U.S. patent application number 10/961942 was filed with the patent office on 2005-04-14 for cryogenic cogeneration system.
Invention is credited to Shirk, Mark A., Storck, Gary A. JR., Weigel, Wesley W..
Application Number | 20050076639 10/961942 |
Document ID | / |
Family ID | 34465217 |
Filed Date | 2005-04-14 |
United States Patent
Application |
20050076639 |
Kind Code |
A1 |
Shirk, Mark A. ; et
al. |
April 14, 2005 |
Cryogenic cogeneration system
Abstract
A cryogenic and thermal source cogeneration method for
converting energy from a heat source, through a cryogenic heat
transfer process, into mechanical and/or electrical energy,
comprising, utilizing a vapor compression cycle to absorb heat from
the heat source and, utilizing a Rankine cycle for energy transfer,
for converting thermal energy to mechanical and/or electrical
energy. A cryogenic and thermal source cogeneration apparatus for
converting energy from a heat source, through a cryogenic heat
transfer process, into mechanical and/or electrical energy is also
disclosed, comprising, vapor compression cycle mechanisms to absorb
heat from the heat source, and Rankine cycle mechanisms for energy
transfer, for converting thermal energy to mechanical and/or
electrical energy. The Rankine cycle mechanisms being operably
linked to the vapor compression cycle mechanisms.
Inventors: |
Shirk, Mark A.; (Boulder
Creek, CA) ; Storck, Gary A. JR.; (Los Altos, CA)
; Weigel, Wesley W.; (Cupertino, CA) |
Correspondence
Address: |
JEFFREY HALL
212 CLINTON ST
SANTA CRUZ
CA
95062
US
|
Family ID: |
34465217 |
Appl. No.: |
10/961942 |
Filed: |
October 8, 2004 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
60511292 |
Oct 14, 2003 |
|
|
|
Current U.S.
Class: |
60/520 |
Current CPC
Class: |
Y02E 10/46 20130101;
F01K 25/08 20130101; F02G 1/04 20130101; F03G 6/005 20130101 |
Class at
Publication: |
060/520 |
International
Class: |
F02G 001/04; F01B
029/10 |
Claims
What is claimed is:
1. A cryogenic cogeneration method for converting energy from a
heat source, through a cryogenic heat transfer process, into
mechanical and/or electrical energy, comprising: utilizing a vapor
compression cycle to absorb heat from said heat source; and,
utilizing a Rankine cycle for energy transfer, for converting
thermal energy to mechanical and/or electrical energy.
2. The method of claim 1, wherein said Rankine cycle includes
utilizing means for conversion of thermal energy into mechanical
and/or electrical energy, including energy absorption and rejection
means to transfer substantial thermal energy from said heat source
to said Rankine cycle, and recycling means for transfer of thermal
energy to and from said vapor compression cycle.
3. The method of claim 1, further including utilizing said vapor
compression cycle with energy absorption and rejection means for
transfer of thermal energy from said heat source to said Rankine
cycle and/or for transfer of energy via transfer to and from said
Rankine cycle.
4. The method of claim 1, further including utilizing a heat
transfer medium in said Rankine cycle.
5. The method of claim 1, further including utilizing a refrigerant
in said Rankine cycle.
6. The method of claim 1, further including utilizing a heat
transfer medium in said vapor compression cycle.
7. The method of claim 1, further including utilizing a refrigerant
in said vapor compression cycle.
8. The method of claim 4, further including utilizing a
thermosiphonic flow stimulated by gravity and natural convection to
circulate said heat transfer medium.
9. The method of claim 5, further including utilizing a
thermosiphonic flow stimulated by gravity and natural convection to
circulate said refrigerant.
10. The method of claim 6, further including utilizing a
thermosiphonic flow stimulated by gravity and natural convection to
circulate said heat transfer medium.
11. The method of claim 7, further including utilizing a
thermosiphonic flow stimulated by gravity and natural convection to
circulate said refrigerant.
12. The method of claim 1, further including utilizing means to
compress and/or superheat a heat transfer medium and/or refrigerant
by passive natural isothermal and/or exothermal processes.
13. The method of claim 1, further including utilizing means for
maintaining a predetermined continuous constant pressure output
and/or flow through a sequenced method of simultaneous and/or
parallel implementation of passive natural isothermal and/or
exothermal processes, using a passive parallel compressors.
14. The method of claim 1, further including utilizing means for
broadening both range and control of pressures and/or flows using a
blowdown cycle.
15. The method of claim 1, further including utilizing means for
broadening both range and control of pressures and/or flows using a
blowdown vacuum heat sink.
16. The method of claim 1, further including utilizing means for
broadening both range and control of pressures and/or flows using
parallel passive volume reduction compressors.
17. The method of claim 1, further including utilizing means to
increase a buoyant vessel lifting capacity using avionic lifting
means.
18. The method of claim 14, further including utilizing means for
broadening said range and control of pressures and/or flows by
utilizing a volume reduction compressor.
19. A cryogenic cogeneration apparatus for converting energy from a
heat source, through a cryogenic heat transfer process, into
mechanical and/or electrical energy, comprising: vapor compression
cycle means to absorb heat from said heat source; and, Rankine
cycle means for energy transfer, for converting thermal energy to
mechanical and/or electrical energy, said Rankine cycle means being
operably linked to said vapor compression cycle means.
20. The apparatus of claim 19, wherein said vapor compressor cycle
means includes a heat transfer medium.
21. The apparatus of claim 19, wherein said Rankine cycle means
includes a heat transfer medium.
22. The apparatus of claim 19, wherein said vapor compressor cycle
means includes a refrigerant.
23. The apparatus of claim 19, wherein said Rankine cycle means
includes a refrigerant.
24. The apparatus of claim 20, further means for creating a
thermosiphonic flow stimulated by gravity and natural convection to
circulate said heat transfer medium.
25. The apparatus of claim 22, further including means for creating
a thermosiphonic flow stimulated by gravity and natural convection
to circulate said refrigerant.
26. The apparatus of claim 21, further including means for creating
a thermosiphonic flow stimulated by gravity and natural convection
to circulate said heat transfer medium.
27. The apparatus of claim 23, further including means for creating
a thermosiphonic flow stimulated by gravity and natural convection
to circulate said refrigerant.
