U.S. patent application number 15/618362 was filed with the patent office on 2018-03-29 for energy management apparatus, system and method.
The applicant listed for this patent is Donald Williams. Invention is credited to Donald Williams.
Application Number | 20180087786 15/618362 |
Document ID | / |
Family ID | 61687786 |
Filed Date | 2018-03-29 |
United States Patent
Application |
20180087786 |
Kind Code |
A1 |
Williams; Donald |
March 29, 2018 |
ENERGY MANAGEMENT APPARATUS, SYSTEM AND METHOD
Abstract
A system and method for power generation and/or distribution and
for providing air conditioning is disclosed, that is particularly
suitable for localized consumption. Power generation includes a
combined cooling, heating and power system (CCHP) containing a gas
or liquid fueled internal combustion engine with a generator and
heat recovery system for providing electrical power and heat for
local consumption. The CCHP system includes an integrated cooling
system for cooling a local environment, using either vapor
compression and/or heat pump and/or evaporative cooling technology.
The CCHP system also contains an energy management unit allowing
CCHP system and local area electrical needs in whole or in part to
be powered by either the CCHP generator and/or a communal
electrical grid and/or renewable energy sources and/or a battery
storage network.
Inventors: |
Williams; Donald; (The
Woodlands, TX) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Williams; Donald |
The Woodlands |
TX |
US |
|
|
Family ID: |
61687786 |
Appl. No.: |
15/618362 |
Filed: |
June 9, 2017 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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14461962 |
Aug 18, 2014 |
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15618362 |
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62348267 |
Jun 10, 2016 |
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61867571 |
Aug 19, 2013 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F25B 41/04 20130101;
F25B 2339/041 20130101; F25B 2400/075 20130101; F24F 2203/104
20130101; F25B 2313/02543 20130101; Y02A 30/274 20180101; F25B
2400/0403 20130101; F24F 2221/34 20130101; F25B 27/00 20130101;
F25B 13/00 20130101; F25B 39/04 20130101; F24F 2203/1032 20130101;
F24F 3/1423 20130101; F25B 25/005 20130101; F25B 2339/047 20130101;
F25B 2600/2507 20130101; F24F 5/0035 20130101; F25B 21/02 20130101;
Y02B 30/54 20130101; F24F 3/147 20130101; F25B 2327/001 20130101;
F25B 27/02 20130101; F25B 2700/02 20130101 |
International
Class: |
F24F 3/14 20060101
F24F003/14; F24F 3/147 20060101 F24F003/147 |
Claims
1. (canceled)
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18. A method of supplying air-conditioned air to a residence or
other target space interior, said method comprising: positioning a
heat and mass exchanger to discharge conditioned air into the
residence or target space; positioning a rotatable desiccant wheel
dehumidifier 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; wherein the heat and mass
exchanger is positioned and configured to received dry air from the
dehumidifier and supply cooler dry air to the residence or target
space.
19. The method of claim 18, further comprising communicating dry
recycled air from the residence or target space as supply air
received by the dehumidifier.
20. The method of claim 18, further comprising receiving outdoor
air into the heat and mass exchanger for treatment.
21. (canceled)
22. The method of claim 18, further comprising: positioning a
second heat and mass exchanger 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.
23. The method of claim 18, further comprising positioning a vacuum
chamber on a discharge side of the heat and mass exchanger and
drawing said cool supply air through the vacuum chamber prior to
discharge to the residence or target space.
24. (canceled)
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44. (canceled)
45. A system for generating electric power and providing air
conditioning in a localized installation, the system comprising: a
hybrid power generator, the hybrid power generator including an
internal combustion engine operatively coupled to an electric
generator; and an air conditioning system, the air conditioning
system including at least one compressor; wherein the at least one
compressor is operatively coupled to the hybrid power generator,
whereby the hybrid power generator is engageable with the
compressor to compress a working refrigerant fluid.
46. The system of claim 45, wherein the at least one compressor is
includes a single compressor that is operatively coupled to both
the electric generator and the internal combustion engine, whereby
the electric generator is selectively engageable with the
compressor to electrically drive the compressor to compress the
working refrigerant fluid, and whereby the internal combustion
engine is selectively engageable with the compressor to
mechanically drive the compressor to compress the working
refrigerant fluid.
47. The system of claim 45, wherein the at least one compressor is
includes: a mechanically driven compressor operatively to the
internal combustion engine, whereby the internal combustion engine
is selectively engageable with the mechanical compressor to
mechanically drive the mechanical compressor to compress the
working refrigerant fluid; an electrically driven compressor
operatively coupled to the electric generator, whereby the electric
generator is selectively engageable with the electric compressor to
electrically drive the compressor to compress the working
refrigerant fluid; or combinations thereof.
