquid working medium and/or wherein a gaseous phase outlet of
the vapor separator (232) is configured for providing the separated working medium
gaseous phase to the organic Rankine turbine module (210, 410) directly or via a super-heating
zone (460).
9. The direct organic rankine cycle system (200) according to any one of the preceding
claims, wherein the boiler sub-system (234) and the vapor separator (232) are part
of a modular heat rejection system (230) of the direct organic Rankine cycle system
(200), and the modular heat rejection system (230) comprises a plurality of boiler
sub-systems and the pumps of the boiler sub-systems are controlled by the control
system such that at least 15%, 20 %, 30 %, 40 %, or 50% of the working medium are
maintained in the liquid phase when exiting the respective boiler.
10. The direct organic rankine cycle system (200) according to any one of the preceding
claims, wherein the organic Rankine turbine module (210, 410) further comprises a
heating system (570) for heating regenerated working medium in the liquid phase, e.g.,
by the heat of a charge air coolant system of a combustion engine.
11. A biomass combined cycle power generating system (100) comprising:
a pyrolysis reactor (110) generating pyrolysis oil and pyrolysis gas from biomass;
a pyrolysis oil engine (130B) for generating power from the pyrolysis oil, thereby
producing waste heat;
a pyrolysis gas engine (130A) for generating power from the pyrolysis gas, thereby
producing waste heat; and
a direct organic Rankine cycle system according to any of the preceding claims 1-11
comprising two boiler sub-systems (234) for generating power from the waste heat of
the pyrolysis oil engine (130B) and the pyrolysis gas engine (130A), wherein the waste
heat is supplied to a respective boiler of the boiler sub-systems.
12. The biomass combined cycle power generating system (100) of claim 11, wherein the
waste heat includes at least one of heat of exhaust gas and heat of a coolant system
of the pyrolysis oil engine (130B) and at least one of heat of exhaust gas and heat
of a coolant system of the pyrolysis gas engine (130A).
13. A method for operating a direct organic Rankine cycle, the method comprising:
circulating an organic working medium through a boiler (238) at a circulation speed
such that at least 15%, 20 %, 30 %, 40 %, or 50% of the organic working medium are
maintained in the liquid phase when exiting the boiler (238), heating the working
medium in the boiler (238) using waste heat such as heat of an exhaust gas or a cooling
circuit of an combustion engine;
separating a working medium gas phase and a working medium liquid phase from the heated
working medium;
deriving power from the separated working medium gas phase;
regenerating a working medium liquid phase of the working medium after power generation;
returning a mix of the regenerated working medium liquid phase and the separated working
medium liquid phase to the boiler (238),
receiving information on a load parameter of a genset, which provides waste heat to
the boiler sub-system (234);
receiving temperature data of the working medium; and
deriving a pump speed control parameter from the load parameter and the temperature
parameter for controlling the circulation speed.
14. The method of claim 13, further comprising:
superheating the separated working medium gas phase.
1. Direktes organisches Rankine-Prozesssystem (200) zur Leistungserzeugung mit einem
Arbeitsmedium, mit
einem Boileruntersystem (234) mit einer Pumpe (236) und einem Boiler (238), wobei
die Pumpe (236) dazu ausgebildet ist, das Arbeitsmedium durch den Boiler (238) zu
pumpen,
einem Dampfabscheider (232), der mit einem Arbeitsmediumausgang (246) des Boilers
(238) verbunden ist und zum Abscheiden einer Gasphase des Arbeitsmediums ausgebildet
ist,
einem organischen Rankine-Turbinenmodul (210, 410), das mit dem Dampfabscheider (232)
fluid verbunden ist, wobei das organische Rankine-Turbinenmodul (210, 410) eine von
der abgeschiedenen Arbeitsmediumgasphase angetriebene Turbine (212) aufweist,
einem Steuerungssystem (305), das dazu ausgebildet ist, die Pumpe (236) zum Einstellen
der Zirkulationsgeschwindigkeit des Arbeitsmediums durch den Boiler (238) derart anzusteuern,
dass mindestens 15%, 20%, 30%, 40% oder 50% des Arbeitsmediums beim Verlassen des
Boilers (238) in der Flüssigphase sind, wobei das Steuerungssystem (305) mit einem
Temperatursensor (308) zum Empfangen von Temperaturdaten des Arbeitsmediums verbunden
ist und dazu ausgebildet ist, einen Lastparameter eines Gensets zu empfangen, welches
Abwärme dem Boileruntersystem (234) zur Verfügung stellt, und wobei das Steuerungssystem
ferner dazu ausgebildet ist, einen Pumpengeschwindigkeitssteuerungsparameter zum Steuern
der Geschwindigkeit der Pumpe (236) von dem Lastparameter und dem Temperaturparameter
abzuleiten.