28. The apparatus of claim 19, further including means to compress
and/or superheat a heat transfer medium and/or refrigerant by
passive natural isothermal and/or exothermal processes.
29. The apparatus of claim 19, further including means for
maintaining a predetermined continuous constant pressure output
and/or flow through a sequenced method of simultaneous and/or
parallel implementation of passive natural isothermal and/or
exothermal processes, using a passive parallel compressor.
30. The apparatus of claim 19, further including means for
broadening both range and control of pressures and/or flows using a
blowdown cycle.
31. The apparatus of claim 19, further including means for
broadening both range and control of pressures and/or flows using a
blowdown vacuum heat sink.
32. The apparatus of claim 19, further including means for
broadening both range and control of pressures and/or flows using
parallel passive volume reduction compressors.
33. The method of claim 19, further including means to increase a
buoyant vessel lifting capacity using avionic lifting means.
34. The method of claim 30, further including means for broadening
said range and control of pressures and/or flows by utilizing a
volume reduction compressor.
35. The apparatus of claim 19, further including a motorized
mechanical driven compressor and motorized mechanical driven
blower, for flow circulation.
36. A thermal source cogeneration method for converting energy from
a heat source, through a heat transfer process, into mechanical
and/or electrical energy, comprising: utilizing a vapor compression
cycle to absorb heat from said heat source; and, utilizing a
Rankine cycle for energy transfer, for converting thermal energy to
mechanical and/or electrical energy.
37. The method of claim 36, further including utilizing means for
broadening both range and control of pressures and/or flows using a
blowdown cycle, and further utilizing means for conversion of
thermal energy into mechanical and/or electric energy using an
expansion engine.
38. The method of claim 37, further including utilizing means for
re-introducing the blowdown cycle heat transfer medium into a vapor
compression cycle for conversion of thermal energy into mechanical
and/or electric energy using an expansion engine and a blowdown
heat sink.
39. A thermal source cogeneration apparatus for converting energy
from a heat source, through a cryogenic heat transfer process, into
mechanical and/or electrical energy, comprising: vapor compression
cycle means to absorb heat from said heat source; and, Rankine
cycle means for energy transfer, for converting thermal energy to
mechanical and/or electrical energy, said Rankine cycle means being
operably linked to said vapor compression cycle means.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application is related to and claims priority from
Provisional Patent Application Ser. No. 60/511,292, filed Oct. 14,
2003.
FIELD OF INVENTION
[0002] This invention relates to methods and apparatuses for
converting thermal energy to mechanical and/or electrical
energy.
DESCRIPTION OF THE RELATED ART
[0003] Heretofore, numerous methods and apparatuses have been
developed for production of mechanical and electrical energy,
however difficulties and limitations are inherent in all of them.
For example, electrical power plants utilizing high priced fossil
fuel to generate electricity are emitting greenhouse gases that
scientists claim to be the greatest contributor to the global
warming problem. It is predicted that this will have a significant
negative impact on our environment within the next 50 years.
[0004] Plants utilizing dams/water reservoirs, to produce
hydroelectricity, also will impact our environment due to the
necessity to flood surrounding inhabited land resources. In
addition, water resources are depleted to suffice electrical
demands.
[0005] The accidents in Chernobyl, in the Soviet Union, and 3 Mile
Island, in the United States, have proven Nuclear power through
history to be very unhealthy and potentially fatal to people within
surrounding areas. An effective means of disposing nuclear waste
has not been established. Nuclear power, still consumes uranium,
and has limited capacity due to the necessity to operate at lower
pressures for safety reasons.
[0006] Chlorofluorohydrocarbon (CFC) emissions from existing
refrigeration and air conditioning systems have been depleting our
Earth's ozone layer, which is believed to be the cause of many
illnesses attributed to harmful radiation entering our
atmosphere.
[0007] Further, growing problems associated with energy production
and supplies that are continuing to decrease the health of our
planet include negative effects as a result of the greenhouse
effect, the depletion of the Earth's ozone layer, nuclear waste
disposal, and the many other adverse effects, including loss of
life and land, that are attributed to the fossil fuel industry
(war, oil tanker spills, offshore drilling, land destruction as a
result of coal mining, etc.) and land flooding from the building of
dams. Economic problems also will continue to grow as consumable
energy resources become more scarce and as a result of the cost of
the necessary upgrading of old, power generation and grid systems
in developed countries.
[0008] In addition, as China's and India's industrial development
continues to grow at an accelerated pace power consumption and
demand increases. Experts anticipate that China alone will soon
consume more oil than the United States. Present estimates by
experts are that our planet's oil resources will deplete within 32
years.
[0009] Fossil fuel burning, and many other presently known
mechanical engines in use today also present problems for the
defense Industry. One problem is that all of these engines release
residual heat that is detectable by the infrared heat sensors.
[0010] Many other technologies have been developed to try to solve
the problem of finding an environmentally friendly, safe, and
economically efficient method to generate electricity, achieve
energy consuming mechanical functions (i.e. for transportation,
industrial manufacturing, etc.) and provide refrigeration, cooling,
and air conditioning functions. The following is a list of some of
those technologies and some of their associated benefits and
liabilities:
[0011] (a) Bio Mass generation is another way to produce
electricity than coal and oil burning power generation plants. But
as fossil fuel plants do, bio mass generation also emits harmful
gases into our atmosphere, again negatively impacting our
environment.
[0012] (b) Wind turbine generation is probably the best existing
technology implemented today but has limited capacity capabilities,
requires considerable initial investments, utilizes considerable
amount of land and it is not aesthetically pleasing to many. It is
also dependent on weather conditions and geographical
locations.
[0013] (c) Solar thermal and solar photovoltaic power generation is
limited due to its dependency on weather conditions and
availability of sunlight. Collector arrays again have to consume
large surface areas of property to generate a reasonable amount of
power. This is attributed to the fact that solar rays produces a
limited amount of Btu's per sq. ft depending upon the time of day
and geographical location. This also requires extra expense and
maintenance costs attributed to the necessary installation of large
thermal or chemical energy storage systems, that are typically
coupled with them.
