Note: Descriptions are shown in the official language in which they were submitted.
ENERGY MANAGEMENT APPARATUS, SYSTEM AND METHOD
FIELD
The present disclosure relates to an energy process handling system, and more
particularly, to combined cooling, heating, and power (CCHP) systems for use
in localized
environments.
BACKGROUND
Each of United States Patent Application Ser. No. 14/461,962 (entitled
"Temperature
Modulated Desiccant Evaporative Cooler and Indirect and Direct Evaporative Air
Conditioning Systems, Methods and Apparatus", filed on August 18, 2014, and
published as
U.S. 2015/0128625), and United States Patent Application Ser. No. 14/314,771
(entitled
"Power Generation System and Method", filed on June 25, 2014, and published as
U.S.
2015/0033778), may provide background and points of reference helpful in the
understanding
of certain subject matter introduced herein, for all purposes and made a part
of the present
disclosure.
Due to a dependence upon existing infrastructures, latent technologies and
industry
specialization, local energy supplies are often remotely and centrally
generated, distributed for
local use via grid systems and divided according to application. As an
example, natural gas
may be transported using a central pumping station and delivered by a pipeline
for local
consumption (e.g., for use in heating water, cooking food or ventilated
heating systems).
Similarly, electricity is typically produced at a central power plant and
distributed over a
traditional electric grid system for use in such applications as lighting and
powering
appliances or ventilated cooling systems. In many respects, such a multi-
management
technique for delivering energy is considered wasteful of manpower and
material. It is also
highly energy inefficient with energy lost to waste heat disposal in
centralized electric power
generation and non-reversible losses of energy transmission both via electric
power lines and
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gas pumping stations and pipelines. Such losses are not only expensive and
wasteful, but also
contribute to the hazardous effects of toxic and green house gas production.
To address these deficiencies, manufacturers have to turned to technologies
affording
local power generation including both renewable energy sources, such as solar,
wind and
geothermal, as well as heat engine technologies, allowing the local burning of
fossil fuels.
Although promising in their clean, inexhaustible nature, renewable
technologies do not offer
performance competitive with that possible with fossil fuel technologies (for
local, low power
generation applications). Noting this, some manufacturers have turned to local
energy
management solutions such as combined heat and power (CHP) systems, heat pumps
(HP)
and absorption chillers. CHP systems vastly improve fuel efficiency by
conducting energy
conversion locally at the spot where the energy is used, thus utilizing
combustion heat and
avoiding transmission losses not possible with conventional centralized
communal electrical
grids. Alternatively, because these move, rather than convert energy, HPs have
proven to be a
highly efficient and flexible method of heating and cooling.
However, such systems are often produced, installed and managed by separate
providers to service separate energy needs; exist in different parts of the
local environment;
and operate independently. Thus, although such technologies eliminate some
inefficiencies of
central production, such lack of integration serves to re-establish
inefficiencies of the multi-
management approach, preventing the utilization of the additional energy
harvesting and
improved efficiencies possible via integrated, symbiotic sharing subsystems.
SUMMARY
In one aspect, the present disclosure provides a fully integrated energy
management
system capable of providing highly efficient energy production and/or
management for local
energy needs, including electric power generation, heating, cooling, energy
storage, and water
processing. A basic architecture of such systems may include a CHP and
supporting elements,
such as vapor-compression cooling systems, HPs, evaporative coolers (EC), heat
exchanger
networks, and energy storage subsystems, to realize a number of configurations
suited for a
given application, energy requirements and\or available energy resources.
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In a further aspect, the present disclosure provides for a CHP and cooling
system
characterized by subsystems having an integrated nature, which afford greater
application
flexibility and higher efficiencies relative to conventional systems.
In a further aspect, the present disclosure provides for a system and method
for
generating electric power and providing air conditioning in a localized
installation. A hybrid
power generator, including an internal combustion engine operatively coupled
to an electric
generator, may be generate both electrical and mechanical energy. The system
may include
an air conditioning system, including at least one compressor. The at least
one compressor
may be operatively coupled to the hybrid power generator. The hybrid power
generator may
be engageable with the compressor, mechanically and/or electrically, to
compress a working
refrigerant fluid.
BRIEF DESCRIPTION OF THE DRAWINGS
So that the manner in which the features and advantages of embodiments of the
present disclosure may be understood in more detail, a more particular
description of the
briefly summarized embodiments above may be had by reference to the
embodiments which
are illustrated in the appended drawings that form a part of this
specification. It is to be noted,
however, that the drawings illustrate only various exemplary embodiments, and
are therefore
not to be considered limiting of the scope of this disclosure, as it may
include other effective
embodiments as well.
FIG. 1 is a simplified block diagram or schematic of an energy management
system or
power generation and distribution system according to the present disclosure;
FIG. 2 is a simplified schematic of an electrical resource management system
according to the present disclosure;
FIG. 3a is a simplified schematic of a power generation and distribution
system
installation, including a CCHP utilizing a vapor compression cooling system,
according to an
embodiment;
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FIG. 3b is a simplified schematic of a power generation and distribution
system
installation, including a CCHP utilizing an electrically driven vapor
compression cooling
system, according to an embodiment;
FIG. 3c is a simplified schematic of a power generation and distribution
system
installation, including a CCHP utilizing both a selectively mechanically
drivable compressor
and a selectively electrically drivable compressor, according to an
embodiment;
FIG. 3d is a simplified schematic of the power generation and distribution
system
installation in FIG. 3c shown with the mechanically drivable compressor
selectively engaged
and directly mechanically driven by an engine, according to the present
disclosure;
FIG. 3e is a simplified schematic of the power generation and distribution
system
installation in FIG. 3c shown with the electrically drivable compressor
selectively engaged
and electrical driven by an electric generator, according to the present
disclosure;
FIG. 3f is a simplified schematic of a power generation and distribution
system
installation, including a CCHP with a single, hybrid compressor, according to
an embodiment;
FIG. 4a is a simplified schematic of a power generation and distribution
system
installation, including a CCHP employing a mechanically driven compressor and
a heat
pump, according to the present disclosure;
FIG. 4b is a simplified schematic of a power generation and distribution
system
installation, including a CCHP employing an electrically-driven compressor and
a heat pump,
according to the present disclosure;
FIG. 4c is a simplified schematic of a power generation and distribution
system
installation, including a CCHP employing a hybrid, dual compressor and heat
pump
configuration, according to the present disclosure;
FIG. 4d is a simplified schematic of a power generation and distribution
system
installation, including a CCHP employing a hybrid, single compressor und heat
pump
configuration, according to the present disclosure;
FIG. 5a is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing a mechanically driven
compressor and a
waste heat recovery system associated with the engine, according to the
present disclosure;
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FIG. 5b is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing an electrically driven
compressor and a
waste heat recovery system associated with the engine, according to the
present disclosure;
FIG. 5c is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing a hybrid dual compressor and
heat pump
configuration and a waste heat recovery system associated with the engine,
according to the
present disclosure;
FIG. 5d is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing a hybrid single compressor and
heat pump
configuration and a waste heat recovery system associated with the engine,
according to the
present disclosure;
FIG. 6a is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing a mechanically driven
compressor and heat
pump configuration, and enhanced waste heat recovery according to the present
disclosure;
FIG. 6b is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing an electrically driven
compressor and heat
pump configuration, and enhanced waste heat recovery according to the present
disclosure;
FIG. 6c is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing a selectively mechanically or
electrically
driven dual compressor and heat pump configuration, and enhanced waste heat
recovery
according to the present disclosure;
FIG. 6d is a simplified schematic of an exemplary power generation and
distribution
system installation, including a CCHP employing a single, selectively
mechanically or
electrically driven compressor and heat pump configuration, and enhanced waste
heat
recovery according to the present disclosure;
FIGS. 7a-7e are simplified illustrations of an exemplary mass heat exchanger
suitable
for use with an evaporative cooling apparatus or system according to the
present disclosure;
FIGS. 8a-8b are simplified illustrations of a desiccant dehumidifier unit
suitable for
use with an evaporative cooling apparatus or system according to the present
disclosure;
CA 29/0144 2017-06-09
FIGS. 9a-9c are simplified illustrations of an exemplary installation
including a CCHP
heater, dehumidifier, and mass heat exchanger according to the present
disclosure;
FIGS. 10a-10e are simplified illustrations of flow patterns associated with an
exemplary installations including a mass heat exchanger according to the
present disclosure;
FIGS. 1 la-11d are simplified illustrations of flow patterns associated with
exemplary
installations, according to the present disclosure;
FIGS. 12a and 12b are simplified illustrations of flow patterns associated
with an
exemplary localized air conditioning system employing a desiccant wheel,
according to the
present disclosure;
FIG. 13 is a simplified diagram of an exemplary CCHP system installation,
including
a waste and ambient heat powered heat engine and vacuum cooler, according to
the present
disclosure;
FIG. 14 is a simplified diagram of an exemplary, CCHP system installation,
including
a waste and ambient heat powered heat engine and indirect evaporative cooler,
according to
the present disclosure;
FIG. 15 is a simplified schematic of an exemplary, CCHP system installation,
including a waste and ambient heat powered heat engine, according to the
present disclosure;
FIG. 16 is a simplified schematic of an exemplary, CCHP system installation,
including a waste heat hot water and ambient heat powered heat engine,
according to the
present disclosure; and
FIG. 17 is a simplified schematic of an exemplary localized air conditioning
or other
energy system utilizing waste heat generated by a heat engine or HVAC to
transfer energy to
a working fluid, according to the present disclosure.