2. Direktes organisches Rankine-Prozesssystem (200) nach Anspruch 1, wobei der Pumpengeschwindigkeitssteuerungsparameter
unter Verwendung einer Last-/Temperaturabhängigen Strömungskurventabelle, die mit
dem Boileruntersystem (234) in Bezug steht, abgeleitet wird.
3. Direktes organisches Rankine-Prozesssystem (200) gemäß Anspruch 1 oder 2, wobei der
Boiler (238) dazu ausgebildet ist, das Arbeitsmedium mit Abwärme des Abgases eines
Verbrennungsmotor (130A, 130B) und/oder Abwärme eines Hoch-Temperaturkühlkreislaufs
eines Verbrennungsmotors (130A, 130B) zu erwärmen.
4. Direktes organisches Rankine-Prozesssystem (200) gemäß einem der vorhergehenden Ansprüche,
wobei der Boiler (238) ein Super-Erwärmsystem aufweist, welches mit einem Gasphasenausgang
des Dampfabscheiders verbunden ist, wobei das Super-Erwärmsystem (460) dazu ausgebildet
ist, die abgeschiedene Arbeitsmediumgasphase super-zu-erwärmen und die super-erwärmte,
abgeschiedene Arbeitsmediumgasphase dem organischen Rankine-Turbinenmodul zur Verfügung
zu stellen.
5. Direktes organisches Rankine-Prozesssystem (200) gemäß einem der vorhergehenden Ansprüche,
wobei der Boiler (238) als ein Lamont-Boiler betreibbar ist.
6. Direktes organisches Rankine-Prozesssystem (200) gemäß einem der vorhergehenden Ansprüche,
wobei das Arbeitsmedium ausgewählt ist aus der Gruppe von Arbeitsmedien, welche saturierte
und unsaturierte Kohlenwasserstoffe, fluorierte Kohlenwasserstoffe, Silikonöle wie
Siloxan, Ammoniak, und Ammoniakwassergemisch aufweist.
7. Direktes organisches Rankine-Prozesssystem (200) gemäß einem der vorhergehenden Ansprüche,
wobei das Boileruntersystem (234) eines einer Mehrzahl von Boileruntersystemen ist,
die jeweils einen Boiler aufweisen, und jeder Boiler ist mit dem Dampfabscheider (232)
fluidverbunden und dazu ausgebildet, das Arbeitsmedium mit Abwärme zu erwärmen.
8. Direktes organisches Rankine-Prozesssystem (200) gemäß Anspruch 7, wobei die Boileruntersysteme
einen Einlass (252) für regeneriertes Arbeitsmedium, welches von dem organischen Rankine-Turbinenmodul
(210, 410) bereitgestellt wird, zum Mischen des regenerierten Arbeitsmediums mit dem
abgeschiedenen flüssigen Arbeitsmedium aufweist und/oder wobei ein Gasphasenausgang
des Dampfabscheiders (232) dazu ausgebildet ist, die separierte Arbeitsmediumgasphase
dem organischen Rankine-Turbinenmodul (210, 410) direkt oder über eine Super-Heizzone
(460) bereitzustellen.