[0014] (d) Hydrogen Fuel Cells do not emit harmful gases into our
atmosphere but other hazardous conditions exist due to the
extremely explosive properties of hydrogen. Also unlike biomass,
wind turbines, and solar, this alternative requires consumption of
hydrogen and it is not economically efficient to completely modify
our infrastructure to make our society dependent on hydrogen, as it
is dependent on fossil fuel today. Present technology requires
costly energy consumption to liquify the hydrogen.
[0015] (e) Several cryogenic energy systems utilizing an expansion
engine have been proposed. For example, in U.S. Pat. No. 4,170,116,
a method and apparatus for converting thermal energy to mechanical
energy is disclosed. In U.S. Pat. No. 4,896,515, a heat pump energy
recovery method and method of curtailing power for driving a
compressor in a heat pump is disclosed. However, both these
technologies require mechanical motor driven compressor(s) and/or
pump(s) that consume more energy than the system can produce in net
shaft work output which requires an external power generation
source for supplemental energy input, and the internal latent heat
of the system is rejected to an external heat sink rendering it
wasted energy.
[0016] In U.S. Pat. No. 4,624,109 a condensing atmospheric engine
is disclosed. The technology proposes to inject and/or extract air
directly from the atmosphere into a specially designed vacuum
chamber maintaining a deep vacuum created by a mechanical vacuum
pump supplemented by an expansion engine. The air is isentropcally
expanded to stimulate a phase transformation of condensation to a
solid state which is also assumed to supplement the vacuum process
and provide a latent heat sink.
[0017] In SAE Series #981898 and #972649 technical papers on the
Quasi-Isothermal Expansion Engine and appurtenances that power the
Cryocar LN2000 developed by the University of Washington, disclose
an engine using liquid air and combustible fuel. In U.S. Pat. No.
3,681,609, a non-polluting motor, including cryogenic fluid as the
motive means is disclosed.
[0018] Significant problems and limitations accompany all such
technology, For example, the Cryocar LN2000 extracts stored liquid
nitrogen an open loop system which consists of an evaporator,
superheater and an expansion engine to create shaft work coupled to
propel and/or power the vehicle. The residual sensible and latent
heat and all the nitrogen is wasted as it is exhausted to the
atmosphere. Therefore, the liquid nitrogen is consumed and has to
be replenished. In similarity to the hydrogen fuel cell technology,
this system, as it is presently developed, is not economically
efficient. Further, being that it requires completely modifying our
infrastructure to make our society dependent on nitrogen, as
opposed to the current dependency on fossil fuel today, its
practicality is very limited. Further, such prior technology
requires costly energy consumption, that can include fossil fuel,
to liquify the nitrogen.
[0019] Accordingly, several objects and advantages of our the
present cryogenic cogeneration system are:
[0020] (a) to provide a closed loop system that generates
power/mechanical energy without emitting any harmful gasses to the
atmosphere, while providing a heat sink for other applications, and
does not require an additional heat sink.
[0021] (b) to provide an independent system with minimal/limited
land use needed and no requirements for specific geographic
locations and weather conditions.
[0022] (c) to provide a safe system that can operate with inert,
non-explosive, non-poisonous gases.
[0023] (d) to provide a system that does not directly and/or
indirectly consume and deplete scarce/non-renewable energy
resources for its operation and will also provide the opportunity
for society to be independent of consumable resources.
[0024] (e) to provide a natural convection, thermosiphonic
iso/exothermal compression process in the vapor compression cycle
requiring only free thermal energy input to achieve the necessary
work. After the free thermal energy is converted to work, the
residual sensible and latent heat energy and the refrigerant medium
can be recycled as it is condensed from the vapor and/or gas state
back into the liquid state, allowing energy conservation, and
minimizing society's dependency on the existing expensive
consumable energy infrastructure.
[0025] Further objects and advantages are to provide the ability
for almost any medium that contains thermal energy to provide the
energy input to the system to produce net work output; to provide
the conversion of thermal energy (heat) to mechanical and/or
electrical energy; to provide an inexpensive, environmentally safe
alternative form of transportation, with only renewable energy
consumption. The method and apparatus can be applied to trucks,
trains, ships, planes, and the like; to provide electricity; to
provide environmental control systems, for example air
conditioning, refrigeration, cryogenics, and the like. The present
invention can be utilized in cryogenic applications for
liquification of gases such as nitrogen, hydrogen, helium, methane,
and the like; laboratory and semiconductor applications, and
medical applications (such as cryonics, etc), which reduce the
expensive costs of electricity consumption that is presently needed
for existing systems. Still further applications include use in
power plants, where such technology is scalable up to the largest
multi-megawatt power generation plant that mankind can conceive and
construct. Specific geographical locations, environmental hazards,
fossil fuel and/or water consumptions are not necessary. All that
is needed is air or other equivalent heat source(s). The present
system may also be used to provide cogeneration for many industrial
facilities and computer server farms have large quantities of waste
heat that has been, in most cases, a liability to operations. With
the subject technology, these liabilities can be turned into an
asset while becoming a supplemental heat source to generate power.
The disclosed technology can also partner with existing renewable
energy projects such as solar, bio-mass, geo-thermal, etc.,
competitively increase their capacity to far exceed the capacities
of existing fossil fuel power generation facilities.
[0026] As well as a mobile power source, (eliminating the need to
carry and replenish fuel supplies), the subject technology can be
combined with other new technologies recently conceived. For
example, such technology creates an opportunity to enhance replace
existing rotocraft technology by decreasing diameters of
propellers/rotors and still lift the same amount of weight that the
larger propellers/rotors lift today. Such technology may also be
used to provide water distillation/purification, extraction and
reserve storage.
[0027] With the cryogenic cogeneration system and thermal source
cogeneration disclosed herein, including both method and apparatus,
the environment is safe from emissions, hazardous waste, flooding
of valuable property and no particular geographic location is
necessary to implement it. This system consumes no water, no fuel,
no storage, and no chemical treatment and is not dependant on
weather conditions. It can also be utilized in water, land, and
aerospace transportation systems.
[0028] Additional objects and advantages of the invention will be
set forth in the description which follows, and in part will be
obvious from the description, or may be learned by practice of the
invention. The objects and advantages of the invention may be
realized and obtained by means of apparatus, methods, and
combinations particularly pointed out in the appended claims.