DETAILED DESCRIPTION
Embodiments of the present disclosure will now be described more fully with
reference to the accompanying drawings, which illustrate various exemplary
embodiments.
The disclosed concepts may, however, be embodied in many different forms and
should not
be construed as being limited by the illustrated embodiments set forth herein.
Rather, these
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embodiments are provided so that this disclosure will be thorough as well as
complete and
will fully convey the scope to those skilled in the art and modes of
practicing the
embodiments.
In one aspect, the present disclosure provides for an improved energy
handling,
distribution, and\or generating system, and\or specific components or
subsystems thereof, and
methods of operating or performing the same. The present disclosure also
provides for a
system and method for air conditioning.
Referring to the system diagram of FIG. 1, certain embodiments of the present
disclosure relate to a power generation system, system 1000. System 1000
includes a power
generator, including internal combustion engine 100 (prime mover) and an
electric generator
110 powered by the internal combustion engine 100. System 1000 includes a heat
recovery
apparatus or unit 130, and a cooling apparatus or unit 320. The internal
combustion engine
100, heat recovery unit 130, and cooling unit 132 are operatively
interconnected. The heat
recovery unit 130 is disposed to capture waste heat produced by the internal
combustion
engine 100. The cooling unit 132 includes a refrigeration unit powered by the
internal
combustion engine 100, and may include at least one compressor driven by the
internal
combustion engine 100. In certain embodiments, the cooling unit 132 includes a
heat pump
driven by the internal combustion engine 100. In operation, the electric
generator 110 is
engageable by the internal combustion engine 100 to generate electricity.
The system 1000 also includes an electrical energy converter 115. The
electrical
energy converter 115 converts, distributes, and regulates electrical energy
such that electrical
energy for a local environment may be supplied by either the internal
combustion engine 100
and electric generator 110; an electric grid 116; a renewable energy source
114, such as solar,
wind or geothermal energy sources; or battery storage 118. Also, the
electrical energy
converter 115 may be configured to allow locally generated energy from the
internal
combustion engine 100 and electric generator 110 and/or from renewable energy
sources 114
to be redistributed into the electric grid 116 for communal use. The cooling
unit 132 may be
electrically or mechanically powered via converter 115 or via a drive shaft
120 coupled with
the internal combustion engine 100, and a heat recovery unit 130 for local
heat generation.
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System 1000 also includes an HVAC system 134 with air temperature and relative
humidity
(RH) controlled via heat recovery unit 130 and/or cooling unit 132.
Additionally, the system
1000 includes a water management system 138, such as a boiler or chiller, with
temperature
controlled via heat recovery unit 130 and/or cooling unit 132. Thus, the
configuration of
system 1000 forms a combined cooling, heat and power (CCHP) system that, in
some
embodiments, is capable of sinking and sourcing energy from multiple sources,
enabling
system 1000 to adapt to a wide range of energy supply conditions and
applications, while also
supplying all forms of energy typically required for local consumption
including utility
power, HVAC, and water conditioning.
With reference to FIG. 2, system 1000, and methods of use thereof for energy
generation and\or distribution, may employ various types of fuels and heat
engine designs
including diesel, gasoline, dual fuel designs, and biofuels.
For example, in some
embodiments, internal combustion engine 100 is a naturally aspirated, four-
cycle, natural gas
internal combustion engine. Electric generator 110 (e.g., alternator) is
operably connected to
an engine crankshaft 101, such as by gear or belt and clutch drive assembly
102. Thus,
engine crankshaft 101 and drive assembly 102 operate to transfer mechanical
energy from the
internal combustion engine 100 to the electric generator 110, for conversion
of the transferred
mechanical energy into electrical energy.
The electrical energy produced in the electric generator 110 is then
transferred to the
electrical energy converter 115 for converting, distributing, and regulating
the electrical
energy. The electrical energy converter 115 includes conditioning circuitry
105 configured to
manage or condition the electricity from electric generator 110, and to
perform other
conditioning functions, including rectification, regulation and generator over
current
protection circuitry, depending upon the specific electric generator 110
design. In some
embodiments, electric generator 110 is a DC brushless generator, and
conditioning circuitry
105 includes a regulator that maintains a constant voltage supply with
variations in engine
RPM and electrical loads.
The electrical energy converter 115 also includes a grid conditioning
subsystem with a
transformer assembly 109 providing galvanic isolation and conditioning
circuitry 106 that
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includes a bidirectional power converter for converting AC power from the
electric grid 116
to a compatible DC supply for use with the system 1000, such as when sinking
energy from
the electric grid 116 as well as when converting the CCHP DC supply to
synchronized AC
supply for supplying power back to the electric grid 116 from system 1000.
The electrical energy converter 115 includes battery monitoring and charging
circuitry
107 for monitoring battery status as well as maintaining proper charging
protocols for
charging battery storage elements 118. In some embodiments, charging circuitry
107 is a
current regulator with voltage feedback to a complex balanced charger used
with a multi-cell
Lithium-Ion battery bank. In some embodiments, charging circuitry 107 is a
current regulator
with voltage feedback to a complex balanced charger, and battery storage 118
includes a
series of parallel, coupled, deep cycle lead acid batteries.
The electrical energy converter 115 includes multiplexing circuitry 108
electrically
coupled with each electrical power source of system 1000, including electric
generator 110,
electric grid 116, and battery storage 118. Multiplexing circuitry 108 may be
adapted to allow
user power source selection via system controller 104 and user interface 111.
System
controller 104 may include mechanical relays and a programmed logic control
(PLC), power
MOSFET arrays and solid-state relays controlled via custom microcontroller
hardware, or
remote distributed control via a SCADA network. The electrical output of
electrical energy
converter 115 passes through power interface circuitry 103, which includes
additional
regulation and protection circuitry such as current limit circuits and fuses
to further protect
load and supply circuitry from system related faults.