9. Direktes organisches Rankine-Prozesssystem (200) gemäß einem der vorhergehenden Ansprüche,
wobei das Boileruntersystem (234) und der Dampfabscheider (232) Teil eines modularen
Wärmeabfuhrsystems (230) des direkten organischen Rankine-Prozesssystems (200) sind
und das modulare Wärmeabfuhrsystem (230) eine Mehrzahl von Boileruntersystemen aufweist
und die Pumpen der Boileruntersysteme von dem Steuerungssystem derart gesteuert werden,
dass mindestens 15%, 20%, 30%, 40% oder 50% des Arbeitsmediums beim Verlassen des
entsprechenden Boilers in der Flüssigphase sind.
10. Direktes organisches Rankine-Prozesssystem (200) gemäß einem der vorhergehenden Ansprüche,
wobei das organische Rankine-Turbinenmodul (210, 410) ferner ein Heizsystem (570)
zum Heizen regenerierten Arbeitsmediums in der Flüssigfaser aufweist, zum Beispiel
durch die Wärme eines Ladeluftkühlsystems eines Verbrennungsmotors.
11. Biomassen-Kombileistungserzeugungssystem (100) mit
einem Pyrolysereaktor (110) zum Erzeugen von Pyrolyseöl und Pyrolysegas aus Biomasse,
einem Pyrolyseölmotor (130B) zur Leistungserzeugung aus dem Pyrolyseöl, wodurch Abwärme
erzeugt wird,
einem Pyrolysegasmotor (130A) zur Leistungserzeugung aus dem Pyrolysegas, wodurch
Abwärme erzeugt wird, und
einem direkten organischen Rankine-Prozesssystem gemäß einem der Ansprüche 1 bis 11
mit zwei Boileruntersystemen (234) zur Leistungserzeugung von der Abwärme des Pyroloyseölmotors
(130B) und des Pyrolysegasmotors (130A), wobei die Abwärme einem entsprechenden Boiler
der Boileruntersysteme zugeführt wird.
12. Biomassen-Kombileistungserzeugungssystem (100) nach Anspruch 11, wobei die Abwärme
Wärme des Abgases und/oder Wärme eines Kühlsystems des Pyrolyseölmotors (130B) und
Wärme des Abgases und/oder Wärme eines Kühlsystems des Pyrolysegasmotors (130A) aufweist.
13. Verfahren zum Betreiben eines direkten organischen Rankine-Prozesses mit
Zirkulieren eines organischen Arbeitsmediums durch einen Boiler (238) bei einer Zirkulationsgeschwindigkeit
derart, dass mindestens 15%, 20%, 30%, 40% oder 50% des organischen Arbeitsmediums
in der Flüssigphase beim Verlassen des Boilers (238) sind,
Erwärmen des Arbeitsmediums in dem Boiler (238) unter Verwendung von Abwärme wie Wärme
eines Abgases oder eines Kühlkreislaufs eines Verbrennungsmotors,
Abscheiden einer Arbeitsmediumgasphase und einer Arbeitsmediumflüssigphase von dem
erwärmten Arbeitsmedium,
Gewinnen von Leistung von der abgeschiedenen Arbeitsmediumgasphase, Regenerieren einer
Arbeitsmediumflüssigphase des Arbeitsmediums nach der Leistungserzeugung,
Rückführen einer Mischung der regenerierten Arbeitsmediumflüssigphase und der abgeschiedenen
Arbeitsmediumflüssigphase zu dem Boiler (238),
Empfangen von Information eines Lastparameters eines Gensets, das Abwärme dem Boileruntersystem
(234) bereitstellt,
Empfangen von Temperaturdaten des Arbeitsmediums und
Ableiten eines Pumpgeschwindigkeitssteuerungsparameters von dem Lastparameter und
dem Temperaturparameter zum Steuern der Zirkulationsgeschwindigkeit.
14. Verfahren nach Anspruch 13, ferner mit
Super-Erwärmen der abgeschiedenen Arbeitsmediumgasphase.