SUMMARY OF THE INVENTION
[0029] The present invention is a cryogenic cogeneration method and
a thermal source cogeneration system for converting energy from a
heat source, through a cryogenic or thermal source heat transfer
process, into mechanical and/or electrical energy utilizing a vapor
compression cycle to absorb heat from a heat source, and utilizing
a Rankine cycle for energy transfer, for converting thermal energy
to mechanical and/or electrical energy. The two cycles preferably
operate as closed loops and complement each other's cycle. A
cryogenic cogeneration apparatus and a thermal source cogeneration
apparatus for converting energy from a heat source, through a
cryogenic or thermal source heat transfer process, into mechanical
and/or electrical energy is also disclosed, comprising, vapor
compression cycle mechanisms to absorb heat from the heat source,
and Rankine cycle mechanisms for energy transfer, for converting
thermal energy to mechanical and/or electrical energy, the Rankine
cycle mechanisms being operably linked to the vapor compression
cycle mechanisms.
BRIEF DESCRIPTION OF THE DRAWINGS
[0030] The accompanying drawings, which are incorporated in and
constitute a part of the specification, illustrate a preferred
embodiment of the invention and, together with a general
description given above and the detailed description of the
preferred embodiment given below, serve to explain the principles
of the invention.
[0031] FIG. 1 shows, in a preferred embodiment, a cryogenic
cogeneration or thermal source system having a vapor compression
cycle and a Rankine Cycle, according to the invention.
[0032] FIG. 1A shows an example of one of many possible ranges of
parameters within a pressure and enthalpy diagram for the proposed
cryogenic or thermal source cogeneration system, according to the
invention.
[0033] FIG. 2-1 and 2-2, shows embodiments including modified
versions of a vapor compression cycle and a Rankine cycle with a
liquid mechanical pump added to the Rankine cycle, a passive
parallel compressor superheater assembly, blowdown expansion
engine, and blowdown heat sink incorporated into the vapor
compression cycle, according to the invention.
[0034] FIG. 3-1 and 3-2 show an optional summary of additional
embodiments including the modified versions of the vapor
compression cycle and the Rankine cycle with the liquid mechanical
pump added to the Rankine cycle, the passive parallel compressor
superheater assembly, a blowdown vacuum diffusion injector system,
a blowdown cycle, and a blowdown vacuum heat sink, according to the
invention.
[0035] FIG. 4-1 and FIG. 4-2 show an optional additional embodiment
including a passive parallel reducing volume compressor subsystem
with flow inducing heat exchangers, according to the invention.
[0036] FIG. 5-1 and FIG. 5-2 show an optional additional embodiment
including the vapor compression cycle and/or the Rankine Cycle
utilizing existing motorized mechanical driven pumps, compressors,
and blowers for flow circulation and an optional desiccant
dehumidification system(s) that can regenerate via the use of an
optional solar collector array, according to the invention.
REFERENCE NUMERALS IN DRAWINGS
[0037] 2--Vapor compression cycle
[0038] 4--Rankine cycle
[0039] 6--Rankine cycle refrigerant medium
[0040] 7--Rankine cycle liquid evaporator/superheater reservoir
[0041] 8--vapor compression refrigerant medium
[0042] 10--vapor compression reservoir liquid receiver
[0043] 11--expansion/compression tanks
[0044] 12--vapor compression metering device
[0045] 14--vapor compression sub cooler
[0046] 16--vapor compression evaporator outlet
[0047] 18--vacuum insulated check valve
[0048] 19--vacuum insulated tee fitting
[0049] 19a--tee
[0050] 19b--tee
[0051] 19c--tee
[0052] 19d--tee
[0053] 19f--tee
[0054] 19h--tee
[0055] 19k--tee
[0056] 19l--tee
[0057] 19m--tee
[0058] 19n--tee
[0059] 20--cryogenic automated isolation valve
[0060] 20n--valve
[0061] 20o--valve
[0062] 2Op--valve
[0063] 21--vacuum insulated piping
[0064] 22--vapor compression super heater
[0065] 25--vapor compression mixed gas
[0066] 27--high pressure regulator valve
[0067] 27a--valve
[0068] 27b--valve
[0069] 27c--valve
[0070] 27d--valve
[0071] 27f--valve
[0072] 27n--valve
[0073] 28--high pressure piping
[0074] 30--vapor compression precondenser
[0075] 35--vapor compression condenser outlet
[0076] 40--vapor compression subcooler outlet
[0077] 45--blowdown expansion valve
[0078] 50--blowdow
[0079] 55--blowdown vacuum evaporator
[0080] 60--blowdown vacuum superheater gas
[0081] 65--blowdown vacuum mixed gas
[0082] 70--blowdown vacuum control valve
[0083] 75--blowdown vacuum
[0084] 80--blowdown vacuum compressor outlet
[0085] 85--blowdown vacuum diffusion ejector (liquid
entrainment)
[0086] 90--blowdown liquid receiver
[0087] 95--blowdown liquid pump discharge
[0088] 97--blowdown liquid pump bypass regulating valve
[0089] 100--blowdown evaporator coil
[0090] 105--blowdown super heater
[0091] 110--blowdown mixed gas
[0092] 112--blowdown vacuum engine bypass valve
[0093] 115--blowdown expansion engine
[0094] 120--blowdown condenser
[0095] 125--blowdown heat sink
[0096] 125a--blowdown condenser liquid
[0097] 125b--vacuum diffusion ejector liquid
[0098] 130--Rankine cycle liquid receiver
[0099] 135--Rankine cycle liquid pump discharge (cryogenic)
[0100] 140--Rankine cycle evaporator outlet
[0101] 145--Rankine cycle superheater outlet
[0102] 150--Rankine cycle expansion engine
[0103] 155--Rankine cycle condenser outlet
[0104] 170--motorized mechanical driven compressor
[0105] 172--motorized mechanical driven blower
[0106] 174--desiccant dehumidification system
[0107] 200A--blowdown vacuum passive parallel compressor
superheater subassembly
[0108] 500A--vapor compression passive parallel compressor
superheater subassembly
[0109] 500B--vapor compression passive parallel compressor
superheater subassembly
[0110] 600--passive parallel array for blowdown vacuum heat
sink
[0111] 700--passive parallel array for vapor compression
[0112] 800A--passive parallel reducing volume compressor
subassembly
[0113] 810--isoexo thermal vessel
[0114] 820--isoexo thermal vessel
[0115] 830--isoexo thermal vessel
[0116] 840--cooling flow inducing heat exchanger
[0117] 842--cooling flow inducing heat exchanger
[0118] 844--cooling flow inducing heat exchanger
[0119] 850--heating flow inducing heat exchanger
[0120] 853--heating flow inducing heat exchanger
[0121] 855--heating flow inducing heat exchanger
[0122] 900--passive parallel reducing volume compressor array
[0123] 1000--external heat source
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0124] Reference will now be made in detail to the present
preferred embodiments of the invention as illustrated in the
accompanying drawings.