Certain embodiments include an electrical control unit 112 (ECU) as a
controller that
provides the logic (hardware and software) for controlling the internal
combustion engine
100. System controller 104 and ECU 112 may be connected via a digital
communication link,
such as OBDII or CANBus, allowing the units to share performance data such as
engine
RPM, manifold pressures, spark advance, electrical load, and supply status,
which may be
used in conjunction with firmware algorithms in one or both units in a
feedback loop to
optimize efficiency and system performance.
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For cooling local environments, system 1000 may include various modes of AC
production. In a first embodiment shown in Fig. 3a, in addition to the power
generation
components described above with reference to FIGS. 1 and 2, system 1000
includes a vapor
compression subsystem. Vapor compression subsystem includes a mechanically
driven
compressor 320 with a clutch and gear or belt drive system 300 coupled with
the engine
crankshaft 101. Vapor compression subsystem includes a condenser 340 located
outside the
local environment, an expansion valve 360, and evaporator 350 located within
the local
environment. The vapor compression subsystem operates to extract heat from the
local
environment via heat transfer through the evaporator 350 with vaporization of
the working
fluid 335. Compressor 320 then receives the vaporized working fluid from the
evaporator
350, and operates to compress the working fluid to a high-pressure vapor. Heat
is then
expelled outside of the local environment via the condenser 340, resulting in
condensation of
the working fluid. The condensed working fluid then flows from the condenser
340 into the
expansion valve 360, wherein the working fluid is expanded into a low-pressure
vapor.
In the embodiment shown in FIG. 3a, compressor 320 is driven by the mechanical
output of the internal combustion engine 100 via a belt and pulley linkage
engaged via drive
system 300 (e.g., an electromagnetic clutch) under control of cooling control
unit 370.
Cooling control unit 370 may be powered by the electrical energy converter
115, as shown
and describe above with reference to FIGS. 1 and 2. The cooling control unit
370 may be, for
example and without limitation, an on/off switch or a thermostatically
controlled feedback
system used to automatically engage the compressor 320 at a duty cycle
sufficient to maintain
a constant local ambient temperature.
In another embodiment shown illustrated by FIG. 3b, system 1000 employs an
electrically driven compressor 310 that is directly powered by or from
electrical energy
converter 115. All other components and functionality are the same as
previously described
with reference to FIG. 3A, with the exception that cooling control unit 370
controls electrical
power to the compressor 310 instead of mechanically engaging the compressor
via drive
system 300.
CA 2970144 2017-06-09
FIGS. 3c-3e illustrate another embodiment of system 1000 that employs a hybrid
vapor compression cooling system, including both an electrically driven
compressor 310 and
a mechanically driven compressor 320. The compressors 310 and 320 may be
selectively
engaged via cooling control unit 370 (not shown), thus allowing cooling to be
achieved using
either fuel (e.g., gas) or electrical power. The cooling control unit 370 in
the embodiment of
FIGS. 3c-3e may include both on/off controls for the electrical compressor 310
and drive
system 300, as well as drive circuitry for control of flow control valves 331,
332 (e.g.,
solenoid valves). Flow control valves 331, 332 may be disposed within the
vapor
compression cooling subsystem refrigerant loop to control the flow of the
working fluid, such
that the working fluid can be selectively controlled to flow through either
compressor 310 or
compressor 320. In operation, to deactivate the cooling system, cooling
control unit 370 turns
off the power supply to the electrical compressor 310, disengages the drive
system 300 of the
mechanical compressor 320, and de-energizes the flow control valves 331, 332.
In some
embodiments, idle valve positions of the flow control valves 331, 332 are
immaterial when
both compressors are deactivated, as there is no working fluid flowing. With
reference to
FIG. 3d, to activate the mechanical compressor 320, cooling control unit 370
powers the drive
system 300, deactivates electrical compressor 310, and energizes both flow
control valves
331, 332 to result in the flow of working fluid through the mechanical
compressor 320. With
reference to FIG. 3e, to activate the electrical compressor 310, cooling
control unit 370
deactivates drive system 300, thus disengaging the mechanical compressor 320
from the
internal combustion engine 100 drive train. Also, when the electrical
compressor 310 is
activated, both flow control valves 331, 332 are de-energized, resulting in
the working fluid
cycling through the electrical compressor 310. As such, the embodiment of
system 1000
shown in FIGS. 3c-3e allow for selectively driving the working fluid of the
vapor
compression subsystem via mechanical compressor 320 or electrical compressor
310.
FIG. 3f depicts another embodiment of system 1000 employing a hybrid vapor
compression that includes a single compressor 315. The single compressor 315
may have a
hybrid design that is capable of operating with either direct mechanical or
electrical input.
Thus, the single compressor 315 is electrically coupled to electric generator
110 via the
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electrical energy converter 115, and is mechanically coupled to the internal
combustion
engine 100 via the engine crankshaft 101 and drive system 300.
Depending on the load applied to the internal combustion engine 100, it may,
at times,
be more efficient to power the vapor compression cooling subsystem using the
electric grid
116, battery storage 118, renewable energy resources 114, electric generator
110, or
mechanical drive system 300. The dual hybrid compressors 310, 320 shown in
FIG. 3c, as
well as the single hybrid compressor 315 shown in FIG. 3f, allow for "on the
fly" selection of
the power source that drives the working fluid of the vapor compression
cooling subsystem.
Such selection of the power source affords a backup source of power in the
case of one power
system becoming inoperable, e.g., if the fuel supply to the internal
combustion engine 100 is
interrupted during such events as a gas leak or if there is a black out in the
electric grid 116.
Additionally, such selection of the power source allows the user to select the
most economical
fuel, such as using the mechanical compressor 320 (or mechanically driving the
single
compressor 315) and a gas supplied internal combustion engine 100 during
periods of high
electric grid 116 demand when tier pricing rates are highest, and switching to
the electrically
driven compressor 310 (or electrically driving the single compressor 315)
during low cost,
low demand electric grid 116 periods.
Certain embodiments of the present disclosure provide for a system 1000 for
generating electric power in a localized installation (e.g., a commercial or
residential
building). In such embodiments, the system 1000 includes a hybrid power
generator
composed of internal combustion engine 100, and electric generator 110; an air
conditioning
cooling system (cooling unit 132) including a compressor (e.g., compressor
310, 320, or 315);
and a selectively engageable drive assembly composed of drive assembly 102
and/or drive
assembly 300. The selectively engageable drive assembly of such a system 1000
is operably
connected with the hybrid power generator, and is operable to selectively
engage the electric
generator 110 and/or the internal combustion engine 1000 with the compressor.
In operation,
the hybrid power generator is engageable with the compressor to compress the
working
refrigerant fluid.
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In some embodiments, due to enhanced efficiency and flexibility in being able
to both
heat and cool, a heat pump (HP) is employed in place of a vapor compression
subsystem.
With reference to FIGS. 4a-4d, an embodiment of system 1000 including a heat
pump is
shown. In FIGs. 4a-4d, all components are the same as those used in the vapor
compression
subsystem of FIGS. 3a-3f, with the exception of the addition of a valve 410
that is configured
to selectively reverse the flow direction of the working fluid 335, thus
interchanging the
operational role of the condenser 340 and the evaporator 350, allowing for
both heating and
cooling. While valve 410 may have any valve configuration capable of reversing
the flow
direction of the working fluid, in certain embodiments valve 410 is a
discharge port driven 4-
way solenoid valve. The operation of system 1000 with the heat pump is similar
to those of
the embodiments previously described with reference to FIGS. 3a-3f using a
vapor
compression refrigeration subsystem. The system 1000 employing the heat pump
may
include a mechanical compressor 320, an electrical compressor 310, dual hybrid
mechanical
and electrical compressors 320 and 310, or a single hybrid compressor 315, as
shown,
respectively, in FIGS. 4a, 4b, 4c, and 4d. The operation of each of said
compressors 310, 320,
and 315 is the same as described above with respect to FIGS. 3a-3f.