1. Système de cycle de Rankine organique direct (200) pour générer de l'énergie en utilisant
un fluide de travail, le système de cycle de Rankine organique direct (200) comprenant:
un sous-système de chaudière (234) comprenant une pompe (236) et une chaudière (238),
la pompe (236) étant configurée pour pomper le fluide de travail à travers la chaudière
(238) ;
un séparateur de vapeur (232) connecté à une sortie de fluide de travail (246) de
la chaudière (238) et configuré pour séparer une phase gazeuse de fluide de travail
;
un module de turbine de Rankine organique (210, 410) connecté de façon fluidique au
séparateur de vapeur (232), le module de turbine de Rankine organique (210, 410) comprenant
une turbine (212) entraînée par la phase gazeuse de fluide de travail séparée ;
un système de commande (305) configuré pour commander la pompe (236) pour régler la
vitesse de circulation du fluide de travail à travers la chaudière (238) de telle
sorte qu'au moins 15 %, 20 %, 30 %, 40 % ou 50 % du fluide de travail soient maintenus
dans la phase liquide lorsque celui-ci sort de la chaudière (238),
dans lequel le système de commande (305) est connecté à un capteur de température
(308) pour recevoir des données de température du fluide de travail et configuré pour
recevoir un paramètre de charge d'un groupe électrogène qui fournit de la chaleur
perdue au sous-système de chaudière (234) et dans lequel le système de commande (305)
est en outre configuré pour dériver un paramètre de commande de vitesse de pompe pour
commander la vitesse de la pompe (236) à partir du paramètre de charge et du paramètre
de température.
2. Système de cycle de Rankine organique direct (200) selon la revendication 1, dans
lequel le paramètre de commande de vitesse de pompe est dérivé en utilisant une table
de courbes de flux dépendant de la température/charge associée au sous-système de
chaudière (234).
3. Système de cycle de Rankine organique direct (200) selon la revendication 1 ou 2,
dans lequel la chaudière (238) est configurée pour chauffer le fluide de travail avec
de la chaleur perdue de gaz d'échappement d'un moteur à combustion (130A, 130B) et/ou
avec de la chaleur perdue d'un cycle de refroidissement à haute température d'un moteur
à combustion (130A, 130B).
4. Système de cycle de Rankine organique direct (200) selon l'une quelconque des revendications
précédentes, dans lequel la chaudière (238) comprend un système de surchauffage connecté
à une sortie de phase gazeuse du séparateur de vapeur, le système de surchauffage
(460) étant configuré pour surchauffer la phase gazeuse de fluide de travail séparée
et pour fournir la phase gazeuse de fluide de travail séparée surchauffée au module
de turbine Rankine organique.
5. Système de cycle de Rankine organique direct (200) selon l'une quelconque des revendications
précédentes, dans lequel la chaudière (238) peut fonctionner comme une chaudière Lamont.
6. Système de cycle de Rankine organique direct (200) selon l'une quelconque des revendications
précédentes, dans lequel le fluide de travail est sélectionné dans le groupe de fluides
de travail organiques comprenant des hydrocarbures saturés et insaturés, des hydrocarbures
fluorés, des huiles de silicium telles que le siloxane, l'ammoniac et un mélange d'eau
et d'ammoniac.
7. Système de cycle de Rankine organique direct (200) selon l'une quelconque des revendications
précédentes, dans lequel le sous-système de chaudière (234) est un parmi une pluralité
de sous-systèmes de chaudière comprenant chacun une chaudière et chaque chaudière
est connectée de façon fluidique au séparateur de vapeur (232) et est configurée pour
chauffer le fluide de travail avec de la chaleur perdue.
8. Système de cycle de Rankine organique direct (200) selon la revendication 7, dans
lequel le sous-système de chaudière comprend une entrée (252) pour un fluide de travail
régénéré fourni par le module de turbine Rankine organique (210, 410) afin de mélanger
le fluide de travail régénéré avec le fluide de travail séparé et/ou dans lequel une
sortie de phase gazeuse du séparateur de vapeur (232) est configurée pour fournir
la phase gazeuse de fluide de travail séparée au module de turbine Rankine organique
(210, 410) directement ou par l'intermédiaire d'une zone de surchauffage (460).