[0125] The cryogenic and thermal source cogeneration system of the
present invention includes both method and apparatus including an
array of heat exchanger(s), flow regulation device(s), compression
system(s) and expansion engines that are assembled to integrate
synchronized thermodynamic and non thermodynamic processes for the
extraction of heat from geo-thermal (natural internal heat sources
below the surface of the earth) or solar-thermal (natural heat
sources above the Earth's surface) energy sources and for the
conversion of this thermal energy (heat) into mechanical energy.
This system may be utilized primarily to drive generators for the
production of electricity but other applications include benefits
from the net mechanical work produced by this system. This system
also has many cogeneration applications that can be utilized as an
attribution to the system's heat extraction and heat rejection
capabilities. By using two cycles this allows for example, the
liquification, evaporation, and then the re-liquification of a heat
transfer medium by recycling latent heat.
[0126] This disclosed cryogenic cogeneration and thermal source
system is preferably comprised of two sub-assemblies, the vapor
compression cycle 2, and the Rankine cycle 4. The method and
apparatus disclosed herein allows for a controlled and adjustable
liquid, vapor, and/or gas flow within all cycles in the system. Any
external heat source may be used, which may be natural such as
geothermal or solar, or manmade, by which the present method and
apparatus convert energy from the heat source into mechanical
and/or electrical energy.
[0127] In the preferred embodiment, the primary method and means to
receive heat from the external heat source, is the vapor compressor
cycle, 2. This heat is then preferably transferred to the Rankine
cycle 4, where the heat energy is converted to mechanical or
electrical energy, as disclosed herein. The two cycles and the
methods and apparatus for implementing them, are configured and
operated to complement and complete each other by hardware and/or
software means.
[0128] The vapor compression cycle may be implemented in many ways,
with the preferred method and apparatus described. In general, the
vapor compression cycle starts with a liquid receiver, with a
refrigerant in liquid form, but may be in gas or vapor form, is
expanded through a metering device, to help sub cool its circuit
through a sub cooler at the end of its cycle, and absorbs heat from
the Rankine cycle (so as to condense the Rankine cycle) through the
Rankine cycle condenser. The vapor compression refrigerant then
runs through a compressor/superheater assembly, to boost pressure
and absorb the heat from an external heat source, and then
transfers heat to the Rankine cycle, which superheats the Rankine
cycle refrigerant and condenses the vapor compression cycle
refrigerant, and is then sub cooled via the aforementioned heat
exchanger. Preferably compression is accomplished by filling the
superheater compressors with slightly superheated refrigerant, and
adding heat from the external heat source where the fixed volume
increases the temperature and pressure of the refrigerant until it
reaches the desired levels and is released. In such embodiments,
multiple vapor compression superheaters/compressors 22 and 60, are
configured in parallel and sequenced to minimize pulsations that
would result from isolation of the superheaters/compressors 22, and
60, to accommodate the process. Expansion tanks 11, also may be
provided to reduce pulsing and provide a more constant flow.
[0129] An embodiment is also described here, where a blowdown is
provided to evacuate the remainder of the high pressure/temperature
that remains in the superheaters/compressors 22, and 60, after they
are evacuated to complete their cycle and add the heat to the
Rankine cycle. To reintroduce this blowdown into the system, as
opposed to discharging into the atmosphere, the blowdown gasses are
expanded through another expansion engine, where a mechanical or
electrical output can be realized, to match the inlet pressure to
the compressors. The blowdown gasses may then be run through a heat
exchanger to eventually transfer heat into the Rankine cycle so as
to also match the temperature of the other gasses being introduced
into the compressors.
[0130] Alternatively, additional superheaters/compressors 810, 820,
and 830, may be provided in each circuit where volumes are
successively reduced to enhance the compression. Such
superheaters/compressors can be provided with heating and cooling
sources to induce the flow of refrigerant from one
superheater/compressor to another, in lieu of the previously
mentioned blowdown; however, it may be desired to incorporate
blowdowns into this configuration as well.
[0131] Preferably, Rankine cycle 4, also starts out with a liquid
receiver, a pump for pumping the liquid from the receiver, which
adds pressure to the liquid, into heat exchanger to absorb heat
from the vapor compression cycle, from its main condenser, blowdown
and/or its compressor, until the Rankine cycle refrigerant has
reached a superheated state where it is then expanded through a
expansion engine to obtain mechanical or electrical output, and is
re-condensed by being cooled by the vapor compression cycle.
[0132] In the embodiments described in detail below, the preferred
liquid refrigerant is nitrogen, however, other refrigerants may be
used if desired.
[0133] In FIG. 1, the vapor compression cycle 2, and means for
implementing the cycle are shown. As depicted in FIG. 1, the vapor
compression cycle can begin with, but is not limited to, an
optional vapor compression liquid reservoir receiver, 10, for
holding vapor compression cryogenic refrigerant 8, which may be any
refrigerant but preferably liquid nitrogen. Refrigerant 8, however,
may be other refrigerants, but preferably cryogenic refrigerants,
or others, such as methane, or the like. Refrigerant 8, may be in
the liquid phase, gas phase, or vapor phase in this cycle.
Reservoir receiver 10, leads to a vapor compression expansion
valve/metering device, or pressure reducing valve, 12, into an
optional vapor compression subcooler 14, and into a Rankine
condenser 155, that can be a subassembly to a cryogenic shell and
tube heat exchanger preferably exiting to an optional check valve
18, and/or an automated isolation valve 20, preferably connected to
a vapor compression superheater/compressor 22, in thermal
conductive contact with external heat source 1000.