Additionally, cooling
control unit 370 of FIGS. 4a-4d operates in the same manner as described above
with respect
to FIGS. 3a-3f, with the exception that the cooling control unit 370 of FIGS.
4a-4d
additionally includes circuitry for controlling the valve 410 to enable either
heating or cooling
functionality. For example, cooling control unit 370 may control valve 410 by
simply
energizing the valve solenoid for one direction of working fluid flow and de-
energizing for
the valve solenoid for the other direction of working fluid flow.
Some embodiments disclosed herein provide for a system for generating electric
power and operating a refrigeration cycle for a localized installation. Such a
system includes
a power generator (internal combustion engine 100 and electric generator 110);
an air
conditioning cooling system (cooling unit 132), including at least one
compressor
(compressor 310, 320, and/ or 315); and a selectively engageable drive
assembly (drive
system 300) operably connected with the power generator. In such a system, the
power
generator is engageable with the at least one compressor to compress a working
refrigerant
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fluid. A heat pump, as shown in FIGS. 4a-4d, is disposed in a refrigeration
cycle with the
compressor. The drive system 300 is operable to selectively engage the
electric motor 110 or
the internal combustion engine 100 with the at least one compressor. For
example, in some
embodiments, the system includes a single compressor 315 that is selectively
engaged or
disengaged from operative coupling with the engine crankshaft 101 of the
internal combustion
engine 100. In other embodiments, such a system includes at least two
compressors,
mechanically driven compressor 320 and electrically driven compressor 310.
The
mechanically driven compressor 320 is selectively engageable with the internal
combustion
engine 100 and powerable thereby, and the electrically driven compressor 310
is selectively
engageable with the electric generator 110 and electrically powerable thereby.
Heat pump operation depends, at least in part, upon the condenser 340 and
evaporator
350 ambient temperature differential, which may exhibit a low coefficient of
performance
(COP) when cooling with high outside temperatures or when heating with low
outside
temperatures. One solution to address this issue is the use of a dual fuel
system in which use
of the heat pump is stopped and use of a conventional electric or gas powered
burner is
initiated to generate heat from fossil fuels or electrical power, such as when
there is
insufficient internal energy in ambient air for operation of the heat pump.
While use of a dual
fuel system is effective, such an approach is relatively complex and
diminishes efficiency by
relying on less efficient support systems. Thus, in some embodiments, system
1000 includes a
heat recovery unit 130 through which the working fluid is cycled. As shown in
FIG. 5a, heat
recovery unit 130 includes heat exchanger 510. Although any radiative or
conductive heat
sources may be used as heat exchanger 510, some embodiments of heat exchanger
510
include a series of heat exchangers attached to the engine exhaust manifold,
catalytic
converter and exhaust distribution system of the internal combustion engine
100. The heat
recovery unit 130 is in fluid communication with the refrigerant cycle of the
cooling unit 132
via flow control valves 331 and 332 for receipt of the working fluid
therefrom. The additional
heat provided by the heat recovery unit 130 to the working fluid both
increases internal
combustion engine 100 efficiency and heat pump COP, while also increasing the
heat pump
dynamic range and allowing it to function during periods of low outside
temperatures without
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CA 2970144 2017-06-09
resorting to the use of generator technologies. In FIGs. 5a-5d, all components
and their
associated functions and operation are the same as those used in system 1000
in FIGS. 4a-4d,
with the exception of the addition of the heat recovery unit 130, including
heat exchanger 510,
as well as flow control valves 333 and 334.
Some embodiments provide for an energy generating and distribution system 1000
including internal combustion engine 100; cooling unit 132 powered by energy
generated by
the internal combustion engine 100; and electric generator 110 powered by the
internal
combustion engine 100. In some such embodiments, the cooling unit 132 is
selectively
directly powerable by the internal combustion engine 100, such as via
mechanically driving
compressor 320 via drive system 300; selectively electrically driven and
interoperably
connected with the electric generator 110, such as via powering compressor 310
with electric
generator 110; or combinations thereof. Such a system 1000 may include heat
recovery unit
130 associated thermally coupled with internal combustion engine 100 to
capture waste heat
generated thereby. In some embodiments of such a system, an HVAC system 134 is
directly
associated (e.g., thermally and/or fluidly coupled) with the heat recovery
unit 130 to transfer
energy there-between.
With reference to FIGS. 6a-6d, certain embodiments of system 1000 exhibit
increased
heating ability and enhanced heat capacity or cooling ability. In FIGs. 6a-6d,
all components
and their associated functions and operation are the same as those used in
system 1000 in
FIGS. 5a-5d, with the exception of the addition of the heat exchanger 610 and
valve 620 to
the heat recovery unit 130. Valve 620 is in fluid communication with the heat
exchanger 610,
heat exchanger 510, and flow control valves 331, 332. In operation, exhaust
heat exchanger
610 and valve 620 allow the working fluid to be routed either through the heat
exchanger 510
alone, or in series with the exhaust heat exchanger 610. The valve 620 may be
in operational
communication with cooling control unit 370, which may control the opening and
closing of
valve 620. Routing the working fluid through heat exchanger 510 enhances
heating ability of
system 1000. Routing the working fluid through exhaust heat exchanger 610
increases the
overall system heat capacity via the use of both the condenser 340 and exhaust
heat exchanger
610 to increase cooling ability of the system 1000. While FIGS. 6a-6d depict a
particular
CA 2970144 2017-06-09
valve configuration the heat recovery unit 130, heat recovery unit 130 may
have different
configurations depending upon the specific application. For example and
without limitation,
valve 620 could be configured with heat exchangers 510 and 610 in parallel
with common
supply and return lines of the working fluid, allowing selective flow of the
working fluid
through either heat exchanger 510 or heat exchanger 610, thus selectively
enhancing either
heating or cooling functions as opposed to both heating and cooling functions.
Thus, the heat
recovery unit 130 is not limited to the specific piping configurations shown
in FIGS. 6a-6d.
Embodiments of system 1000 with heat recovery unit 130 provide physical and/or
thermodynamic integration of CHP and HP devices of the system 1000.
Certain embodiments of the system provided herein include evaporative cooling
(EC)
subsystems. Such subsystems utilize the high heat capacity of water to lower
the air
temperature by using its internal energy to vaporize liquid water. Such
subsystems may be
used, for example, in low humidity environments, and have may have a
relatively simple
design and operation. For example, some embodiments of such subsystems may
require no
refrigerant, minimal capital investment, and provide a nearly 80% savings in
operational cost
compared to vapor compression systems. Evaporative cooling subsystems may be
employed
in dry climate zones, industrial complexes, and buildings having large volume
requirements.
Operation is relatively simple compared to refrigerant based systems, with one
difference
being that while both take advantage of the latent heats during a phase change
of a medium,
refrigerant based systems carry heat outside the local environment via
refrigerant while EC
systems replace local air with cooled air from outside. FIGS. 7a-7e are
reproduced from
incorporated United States Patent No. 14,461,962, and correspond to FIGS. 19A-
19E of
United States Patent No. 14,461,962 (the '962 application), respectively.