9. Système de cycle de Rankine organique direct (200) selon l'une quelconque des revendications
précédentes, dans lequel le sous-système de chaudière (234) et le séparateur de vapeur
(232) font partie d'un système de rejet de chaleur modulaire (230) du système de cycle
de Rankine organique direct (200) et le système de rejet de chaleur modulaire (230)
comprend une pluralité de sous-systèmes de chaudière et les pompes des sous-systèmes
de chaudière sont commandées par le système de commande de telle sorte qu'au moins
15 %, 20 %, 30 %, 40 % ou 50 % du fluide de travail soient maintenus dans la phase
liquide lorsque celui-ci sort de la chaudière respective.
10. Système de cycle de Rankine organique direct (200) selon l'une quelconque des revendications
précédentes, dans lequel le module de turbine Rankine organique (210, 410) comprend
en outre un système de chauffage (570) pour chauffer un fluide de travail régénéré
dans la phase liquide, par exemple par la chaleur d'un système de refroidissement
d'air de charge d'un moteur à combustion.
11. Système de génération d'énergie à cycle combiné avec la biomasse (100), comprenant:
un réacteur de pyrolyse (110) générant de l'huile de pyrolyse et du gaz de pyrolyse
à partir d'une biomasse ;
un moteur à huile de pyrolyse (130B) pour générer de l'énergie à partir de l'huile
de pyrolyse, produisant de ce fait de la chaleur perdue ;
un moteur à gaz de pyrolyse (130A) pour générer de l'énergie à partir du gaz de pyrolyse,
produisant de ce fait de la chaleur perdue ; et
un système de cycle de Rankine organique direct selon l'une quelconque des revendications
précédentes 1 à 11, comprenant deux sous-systèmes de chaudière (234) pour générer
de l'énergie à partir de la chaleur perdue du moteur à huile de pyrolyse (130B) et
du moteur à gaz de pyrolyse (130A), dans lequel la chaleur perdue est fournie à une
chaudière respective des sous-systèmes de chaudière.
12. Système de génération d'énergie à cycle combiné avec la biomasse (100) selon la revendication
11, dans lequel la chaleur perdue comprend au moins une parmi de la chaleur de gaz
d'échappement et de la chaleur d'un système de refroidissement du moteur à huile de
pyrolyse (130B) et au moins une parmi de la chaleur de gaz d'échappement et de la
chaleur d'un système de refroidissement du moteur à gaz de pyrolyse (130A).
13. Procédé d'exploitation d'un cycle de Rankine organique direct, le procédé comprenant
les étapes suivantes:
faire circuler un fluide de travail organique à travers une chaudière (238) à une
vitesse de circulation telle qu'au moins 15 %, 20 %, 30 %, 40 % ou 50 % du fluide
de travail soient maintenus dans la phase liquide lorsque celui-ci sort de la chaudière
(238),
chauffer le fluide de travail dans la chaudière (238) en utilisant de la chaleur perdue
telle que de la chaleur de gaz d'échappement ou d'un circuit de refroidissement d'un
moteur à combustion ;
séparer une phase gazeuse de fluide de travail et une phase liquide de fluide de travail
du fluide de travail chauffé ;
dériver de l'énergie de la phase gazeuse de fluide de travail séparée ;
régénérer une phase liquide de fluide de travail du fluide de travail après la génération
d'énergie ;
renvoyer un mélange de la phase liquide de fluide de travail régénérée et de la phase
liquide de fluide de travail séparée à la chaudière (238),
recevoir des informations sur un paramètre de charge d'un groupe électrogène qui fournit
de la chaleur perdue au sous-système de chaudière (234) ;
recevoir des données de température du fluide de travail ; et
dériver un paramètre de commande de vitesse de pompe à partir du paramètre de charge
et du paramètre de température afin de commander la vitesse de circulation.
14. Procédé selon la revendication 13, comprenant en outre le surchauffage de la phase
gazeuse de fluide de travail séparée.