Superheater/compressor 22, is preferably exited to a vapor
compression condenser 35, in thermally conductive contact with the
Rankine cycle refrigerant 6, preferably in the liquid phase
occupying a Rankine cycle liquid evaporator reservoir 7, that can
be a subassembly to a heat exchanger, and then passes back through
the subcooler 14, and into the receiver 10, in the preferred
methodology.
[0134] Also depicted in FIG. 1, the Rankine cycle 4, and means for
implementing the cycle are shown, preferably starts at an optional
Rankine cycle liquid evaporator/superheater reservoir 7, with
Rankine cycle refrigerant medium 6, which is preferably cryogenic.
Refrigerant medium 6, may be any refrigerant, but preferably a
cryogenic refrigerant such as liquid nitrogen, and is in thermally
conductive contact with the vapor compression condenser 35, as a
subassembly to a cryogenic and tube heat exchanger. Refrigerant 6,
may be in the liquid phase, gas phase, or vapor phase in this
cycle. Reservoir/receiver 7, connected to an array of piping and
appurtenances leads to a Rankine cycle expansion engine 150, and
discharging into a Rankine cycle condenser 155, which is in
thermally conductive contact with the vapor compression evaporator
16, as a subassembly to a cryogenic shell and tube/tube and tube
heat. Refrigerant 6, then passes back to the reservoir 7, in the
preferred methodology.
[0135] In the preferred operation of vapor compression cycle 2,
natural head from gravity can provide the pressure upon the liquid
within the vapor compression liquid reservoir receiver 10. This
head pressure can induce flow through the vapor compression
expansion valve/metering device/pressure-reducing valve 12, as the
refrigerant is discharged/released to a lower pressure within a
preferably vertical positioned vacuum. It will simultaneously
absorb latent heat from the optional vapor compression subcooler
14, and/or from the Rankine cycle condenser 155, as it passes
through its vapor compression evaporator 16. After the refrigerant
medium 8, is fully vaporized and slightly superheated it can
continue to absorb sensible heat from an external source as the
medium 8, travels through the vapor compression superheater 22, in
thermal conductive contact with external heat source 1000. Being
superheated at a constant and/or reduced volume, this thermal
expansion process will simultaneously increase the refrigerant
medium's pressure and reduce it's density forcing it to rise,
replace and transfer heat to denser atoms and/or molecules of
medium 8 until a near equilibrium temperature and density is
reached throughout. Hence, the buoyant, compressed superheated
medium 8, will be induced to flow upward via vertical piping 28,
into the vapor compression condenser 35, located at a calculated
higher elevation. Medium 8, can then proceed to conduct and release
its latent and sensible heat enthalpy to the Rankine cycle liquid
evaporator superheater reservoir 7, until medium 8, condenses into
the liquid state. This inverted process again increases the density
of the liquid medium 8, and gravity induces the flow downward back
through the subcooler 14, and into the receiver 10 to complete the
vapor compression cycle, 2. Hence, being that the system is
described closed loop, (but it is not limited to this
configuration, as it can be open loop or many other
configurations), displacement can cause a vacuum void to occur in
the vapor compression evaporator 16, the vapor compression
superheater 22, in thermal conductive contact with external heat
source 1000, and the vapor compression condenser 35. This can
stimulate continued thermosiphonic flow back through the expansion
valve 12, via natural convection.
[0136] In the preferred operation of Rankine cycle 4, medium 6,
preferably absorbs heat from the vapor compression condenser 35,
while in the Rankine cycle liquid evaporator/superheater reservoir
7. As medium 6, preferably liquid nitrogen, changes state from
liquid to superheated vapor and is being superheated at a constant
and/or reduced volume, this thermal process will simultaneously
increase the refrigerant medium's pressure and reduce it's density
forcing it to rise, replace and transfer heat to denser atoms
and/or molecules of medium 8, until a near equilibrium temperature
and density is reached throughout. Hence, the buoyant, compressed
superheated medium 6, will be induced to flow upward into the
Rankine cycle expansion engine 150, where medium 6, converts it's
heat energy into mechanical energy as it expands through engine
150. The residual saturated cold vapor is discharged from engine
150, into the Rankine cycle condenser 155, located at a calculated
lower elevation. Medium 6, releases it's sensible and latent heat
into the vapor compression evaporator 16, as it completes it's
condensation process while gravity induces the flow downward back
into the reservoir 7, to complete the Rankine cycle. Hence, being
that the system can be a closed loop system, displacement will
cause a vacuum void to occur in the Rankine cycle expansion engine
150, and upper section of the liquid evaporator/superheater
reservoir 7. This stimulates continued thermosiphonic flow back
through the expansion engine 150, via natural convection.
[0137] In other embodiments, in a passive parallel compressor
superheater assembly, depicted in FIG. 2-1, FIG. 2-2, FIG. 3-1 and
FIG. 3-2 can be enhanced by following check valve 18a, with a
connection to a passive parallel compressor superheater subassembly
500A, which comprises of a tee 19c, to a cryogenic automated
isolation valve 20a, as the cold vapor supply entering the vapor
compression super heater 22 exiting via a high pressure regulator
valve 27a, and a high pressure regulator valve 27b. The subassembly
500A, can be interconnected in parallel with an indefinite number
of other parallel compressor superheater subassemblies 500b, based
on the pertinent scalable design forming a passive parallel array
700.
[0138] In operation, this embodiment can facilitate the
simultaneous compression and superheating of several parallel
circuits. Accordingly, constant pressure and temperature may always
be available for feeding the remaining portion of the circuit and
its pertinent functions. This methodology also prevents any time
deference and/or pulsations that could be attributed to
inconsistent heat transfer, and the like.
[0139] In operation, superheating and/or compression is
accomplished by the filling of superheater 22, with the slightly
superheated medium 8 but still in a cold vapor state. Heat is then
added from the external heat source which increases the temperature
and pressure of medium 8, within the fixed volume of superheater
22, in thermal conductive contact with external heat source 1000.
This heat absorption will occur until predetermined parameters are
reached and valve 27a, then releases medium 8. This design can
facilitate the simultaneous compression and superheating of several
parallel circuits. Hence, constant pressure and/or temperature can
always be available for feeding the remaining portion of the
circuit and its pertinent functions. Expansion tank(s) can be
incorporated to prevent any time deference and/or pulsations that
could be attributed to inconsistent heat transfer, and/or isolation
of the superheater 22, and the like.