Thus, the
descriptions from the '962 application of FIGS. 19A-19E are incorporated
herein with
reference to present FIGS. 7a-7e, respectively. Additionally, FIGS. 8a and 8b
are reproduced
from the incorporated '962 application, and correspond to FIGS. 10 and 11 of
the '962
application. Thus, the descriptions of FIGS. 10 and 11 from the '962
application are
incorporated herein with reference to present FIGS. 8a and 8b, respectively.
16
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With references to FIGS. 7a-8b, embodiments of EC subsystems include a mass
heat
exchanger (MHX) 700, and a desiccant dehumidifier 800. The MHX 700 includes a
basic
evaporation cooling architecture (e.g., a dew point cooler architecture)
composed of air
channels 710 (e.g., plastic vent panels and separators) sandwiched between
layers of
hygroscopic foil 705 (e.g., natural fiber hygroscopic membranes) for
channeling air input via
ports 720 and 721 and cool and warm outputs 722 and 723, respectively and
exhaust port 724.
The MHX 700 channels water via fill port 725, distribution 727, collection
tray 728, and drain
port 726. Some embodiments include a steel enclosure 729 formed as a generally
rectangular
housing with a length from inlet to outlet ports greater than either the
height or width.
As describe in more detail below, the MHX 700 may be configured into:
= Air Pass Through mode
= Direct Evaporative Cooling (DEC) or Swamp Cooling mode (e.g., FIG. 10a)
= Indirect Evaporative Cooling (IEC) or Dew Point Cooling mode (e.g., FIG.
10c)
= Combination DEC/IEC mode (e.g., FIG. 10d)
Embodiments in which MHX 700 is combined with desiccant dehumidifier 800 and
indirect evaporative cooling (IEC) control unit 810 may be configured for
multiple air
processing techniques including, but not limited to:
= Increased evaporative air flow
= Modulated preheating of working air
= Increased evaporation surface
= Dehumidification of both working and process air
= Water (refrigerant) treatment
= Vacuum creation to reduce dew point temperature
Such EC subsystems may be powered by the CCHP system 1000, thus provide the EC
subsystem with operational independence from the electric grid, producing
little or no outside
exhaust with the use of multiple such units, maintaining the desired RH via
full control of
both humidifying and dehumidifying operations without additional fuel
consumption, and
17
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using an environmentally-friendly water in place of chemical refrigerants.
FIGS. 9a-9c are
reproduced from the '962 application, and correspond to FIGS. 12-14 of the
'962 application,
respectively.
Thus, the descriptions of FIGS. 12-14 from the '962 application are
incorporated herein with reference to present FIGS. 9a-9c, respectively. FIGS.
9a-9c depict a
residential installation of system 1000 showing water supply lines and fan
locations. System
1000 is installed at a local environment 1001 (e.g., a residential or
commercial building), and
operatively coupled with energy sources 116a (e.g., an electrical grid) and
1166 (e.g., a
natural gas line) for operation of the internal combustion engine. System
1000, as shown in
FIG. 9a, is configured to provide heat for heating water in hot water heater
117. Hot water
heater 117 may be in fluid communication with desiccant dehumidifier 800,
which may be
operatively coupled with MHX 700. System 1000 of FIGS. 9a-9c may be, for
example, the
same or similar as any of the embodiments of system 1000 shown in FIGS.3a-6d,
15, or 16.
Certain embodiments provide for an evaporative cooling (EC) system including a
desiccant dehumidifier 800 and one or more heat and mass exchangers, MXH 700,
one or
more fans, water source, and distribution to control the air temperature,
relative humidity
(RH) and ventilation of the air in a local environment. The desiccant
dehumidifier 800 may
have a rotating wheel type construction in which desiccant is heated via a hot
water supply
and a conductive heat exchanger or directly via a resistive heat source
powered by electrical
energy provided from the electric energy converter 115. The MHX 700 may be
composed of
fans, a water source and a series of channels or flutes and hygroscopic film
that increase the
surface area, allow for fresh water filtration and forced convection to
efficiently engage
cooling of air via evaporation of the water, as well as control the direction
and source of air
input and exhaust. The fans of the MHX 700 may include pre-primary supply fans
at the inlet
of the MHX 700 to draw supply air into the MHX unit 700; post-primary fans at
the outlet of
the MHX unit 700 to pull primary air out of the MHX unit 700; secondary
exhaust fans for
drawing secondary air out of the MHX unit 700 for exhausting outside of the
local
environment; or combinations thereof. In some embodiments of the system, the
desiccant
dehumidifier 800 is engaged with one or more MHX 700 units to dehumidify
either the MXH
700 supply or exhaust air. One or multiple MHX units 700 may be used to
provide a number
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of EC protocols, including direct evaporation (DEC), indirect evaporation
(IEC), indirect-
direct evaporation (IDEC), and DX. In some embodiments, multiple MHX 700 units
may be
placed in parallel to handle larger amounts of air throughput than is possible
with a single
MHX unit 700. Multiple MHX units 700 may be placed in series or staged for
super cooling
to generate larger temperature differentials than is possible using a single
MHX unit 700.
The MHX units 700 may be adapted to accept supply air from one or multiple
sources
including both recycled air from within the local environment and unprocessed
air from
outside the local environment.
FIGS. 10a-10e depict various MHX 700 airflow patterns for various, exemplary
configurations. FIGS. 10a-10e are reproduced from the '962 application, and
correspond to
FIGS. 21-23, 25 and 25 of the '962 application, respectively. Thus, the
descriptions of FIGS.
21-23, 25 and 25 from the '962 application are incorporated herein with
reference to present
FIGS. 10a-10e, respectively.
The configuration of MHX 700 shown in FIG. 10a is a direct evaporative cooling
configuration in which the primary air from outside (e.g., dry, fresh outside
air) enters MHX
700 via port 720, is cooled via evaporation within MHX 700, and is then passed
directly to the
local environment via port 722.
The configuration of MHX 700 shown in FIG. 10b is a humidifier configuration
in
which the primary air (e.g., hot air or cool dry air from indoors) enters MHX
700 via port 721,
water vapor is added (e.g., via fill port 725 and distribution 727), and the
humid air is then
passed directly to the local environment via port 723. The resulting airflow
pattern from the
MHX 700 configuration of FIG. 10a within the local environment 100 is depicted
in Fig. 12a.
FIG. 12a is reproduced from the '962 application, and corresponds to FIG. 22
of the '962
application. Thus, the description of FIG. 22 from the '962 application is
incorporated herein
with reference to present FIG. 12a.
The configuration of MHX 700 shown in FIG. 10c is an indirect evaporative
cooling
configuration. One drawback of direct evaporative cooling is the increased
humidity of the
primary air due to the added moisture providing a 'swamp' or muggy feeling to
the air quality.
To avoid this, many evaporative systems use an indirect method in which the
primary air
19
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feeding the local environment is isolated from the evaporative cooled air with
heat transferred
via a heat exchanger. With reference to FIG. 10c, primary air (e.g., hot
outside air) enters port
721, is cooled via evaporation in MHX 700, and is passed through a heat
exchanger as
secondary air where it cools primary air (e.g., hot dry air) entering port 720
via conduction
before exiting via exhaust port 724. The conduction cooled primary air (cold
dry air) is then
passed to the local environment via port 722. The resulting airflow pattern,
from the
configuration of FIG. 10c, within said local environment 1001 is shown
depicted in Fig. 12b.
FIG. 12b is reproduced from the '962 application, and corresponds to FIG. 24
of the '962
application. Thus, the description of FIG. 24 from the '962 application is
incorporated herein
with reference to present FIG. 12b.
The configuration of MHX 700 shown in FIG. 10d is a combination of direct and
indirect evaporative cooling. The operation of the configuration of MHX 700
shown in FIG.