48. The system of claim 45, wherein the electric generator is
electrically coupled to an electrical energy convertor, and wherein
the electrical energy convertor is electrically couple to battery
storage, an electric grid, a renewable energy resource, or
combinations thereof.
49. (canceled)
50. The system of claim 45, wherein the air conditioning unit
includes a vapor compression cooling subsystem disposed in a
refrigeration cycle with the at least one compressor.
51. The system of claim 45, wherein the air conditioning unit
includes a heat pump disposed in a refrigeration cycle with the at
least one compressor.
52. The system of claim 51, further comprising a heat recovery unit
in fluid communication with the refrigeration cycle of the heat
pump, wherein the heat recovery unit includes a first heat
exchanger thermally coupled with the internal combustion
engine.
53. The system of claim 52, wherein the heat recovery unit further
comprises a second heat exchanger thermally coupled with an exhaust
of the internal combustion engine.
54. (canceled)
55. The system of claim 52, wherein the heat recovery unit further
comprises a second heat exchanger downstream of the first heat
exchanger and a heat engine fluidly coupled between the first and
second heat exchangers.
56. The system of claim 55, wherein said heat engine is a adapted
to generate an electromotive force via heat conduction through
dissimilar metals, or wherein said heat engine is a thermoacoustic
heat engine adapted to produce a resonant or regenerative acoustic
wave in a medium in response to a temperature differential across
said medium.
57. (canceled)
58. The system of claim 52, further comprising a pump fluidly
coupled with, and downstream of, the first heat exchanger, wherein
the pump is in fluid communication with at least one water
condenser.
59. The system of claim 58, wherein the at least one water
condenser includes: a first water condenser thermally coupled with
a desiccant dehumidifier; a second water condenser thermally
coupled with a boiler; a third water condenser thermally coupled
with a radiant space heater; or combinations thereof.
60. The system of claim 58, wherein the at least one water
condenser includes a first water condenser thermally coupled with a
desiccant dehumidifier, the desiccant dehumidifier in fluid
communication with a heat and mass exchanger.
61. A method of generating electric power and providing air
conditioning in a localized installation, the method comprising:
providing a hybrid power generator, the hybrid power generator
including an internal combustion engine operatively coupled to an
electric generator; operating the hybrid power generator to
generate mechanical energy via the internal combustion engine and
electrical energy via the electric generator; 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, wherein the compressor compresses a working refrigerant
fluid of the air conditioning system.
62. (canceled)
63. (canceled)
64. The method of claim 61, further comprising selectively driving
the at least one compressor with electrical energy from the
electric generator, a battery, an electric grid, or a renewable
energy resource.
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Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] The present application claims the benefit of U.S.
Provisional Patent Application No. 62/348,267, filed on Jun. 10,
2016 (pending), the entirety of which is incorporated herein by
reference for all purposes and made a part of the present
disclosure. The present application also claims the benefit, as a
Continuation-in-Part, of U.S. patent Ser. No. 14/461,962, filed on
Aug. 18, 2014 (pending), which claims priority to U.S. Provisional
Patent Application No. 61/867,571, filed on Aug. 19, 2013
(expired), the entireties of which are incorporated herein by
reference for all purposes and made a part of the present
disclosure.
FIELD
[0002] 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
[0003] Each of U.S. 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 Aug. 18, 2014, and published as U.S.
2015/0128625), and U.S. patent application Ser. No. 14/314,771
(entitled "Power Generation System and Method", filed on Jun. 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, and are, therefore, hereby
incorporated by reference for all purposes and made a part of the
present disclosure.
[0004] 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 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.
[0005] 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.
[0006] 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
[0007] 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.
[0008] 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.
[0009] 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
[0010] 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.
[0011] 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;
[0012] FIG. 2 is a simplified schematic of an electrical resource
management system according to the present disclosure;
[0013] 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;
[0014] 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;
[0015] 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;
[0016] 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;
[0017] 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;
[0018] 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;
[0019] 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;
[0020] 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;
[0021] 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;
[0022] FIG. 4d is a simplified schematic of a power generation and
distribution system installation, including a CCHP employing a
hybrid, single compressor and heat pump configuration, according to
the present disclosure;
[0023] 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;
[0024] 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;
[0025] 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;
[0026] 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;
[0027] 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;
[0028] 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;
[0029] 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;
[0030] 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;
[0031] 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;
[0032] 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;
[0033] FIGS. 9a-9c are simplified illustrations of an exemplary
installation including a CCHP heater, dehumidifier, and mass heat
exchanger according to the present disclosure;
[0034] FIGS. 10a-10e are simplified illustrations of flow patterns
associated with an exemplary installations including a mass heat
exchanger according to the present disclosure;
[0035] FIGS. 11a-11d are simplified illustrations of flow patterns
associated with exemplary installations, according to the present
disclosure;
[0036] 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;
[0037] 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;
[0038] 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;
[0039] 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;
[0040] 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
[0041] 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
[0042] 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 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.