[0140] As depicted in FIGS. 2-1 and 3-1, the Rankine Cycle, in the
preferred embodiment can be enhanced by following the Rankine cycle
liquid receiver 130, with a Rankine cycle cryogenic liquid pump
135, that can be driven by any fixed speed, multiple speed, and/or
variable frequency motor (but external power sources will not be
necessary for its energy input), that discharges into Rankine cycle
evaporator 140.
[0141] In operation this embodiment can facilitate a
controlled/adjustable liquid flow within the Rankine cycle and
thereby directly and/or indirectly effect and control the medium
flow and heat transfer rates within the entire system and allow
adjustments as needed.
[0142] As depicted in FIGS. 3-1 and 3-2, the vapor compression
cycle can be modified to include a blowdown cycle that can begin by
a modification of the preferred embodiment that can begin with the
vapor compression liquid receiver 10, being connected to a vacuum
insulated tee fitting 19a, with one branch of the array of vacuum
insulated piping and appurtenances leading to the vapor compression
expansion valve 12, through pipe 21, into the vapor compression
stage 1 subcooler 14, out via pipe 21, into the vapor compression
evaporator 16, which is in thermally conductive contact with the
Rankine condenser 155. The flow then exiting to a connection with a
vacuum insulated check valve 18a followed by a tee 19b and
continuing with the same branched circuit to a passive parallel
compressor superheater subassembly 500A which may include another
tee 19c to the cryogenic automated isolation valve 20a as the cold
vapor supply. The High Pressure minimal or not insulated tee 160a,
is operably connected to the high pressure regulator valve 27c, as
a high pressure blowdown superheated gas supply entering the vapor
compression super heater 22, in thermal conductive contact with
external heat source 1000, and exiting via a high pressure
regulator valve 27a, and a high pressure regulator valve 27b. The
subassembly 500A, can be interconnected in parallel with an
indefinite number of other parallel compressor superheater
subassemblies 500B, based on the pertinent scaleable design forming
a passive parallel array 700. The interconnected array 700, is
exited through a minimal or non-insulated high-pressure piping and
appurtenances 28, to a vapor compression pre-condenser 30, via more
piping 28. The flow continues to the vapor compression condenser
35, which is in thermally conductive contact with a Rankine cycle
evaporator 140, as a subassembly to a cryogenic shell and tube/tube
and tube heat exchanger and back through the subcooler 14, through
a check valve 18b, and into the receiver 10. The actual blowdown
cycle can begin at a blowdown liquid receiver 90, supplying via
pipe 21, a blowdown cryogenic liquid pump 95, this can be driven by
any fixed speed, multiple speed, and/or variable frequency motor,
but external power sources will not be necessary for its energy
input, that discharges through one branch of tee 19h, into a
blowdown evaporator coil 100, which is in thermally conductive
contact with the vapor compression precondenser 30, as a
subassembly to a cryogenic shell and tube/tube and tube heat
exchanger connected through the pipe 28, to a blowdown super heater
105. The high pressure regulator valve 27e, is connected to a
passive parallel array 600 and 700, which are exited through a
blowdown mixed gas outlet 110, to bottleneck through one branch of
a tee 19k, into a blowdown expansion engine 115, preferably
discharges into a blowdown vacuum condenser coil 120. The vapor
outlet of coil 120, can be entrained via pipe 21, by the vacuum
suction side of an optional vacuum diffusion ejector 85. A blowdown
condenser which is in thermally conductive contact with a blowdown
vacuum evaporator 55, as a subassembly to a cryogenic shell and
tube heat exchanger. liquid outlet 125a, can be adjoined with a
vacuum diffusion ejector liquid outlet 125b through more of pipe
21, at tee 19e, with the remaining branch leading back to the
receiver 90. The other branch of tee 19h, can lead to a blowdown
liquid pump bypass regulating valve 97, continuing though more of
pipe 21, to terminate into the bottom of the vapor compression
liquid receiver 10. The other branch of tee 19k, preferably detours
through a blowdown vacuum engine bypass valve 112, and to the
discharge side of engine 115 at tee 191.
[0143] In FIGS. 3-1 and 3-2, to further support the efficient
operation of the blowdown cycle, the vapor compression cycle can be
further modified by adding a blowdown vacuum heat sink that can
commence at the other branch of the tee 19a, that is routed with
the vacuum insulated piping 21, through a blowdown stage 2
subcooler 50, to another vacuum insulated tee 19d. The flow
continues with the same branched circuit to a blowdown expansion
valve 45, back through subcooler 50, via more of the pipe 21, to
enter a blowdown vacuum evaporator 55, which is in thermally
conductive contact with the blowdown condenser coil sections 120,
and 125a, as a subassembly to a tube heat exchanger, exiting to a
passive parallel compressor superheater subassembly 200A, which can
consist of another tee 19f, to a cryogenic automated isolation
valve 20f, as the cold vapor supply and a high pressure minimally
or not insulated tee 160f, connected to a high pressure regulator
valve 27g, as a high pressure blowdown superheated gas supply
entering a blowdown vacuum compressor superheater 60. One exit of
superheater 60, can connect to an automated 3 way blowdown vacuum
control valve 70, and another exit via a high pressure regulator
valve 27f. The subassembly 200A, can be interconnected in parallel
with an indefinite number of other blowdown vacuum parallel
compressor superheater subassemblies 200B, and is based on the
pertinent scaleable design forming another passive parallel array
600. The interconnected array 600, can be exited through several
channels. One being valve 70 with one branch leading through pipe
21, to a blowdown vacuum cryopump 75, joined to the suction side of
a blowdown vacuum compressor 80, with its discharge side connected
to pipe 21, that can complete the circuit via the connection to the
previously unmentioned branch of Tee 19b. The other branch of tee
19d, can travel through more of pipe 21, to terminate as the high
pressure side of the optional liquid entrainment blowdown vacuum
diffusion ejector 85.