10d is the same as that of the of MHX 700 shown in FIG. 10c, with the
exception that a
portion of the evaporation cooled primary air (cold wet air) is passed
directly to the local
environment via port 723, such that the local environment is cooled by a
mixture of wet and
dry primary air.
The configuration of MHX 700 shown in FIG. 10e is an indirect evaporative
cooling
with indoor air venting. The operation of the configuration of MHX 700 shown
in FIG. 10e is
the same as that of the of MHX 700 shown in FIG. 10c, with the exception that
inside air (i.e.,
stale indoor air from within the local environment) enters via port 723 and is
used as
secondary air to conduction cool primary air (hot outside air) entering port
720. The inside
airflow may be assisted via an exhaust fan.
FIGS. 1 1 a-lld depict various airflow patterns and quality within the local
environment resulting from various system configurations. FIGS. 11a-11 d are
reproduced
from the '962 application, and correspond to FIGS. 15-18 of the '962
application,
respectively.
Thus, the descriptions of FIGS. 15-18 from the '962 application are
incorporated herein with reference to present FIGS. 1 1 a-11d, respectively.
FIG. 1 la depicts
an example of an indirect/direct evaporative cooling (IDEC) in which a 50%
mixture of inside
and outside air is used to cool the local environment 1001 using both direct
and indirect
CA 2970144 2017-06-09
methods. As used herein, "outside air" refers to air from outside of the local
environment
1001, and "inside air" refers to air from inside of the local environment
1001. Using a
mixture of low temperature indoor air and high temperature outside air
provides allows for a
continual supply of fresh air, while also reducing the cooling load. FIG. 1 lb
depicts a multi-
staged or super cooling configuration using two MHXs, 700a and 700b, in which
primary air
is cooled in MHX 700a, dehumidified in desiccant dehumidifier 800, and again
cooled a
second time in MHX 700b before passing to the local environment 1001. Such a
configuration
may be capable of handling large temperature differences such as is common
with equatorial
climates, walk-in coolers or large scale local environments where the air-flow
rate exceeds the
maximum cooling rate possible with a single MHX unit. FIG. 11c depicts an
airflow pattern
that reduces local environment 1001 temperature via the use of a secondary
cooling stage at
the output of MHX 700 MX, including a direct evaporative (DX) unit 701. FIG. 1
1 d depicts
an airflow pattern utilizing heat pipes.
Some embodiments of the present disclosure provide for a system for supplying
cooling air to a residence or building interior. Such a system includes a heat
and mass
exchanger, MHX 700, positioned to discharge conditioned air into a residence
or building
interior, local environment 1001; and a rotatable desiccant wheel
dehumidifier, desiccant
dehumidifier 800. The desiccant dehumidifier 800 is positioned and configured
to receive
supply air for treatment; exhaust hot, humid air; and supply dry air to the
MHX 700. The
MHX 700 is positioned and configured to receive dry air from the desiccant
dehumidifier 800,
and to supply cooler dry air to the local environment 1001. In some
embodiments, the
desiccant dehumidifier 800 is positioned and configured to receive dry
recycled air from
within the interior of the residence or building (local environment 1001).
In some embodiments of the system for supplying cooling air to a residence or
building interior, the desiccant dehumidifier 800 is positioned and configured
to receive dry
recycled air from the residence or building interior, or is positioned and
configured to receive
outdoor air for treatment.
Some embodiments of the system for supplying cooling air to a residence or
building
interior include a second heat and mass exchanger, MHX 700a, positioned
upstream of the
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desiccant dehumidifier 800 to deliver supply air to the desiccant dehumidifier
800, and
configured to receive return air from the residence or building interior and
outdoor air for
treatment.
In some embodiments of the system for supplying cooling air to a residence or
building interior, the MHX 700 includes a vacuum chamber positioned on a
discharge side
through which said cool supply air discharged to the residence or building
interior travels. In
certain embodiments, the MHX 700 includes a vacuum chamber positioned on an
exhaust
side through which exhaust air exits.
In some embodiments of the system for supplying cooling air to a residence or
building interior, the MHX 700 is configured in a direct evaporative cooling
mode. In other
embodiments, the MHX 700 is configured and operable in an indirect evaporative
cooling
mode, including inlet ports to receive hot dry air and hot outside air, an
exhaust to discharge
wet cool exhaust, and an outlet to discharge cool dry air. The MXH 700 may be
configured
and operable in an indirect/direct evaporative cooling mode, including inlet
ports to receive
hot dry air and hot outside air, an exhaust to discharge wet cool exhaust, and
outlet ports to
discharge cool dry air and cool wet air. The MHX 700 may also be configured
and operable
in an enthalpy mode, including inlet ports to receive hot outside air, an
exhaust to discharge
wet cool exhaust, an outlet to discharge cool dry air, and an auxiliary port
selectively
positionable and operable to receive stale indoor air into the MHX 700.
FIG. 13 depicts an embodiment of the system 1300 employing a vacuum cooler
1310
in a closed loop system (waste heat evaporator), which uses water as the
operating fluid
(refrigerant). FIG. 13 is reproduced from the '962 application, and
corresponds to FIG. 27 of
the '962 application. Thus, the description of FIG. 27 from the '962
application is
incorporated herein with reference to present FIG. 13. The heat and mass
exchanger is
modified to operate with the vacuum cooler 1310 adjacent and upstream of a
liquid desiccant
absorber 1312. As shown, a vacuum pump 1314 is operated with the vacuum cooler
1310.
The liquid desiccant absorber 1312 receives mixed hot humid outside air and
indoor air, as
well as solely outside air. Heat exchanger 1316 is positioned to interact with
(and heat) liquid
desiccant 1318 and hot water source 1330. Warmer desiccant concentrate is
communicated to
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the liquid desiccant absorber 1312 and cooler desiccant dilute is returned.
Cool dry air is
discharged from the vacuum cooler 1310 to the target environment (e.g., a
local environment,
such as a house or building). The system 1300 is also equipped with a
condenser 1320 and
vapor separator 1322 to treat and cycle system water passing from and to the
vacuum cooler
1310.
In the embodiment of system 1300 depicted in FIG. 14, the closed loop system
employs an indirect evaporative cooler 1311 in place of the vacuum cooler
1310. Humid cool
air is exhausted from the cooler via the humid cool air outlet 1315, and cool
dry air is supplied
to the local environment. FIG. 14 is reproduced from the '962 application, and
corresponds to
FIG. 28 of the '962 application. Thus, the description of FIG. 28 from the
'962 application is
incorporated herein with reference to present FIG. 14.
In a method operating the closed loop system of FIG. 13 or 14, the system 1300
recovers condensate absorbed by the desiccant. Minimizing liquid desiccant
exposure, the
closed loop system 1300 reduces the corrosion effects on system components and
associated
systems and equipment, and other damage otherwise caused by liquid desiccant
exposure. The
system 1300 also reduces system water loss and produces clean distilled water.
FIG. 15 depicts an embodiment of system 1000 in which the heat recovery unit
130
includes heat exchanger 510 thermally coupled with the internal combustion
engine 100, heat
exchanger 1520 in fluid communication with the evaporator 350, and a heat
engine 1510
disposed in series with the heat exchangers 510 and 1520. The heat engine 1510
may be, for
example and without limitation, a thermoelectric or thermoacoustic generator
or cooler.
System 1000 with the heat engine 1510 may power electrical appliances from
either natural
gas or the internal energy of the surrounding air.