[0043] 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.
[0044] 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.
[0045] 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. 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.
[0046] 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.
[0047] 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.
[0048] The electrical energy converter 115 also includes a grid
conditioning subsystem with a transformer assembly 109 providing
galvanic isolation and conditioning circuitry 106 that 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.
[0049] 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.
[0050] 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.
[0051] 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.
[0052] 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.
[0053] 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.
[0054] 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.
[0055] 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.
[0056] 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 electrical energy converter 115, and is
mechanically coupled to the internal combustion engine 100 via the
engine crankshaft 101 and drive system 300.
[0057] 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.
[0058] 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.
[0059] 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.
[0060] 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 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.
[0061] 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 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.
[0062] 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.
[0063] 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
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.
[0064] 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 U.S. patent
Ser. No. 14/461,962, and correspond to FIGS. 19A-19E of U.S. patent
Ser. 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.
[0065] 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.
[0066] As describe in more detail below, the MHX 700 may be
configured into: [0067] Air Pass Through mode [0068] Direct
Evaporative Cooling (DEC) or Swamp Cooling mode (e.g., FIG. 10a)
[0069] Indirect Evaporative Cooling (IEC) or Dew Point Cooling mode
(e.g., FIG. 10c) [0070] Combination DEC/IEC mode (e.g., FIG.
10d)
[0071] 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: [0072] Increased evaporative air
flow [0073] Modulated preheating of working air [0074] Increased
evaporation surface [0075] Dehumidification of both working and
process air [0076] Water (refrigerant) treatment [0077] Vacuum
creation to reduce dew point temperature
[0078] 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 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 116b (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.
[0079] 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 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.
[0080] 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.
[0081] 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.
[0082] 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.
[0083] 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 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.
[0084] 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.
[0085] 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.
[0086] FIGS. 11a-11d depict various airflow patterns and quality
within the local environment resulting from various system
configurations. FIGS. 11a-11d 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.
11a-11d, respectively. FIG. 11a 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 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. 11b
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. 11d depicts an airflow pattern
utilizing heat pipes.
[0087] 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).
[0088] 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.
[0089] 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 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.
[0090] 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.
[0091] 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.
[0092] 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 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.
[0093] 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.
[0094] 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.
[0095] 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.
[0096] 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 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.
[0097] 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.
[0098] 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.
[0099] 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.
[0100] 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.
[0101] 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
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 exchanger 1620.
[0102] 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-US-00001 TABLE 1 Exemplary Coefficient of Performance (COP)
Specifications Combined Combined Cooling Heat and Cooling, and Heat
Power Heat, and Only Mode Power Mode Mode Electrical 24.4% 21.0% --
(DC) Heating 56% 64% 72.7% Cooling -- 57.6% 83.3%
[0103] Emissions data (from in-house emissions test): [0104] Fuel
Consumption: 105,450 Btu/hr [0105] NOx: 51 ppm [0106] CO: 54 ppm
[0107] O2%: 13.3 [0108] NOx (g/kW-h 15% O2): 0.26 [0109] CO
(g/kW-hr 15% O2): 0.17
[0110] 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/preheating,
before using the higher-quality waste heat from the gas driven
process in a second stage heating process for the ORC fluid.
[0111] 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 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.
[0112] 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.
[0113] 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.
[0114] Method of Generating Energy
[0115] 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.
[0116] Method of Driving a Compressor
[0117] 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.
[0118] 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.
[0119] Method of Supplying Air Conditioned Air to a Residence
[0120] 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.
[0121] In some embodiment, the method includes communicating dry
recycled air from the residence or target space as supply air
received by the dehumidifier.
[0122] The method may include receiving outdoor air into the heat
and mass exchanger for treatment.
[0123] 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.
[0124] 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.
[0125] 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
positioning a vacuum chamber on an exhaust side of the heat and
mass exchanger, such that exhaust air passes therethrough.
[0126] Method of Generating Electric Power and Providing Air
Conditioning
[0127] 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.
[0128] 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.
[0129] 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.
[0130] 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).
[0131] 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.
[0132] 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.
[0133] 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.
* * * * *