[0144] Seen in FIGS. 3-1 and 3-2, is another embodiment of the
Rankine cycle. The Rankine cycle starts at a Rankine cycle liquid
receiver 130, supplying via pipe 21, the Rankine cycle cryogenic
liquid pump 135, that discharges into a Rankine cycle evaporator
140, in thermally conductive contact with the vapor compression
condenser 35, connected through the pipe 28, to a Rankine cycle
superheater 145, and the external heat source, exiting via more of
pipe 28 into the Rankine cycle expansion engine 150. Discharging
through pipe 21 into the Rankine cycle condenser 155, which is in
thermally conductive contact with the Vapor Compression Evaporator
16, and back to the receiver 130.
[0145] This broadened design can facilitate a controlled/adjustable
liquid, vapor and/or gas flow within all cycles of the entire
system. The blowdown cycle and blowdown vacuum heat sink is one
method, among many others using the present invention, that can
produce any pressure and enthalpy conditions desired within any and
all sections of the entire system. The blowdown expansion engine
also can provide additional net work output.
[0146] In FIGS. 4-1 and 4-2 depicts a slightly superheated cold
vapor of medium 8, exiting the evaporator 16, through one branch of
tee 19m into a passive parallel reducing volume compressor
subassembly 800A comprising of the path through valve 20n into an
isoexo thermal vessel 810 (in thermally conductive contact with a
cooling flow inducing heat exchanger 840 and a heating flow
inducing heat exchanger 850) through a valve 20o into another
isoexo thermal vessel 820, preferably in thermally conductive
contact with a cooling flow inducing heat exchanger 842, and a
heating flow inducing heat exchanger 853, through valve 20p. It
then passes into another isoexo thermal vessel 830, preferably in
thermally conductive contact with a cooling flow inducing heat
exchanger 844, and a heating flow inducing heat exchanger 855,
through valve 27n, into one branch of tee 19n, and through pipe 28,
to condenser 35, preferably in thermally conductive contact with
the Rankine cycle liquid evaporator 140. It then passes through
pipe 21, into the subcooler 14 exiting into the receiver 10 through
valve 12 and back to the evaporator 16. The subassembly 800A can be
interconnected in parallel with an indefinite number of other
passive parallel reducing volume compressor subassemblies 800B,
based on the pertinent scalable design forming a passive parallel
reducing volume compressor array 900.
[0147] As depicted in FIGS. 4-1 and FIG. 4-2, the Vapor Compression
Cycle within the Preferred Embodiment can be enhanced by
interacting with a sequenced isothermal and exothermal process
utilized by a Passive Parallel Reducing Volume Compressor Array 900
for the flow induction, compression and/or superheating of any
refrigerant medium. This process may produce a broadened scope of
pressure and enthalpy conditions.
[0148] In FIGS. 5-1 and 5-2 show an optional embodiment including
the vapor compression cycle and/or the Rankine Cycle utilizing a
motorized mechanical driven compressor 170, and motorized
mechanical driven blower 172, for flow circulation. FIG. 5-2 also
includes an optional desiccant dehumidification system 174, that
can regenerate via the use of an optional solar collector
array.
[0149] It is seen that with the proposed invention, the environment
is safe from emissions, hazardous waste, flooding of valuable
property and no particular geographic location is necessary. This
system will consume no water, no fuel, no storage, no chemical
treatment and is not dependant on weather conditions. Additional
advantages are that this system:
[0150] can be an integrated dual cycle closed loop system that
generates power/mechanical energy without emitting any gases to the
atmosphere.
[0151] can be a system that does not directly and/or indirectly
consume and deplete scarce/non-renewable energy resources for its
operation and will also provide the opportunity for society to be
independent of consumable resources.
[0152] can provide a natural convection thermosiphonic
iso/exothermal compression process in the vapor compression cycle
requiring only free thermal energy input to achieve the necessary
work. So after a substantial amount of the free thermal energy is
converted to work, the residual sensible and latent heat energy and
the refrigerant medium can be recycled as it is condensed from the
vapor and/or gas state back into the liquid state. Thereby
conserving the energy and preventing and eliminating society's
dependency on the existing expensive consumable energy
infrastructure.
[0153] An avionic lifting system may also be utilized in another
embodiment. Any of the above embodiments can utilize any of the
compressor/superheater subassemblies mentioned herein, but are not
limited to just the methods described herein. Any method to cool
air can be used to increase the density of the atmospheric air
surrounding a vessel containing a buoyant medium, such as helium.
The buoyant vessel's lifting capacity can be significantly
increased as a result of the increased density difference between
the buoyant medium in the vessel and the increased density of the
surrounding air. This technology is capable of replacing existing
rotorcraft by decreasing diameters of propellers and/or rotors.
[0154] As is evident from the above description, a wide variety of
applications, methods, and systems may be envisioned from the
disclosure provided. The apparatus and methods described herein are
applicable in numerous applications, for example, the external heat
source may be solar, geothermal, air conditioning loads, research
systems, avionic, topping cycles, refrigeration, cogeneration,
cryogenic applications, and additional advantages and modifications
will readily occur to those skilled in the art. For example, the
exterior heat source absorption can be located as a front surface
area to be exposed in the front of an automobile. This surface area
could be reduced by recovering residual heat from friction
producing assemblies throughout the vehicle. This is a very
feasible possibility. The proposed invention system can also be
modified and incorporated to power and propel this same vehicle.
Modified versions of this conception can be applied to trucks,
trains, ships, planes, etc. Scalable electrical generators,
compressors, etc. can be coupled with the proposed system(s) shafts
of the expansion engines. Further, the subject technology can be
utilized in cryogenic applications for liquification of gases such
as nitrogen, hydrogen, helium, methane, water etc; laboratory and
semiconductor applications, and medical applications (such as
cryronics, etc). which eliminate the expensive costs of electricity
consumption that is presently needed for existing systems. The
Subject technology can also partner with existing renewable energy
projects such as solar, bio-mass, geo-thermal, etc. to infinitely
and competitively increase their capacity to far exceed the
capacities of existing fossil fuel power generation facilities.
This new technology will also eliminate any heat sources and noise
sources that can be detected by the enemy and anti-aircraft
weaponry such as the stinger missile. Further, additional topping
cycles and bottom cycles that can comprise of different refrigerant
mediums can also be cascaded with this system. The invention in its
broader aspects is, therefore, not limited to the specific details,
representative apparatus and illustrative examples shown and
described. Accordingly, departures from such details may be made
without departing from the spirit or scope of the applicant's
general inventive concept.
* * * * *