With reference to FIG. 16, aside from HVAC applications, heat recovered from
the
internal combustion engine 100 by the heat recovery unit 130 may be used
directly to produce
hot water or steam, such that system 1000 is capable of supplying the local
environment with
a number of heat related services. In the embodiment shown in FIG. 16, water
is circulated
through a pipeline via pump 1605, where waste heat is transferred via heat
exchanger 510
(e.g., an evaporator) to water condensers 1610, 1620 and 1630. Water condenser
1610 is
23
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thermally coupled to a desiccant dehumidifier 800, water condenser 1620 is
thermally coupled
to a boiler 1650, and water condenser 1630 is thermally coupled to a radiating
space heater
1660, thus providing desiccant dehumidification, boiler, and radiating space
heater functions,
respectively. Water flow to each water condenser 1610, 1620, and 1630 may be
selectively
controlled and/or bypassed via flow control valves 1611, 1621 and 1631,
depending upon
need. Flow control valves 1611, 1621, and 1631 may be controlled via a master
water heater
control panel 1600 or via individual controls. As discussed with respect to
compressors 1310,
1320 and 1315, pump 1605 may be driven either mechanically via a gear or belt
linkage to
engine crankshaft 101, or electrically via electric generator 110, electric
grid 116, or battery
storage 118 in conjunction with electric energy converter 115.
Some embodiments disclosed herein provide for a system and method for
generating,
converting, and/or distributing energy for use in a local environment. The
energy generated,
converted, and/or distributed in such a system may include mechanical energy
obtained from
the crankshaft 101 of a reciprocating internal combustion engine (ICE) 100;
electrical energy
produced by the electric generator 110 powered by said mechanical energy;
electrical energy
produced delivered via a communal electric grid 116 from a remote source;
electrical energy
produced produced by a local renewable energy source 114; electrical energy
produced stored
within an electrochemical battery medium 118; heat energy derived from the
capture of the
ICE 100 combustion waste heat via heat recovery unit 130; or combinations
thereof The
system may include an energy conversion and distribution circuit (electrical
energy converter
115) composed of a series of energy converters, such as transformers and
inductive switch
mode circuits and switches, such as relays and power MOSFETS, allowing the
system
electrical energy to be obtained in part or in whole by a combination of
multiple electrical
energy sources including, but not limited to: (1) electrical energy produced
by electric
generator 110 powered by ICE 100; (2) electrical energy supplied by a communal
electric grid
system 116 powered by a remote source external to the local environment; and
(3) electrical
energy produced by renewable energy resources 114, including photovoltaic
cells, wind
turbines, and/or geothermal generators.
24
CA 2970144 2017-06-09
Embodiments of such a system include a compressor (310, 320, and/or 315)
disposed
in a vapor compression or heat pump refrigeration cycle to cool and/or heat
the local
environment. The compressor may be powered by the mechanical energy form ICE
100, the
electrical energy, or selectively via both the mechanical and electrical
energy.
In some such embodiments, the system includes a heat pump (HP) composed of a
refrigerant circuit containing working fluid, a heat exchanger for
transferring heat from the
surrounding air into the working fluid, a heat exhausting exchanger for
transferring heat from
the working fluid to the surrounding air, compressor (310, 320, or 315) for
compressing and
cycling the working fluid, and a pressure lowering device to heat or cool the
local
environment.
The heat pump refrigerant may be cycled through the ICE 100 heat recovery unit
130,
thus allowing ICE 100 waste heat to be transferred to the working fluid of the
HP to augment
heat also recovered from HP heat exchanger. In some embodiments, the heat pump
refrigerant is cycled through the ICE 100 waste heat exhaust system, thus
allowing heat
within the working fluid to be expelled via both the HP exhaust exchanger and
ICE 100 heat
sinks, increasing the heat capacity of both the ICE 100 and HP subsystem. In
some
embodiments, a heat engine (e.g., 1510) is added to the refrigerant cycle,
allowing both ICE
100 waste heat and/or HP absorbed heat to be utilized to produce electrical or
mechanical
energy via the use of a conductive heat exchanger. The heat engine 1510 may be
a
thermoelectric device, such as a thermopile operating in accordance with the
thermoelectric
effect, generating an electromotive force via heat conduction through
dissimilar metals. In
other embodiments, the heat engine is a thermoacoustic heat engine producing a
resonant or
regenerative acoustic wave in a medium in response to a temperature
differential across said
medium.
Some embodiments of such a system include pump 1605; at least one heat
exchanger
(e.g., heat exchangers 1610, 1620, 1630); and a piping system (hot water
lines), which may
include flow control valves 1611, 1621, and 1631. Water may be heated by
transfer of heat
from ICE 100 through heat exchanger 510 for distribution to the local
environment. In some
embodiments, heat exchangers 1610, 1620, 1630 and plumbing may be staged to
produce
CA 2970144 2017-06-09
separate channels of varying water state such as liquid or steam. In certain
embodiments, hot
water supply may be tapped within the local environment for cooking and
drinking, and/or hot
water lines may be plumbed to automated washers, such as for cleaning
tableware and
clothes. In some such embodiments, the hot water lines may be plumbed to
radiative heaters
(e.g., space heater 1660), allowing internal heat energy within said water or
steam to be
transferred via conduction through said heat exchanger 1630 and radiate into
the surrounding
air to raise the temperature of the air in the local environment. The hot
water may be used to
heat the desiccant material of desiccant dehumidifier 800 within the local
environment, via
heat exchanger 1610. The hot water may be used to provide heat to boiler 1650
via heat
ex?hanger 1620.
Table 1, below, provides specifications available from operation of exemplary
systems
or embodiments as discussed above with respect to the Figures. Typical
coefficient of
performance (COP) values are provided, which are achievable with operation of
embodiments
of CCHP systems disclosed herein.
Table 1. Exemplary Coefficient of Performance (COP) Specifications
Combined Combined Cooling
Heat and Cooling, and Heat
Power Mode Heat, and Only Mode
Power Mode
Electrical 24.4% 21.0%
(DC)
Heating 56% 64% 72.7%
Cooling 57.6% 83.3%
Emissions data (from in-house emissions test):
= Fuel Consumption: 105,450 Btu/hr
= NOx: 51 ppm
= CO: 54 ppm
26
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= 02%: 13.3
= NOx (g/kW-h 15% 02): 0.26
= CO (g/kW-hr 15% 02): 0.17
Certain embodiments of the system according to the present disclosure utilize
waste
heat rejected to ambient surroundings by, for example, a traditional HVAC
system, for power
generation. Such captured waste heat may be directed and provided as an energy
source for an
Organic Rankine Cycle (ORC) system, and\or more specifically as a heat
transfer medium to
a working fluid (e.g., at constant pressure), where the working fluid may be
vaporized and
then expanded to transfer energy to a turbine or other energy component. Such
systems may:
1) use a gas driven engine (internal combustion engine 100) to run a
compressor (compressor
320 or 315) as opposed to an electrically driven compressor; 2) recover the
waste heat
generated by this gas driven process (heat recovery unit); and 3) feed the
waste heat from both
the HVAC cycle and the gas driven cycle into an ORC system through a two-stage
heating
system. This results in an ORC system that uses low-quality waste heat from
the HVAC
cycle for a first stage heating / pre-heating, before using the higher-quality
waste heat from
the gas driven process in a second stage heating process for the ORC fluid.
In one aspect, such a system uses the excess heat rejected by the ORC system
in the
condenser to further heat refrigerant in the HVAC system after it has
recovered heat from the
conditioned space of the local environment 1001 (e.g., home, refrigerator,
office space, tent,
etc.). A result is the raising of the pressure of the refrigerant, reducing
the high and low side
operating pressures, thus reducing the amount of work done by the compressor
320, which
may be at the expense of additional heat rejection capacity both in the HVAC
system
condenser and the excess heat dump 1700 of the ORC system. The HVAC system
134, thus,
operates as a regenerator with additional heat input for the ORC system. On
the low-pressure
side of the HVAC system, both the heat absorbed from the conditioned space
(heat input) and
at least some of the excess heat rejected by the ORC cycle is fed back into
the ORC system on
the high pressure side (regeneration). Such a combination ORC system with HVAC
driven
regenerator is limited to being gas driven, so long as there is an additional
source of heat input
27
CA 2970144 2017-06-09
for the ORC system. FIG. 17 depicts a schematic of a system or installation
utilizing such a
process, and specifically the capture of waste heat and transfer of energy to
the ORC system.
An exemplary or suitable application may be one for, or in, a data center
where there
is a consistent, substantial cooling load and consequently a large amount of
waste heat being
consistently generated. The proposed system operating in this application
would provide the
necessary cooling to the data center while producing electricity as a by-
product of the process.
Some embodiments provide for a method of use and/or operating any of the
systems
disclosed herein, and described with respect to FIGS. 1-17, to provide energy
(electrical
and/or mechanical); air conditioning (heating and/or cooling); electrical
energy resource
management, such as selective control over energy source, such as ICE 100,
electric generator
110, electric grid 116, battery storage 118, and/or renewable energy resources
114; waste heat
recovery; selective powering of cooling units, such as selectively driving a
compression in a
refrigerant cycle mechanically or electrically; evaporative cooling;
humidification and/or
dehumidification; water heating; powering an ORC system; or combinations
thereof.
Method of Generating Energy
Some embodiments include a method of generating energy for use in a local
environment (e.g., local environment 1001). The method includes operating an
internal
combustion engine (e.g., ICE 100). The method includes powering an electrical
generator
(e.g., electrical generator 110) using the internal combustion engine. The
method also
includes driving a compressor (e.g., compressor 310, 315, or 320) to compress
a working fluid
of a refrigeration cycle. In some embodiments of the method, waste heat is
generated, which
may be recovered.
Method of Driving a Compressor
Some embodiments include a method of driving a compressor of an air
conditioner to
meet localized demand. The method includes providing a local environment
(e.g., 1001)
having an air conditioning unit (e.g., cooling unit 132) for supplying cooled
air within the
local environment. The air conditioning unit may include a closed loop circuit
configured to
operate a closed loop refrigeration cycle, including a compressor (e.g., 310,
320 or 315)
operable to compress a working fluid of the closed loop circuit.
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The method includes selectively engaging an internal combustion engine (e.g.,
100)
with the compressor, and operating the internal combustion engine to drive the
compressor,
thereby transferring energy from the internal combustion engine to the
refrigeration cycle.
Method of Supplying Air Conditioned Air to a Residence
Some embodiments include a method of supplying air-conditioned air to a
residence
or other target space interior (local environment 1001). The method includes
positioning a
heat and mass exchanger (MHX 700) to discharge conditioned air into the
residence or target
space; positioning a rotatable desiccant wheel dehumidifier (desiccant
dehumidifier 800) in
fluid communication with the heat and mass exchanger; and receiving and
treating supply air
in the dehumidifier, thereby supplying dry air to the heat and mass exchanger
and exhausting
hot humid air. The heat and mass exchanger is positioned and configured to
receive dry air
from the dehumidifier, and to supply cooler dry air to the residence or target
space. The heat
and mass exchanger may be operated evaporative cooling mode, or in indirect
evaporative
cooling mode.
In some embodiment, the method includes communicating dry recycled air from
the
residence or target space as supply air received by the dehumidifier.
The method may include receiving outdoor air into the heat and mass exchanger
for
treatment.
Receiving supply air by the dehumidifier may include receiving dry recycled
air that is
less than about 80 to 85 degrees Fahrenheit, and, thereby, delivering dry air
that is above 100
degrees Fahrenheit to the heat and mass exchanger. The heat and mass exchanger
supplies
dry air at a temperature below about 78 degrees Fahrenheit to the residence or
target space.
The method may include positioning a second heat and mass exchanger, MHX 700a,
upstream of the dehumidifier, and operating the second heat and mass exchanger
to deliver
supply air to the dehumidifier and to receive return air from the residence or
target space and
outdoor air for treatment.
In certain embodiments, the method includes positioning a vacuum chamber on a
discharge side of the heat and mass exchanger, and drawing cool supply air
through the
vacuum chamber prior to discharge to the residence or target space. The method
may include
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positioning a vacuum chamber on an exhaust side of the heat and mass
exchanger, such that
exhaust air passes therethrough.
Method of Generating Electric Power and Providing Air Conditioning
Certain embodiments provide for a method of generating electric power and
providing
air conditioning in a localized installation (e.g., 1001). The method includes
providing a
hybrid power generator that includes an internal combustion engine (e.g., 100)
operatively
coupled to an electric generator (e.g., 110); operating the hybrid power
generator to generate
mechanical energy via the internal combustion engine and electrical energy via
the electric
generator; and driving at least one compressor of an air conditioning system
with the
mechanical energy generated via the internal combustion engine, with the
electrical energy
generated via the electric generator, or combinations thereof The compressor
compresses a
working refrigerant fluid of the air conditioning system.
In embodiments in which the at least one compressor is includes a single
compressor
that is operatively coupled to both the electric generator and the internal
combustion engine,
the method includes selectively engaging the electric generator with the
compressor to
electrically drive the compressor to compress the working refrigerant fluid,
and selectively
engaging the internal combustion engine with the compressor to mechanically
drive the
compressor to compress the working refrigerant fluid.
In embodiments in which the at least one compressor is includes a mechanically
driven compressor operatively to the internal combustion engine and an
electrically driven
compressor operatively coupled to the electric generator, the method includes
selectively
engaging the internal combustion engine with the mechanical compressor to
mechanically
drive the mechanical compressor to compress the working refrigerant fluid; and
selectively
engaging the electric generator with the electric compressor to electrically
drive the
compressor to compress the working refrigerant fluid.
In some embodiments, the method includes selectively driving the at least one
compressor with electrical energy from the electric generator, a battery
(e.g., 118), an electric
grid (e.g., 116), or a renewable energy resource (e.g., 114).
CA 2970144 2017-06-09
The air conditioning unit may include a vapor compression cooling subsystem
disposed in a refrigeration cycle with the at least one compressor, or a heat
pump disposed in
a refrigeration cycle with the at least one compressor. Certain embodiments
includes
transferring heat into the working fluid of the refrigeration cycle vial a
heat exchanger (e.g.,
510) thermally coupled with the internal combustion engine.
It should be noted and understood that many of the specific features or
combination of
features illustrated in or introduced above (or described in the claims
submitted below),
and\or discussed in accompanying descriptions, may be combined with or
incorporated with
or other feature(s) or embodiment(s) described or illustrated in any other
Figure provided
herein. Moreover, the following claims serve also to describe and illustrate
some (but not all)
aspects of the present disclosure. The claims serve therefore as an integral
part of the present
disclosure.
The foregoing description has been presented for purposes of illustration and
description of preferred embodiments. This description is not intended to
limit associated
concepts to the various systems, apparatus, structures, processes, and methods
specifically
described herein. For example, aspects of the processes and equipment
illustrated by the
Figures and discussed above may be employed or prove suitable for use with
other energy
systems, and energy handling or conversion systems and apparatus. The
embodiments
described and illustrated herein are further intended to explain the best and
preferred modes
for practicing the system and methods, and to enable others skilled in the art
to utilize same
and other embodiments and with various modifications required by the
particular applications
or uses of the present disclosure.
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