U.S. patent application number 11/328401 was filed with the patent office on 2007-07-12 for multi-stage refrigerant turbine.
Invention is credited to Richard JR. McPhail.
Application Number | 20070157659 11/328401 |
Document ID | / |
Family ID | 38231459 |
Filed Date | 2007-07-12 |
United States Patent
Application |
20070157659 |
Kind Code |
A1 |
McPhail; Richard JR. |
July 12, 2007 |
Multi-stage refrigerant turbine
Abstract
A multi-stage refrigerant driven turbine is incorporated into a
closed loop system to generate electricity. Heat transfer conduits
and optional flow diverting members are disposed between the rotor
blades of each stage of the turbine. The closed loop system also
includes a condenser, pump, refrigerant storage container,
refrigerant, and expansion valve. A heat source and heat sink are
also provided. The expansion valve introduces a saturated
refrigerant mist into the turbine, and the refrigerant expands as
it flashes to a gas, thereby rotating the rotor blades and turbine
shaft. Heat from the heat source is added between stages to
increase the portion of refrigerant converted to gas. The gas is
passed from the turbine, condensed, and passed as a liquid to
storage or to repeat the cycle. The blending of refrigeration cycle
and turbine technologies allows electricity to be generated in a
closed loop system under moderate conditions.
Inventors: |
McPhail; Richard JR.; (Bald
Knob, AR) |
Correspondence
Address: |
Kyla Cummings;Speed Law Firm
Suite 1200
111 Center Street
Little Rock
AR
72201
US
|
Family ID: |
38231459 |
Appl. No.: |
11/328401 |
Filed: |
January 10, 2006 |
Current U.S.
Class: |
62/498 |
Current CPC
Class: |
F22B 37/04 20130101;
F01K 25/10 20130101; F01K 7/22 20130101 |
Class at
Publication: |
062/498 |
International
Class: |
F25B 1/00 20060101
F25B001/00 |
Claims
1. A combination, comprising: a housing; a refrigerant source
operably connected to said housing; a refrigerant disposed within
said refrigerant source; a shaft, at least a portion of said shaft
being disposed within said housing; a first rotor blade affixed to
said shaft within said housing; at least one first conduit disposed
within said housing, said at least one first conduit being disposed
downstream of said first rotor blade; and a second rotor blade
affixed to said shaft within said housing, said second rotor blade
being disposed downstream of said at least one first conduit.
2. The combination of claim 1, wherein said housing has a front,
upstream end and a rear, downstream end, and further comprising: a
first flow diverting member disposed within said housing between
said first rotor blade and said second rotor blade, said first flow
diverting member being configured to direct said refrigerant
downstream of and forward of said first rotor blade, said shaft
passing through said first flow diverting member.
3. The combination of claim 1, wherein said first rotor blade
extends a first distance radially from said shaft, and said second
rotor blade extends a second distance radially from said shaft,
said first distance being less than said second distance.
4. The combination of claim 1, further comprising: at least one
second conduit disposed within said housing, said at least one
second conduit being disposed downstream of said second rotor
blade; and a third rotor blade affixed to said shaft within said
housing, said third rotor blade being disposed downstream of said
at least one second conduit.
5. The combination of claim 4, wherein said housing has a front,
upstream end and a rear, downstream end, and further comprising: a
second flow diverting member disposed within said housing between
said second rotor blade and said third rotor blade, said second
flow diverting member being configured to direct said refrigerant
downstream of and forward of said second rotor blade, said shaft
passing through said second flow diverting member.
6. The combination of claim 4, wherein said first rotor blade
extends a first distance radially from said shaft, said second
rotor blade extends a second distance radially from said shaft, and
said third rotor blade extends a third distance radially from said
shaft, said first distance being less than said second distance,
and said second distance being less than said third distance.
7. The combination of claim 1, wherein said refrigerant has a
boiling point at 14.7 psi that is less than or equal to
approximately 32.degree. F.
8. The combination of claim 1, wherein said refrigerant is selected
from the group consisting of R-11, R-12, R-13, R-134a, R-142b,
R-152A, R-290, R-410a, R-404a, R-600, R-600a, a hydrofluorocarbon,
a chlorofluorocarbon, CO.sub.2, ammonia, nitrogen, freon, and
combinations thereof.
9. The combination of claim 1, wherein said first rotor blade
comprises at least approximately 20% of a material selected from
the group consisting of aluminum, composites, plastics, and
combinations thereof.
10. A combination, comprising: a closed loop system, said closed
loop system comprising: a refrigerant storage container; a
refrigerant disposed within said refrigerant storage container; a
turbine operably connected to said refrigerant storage container
for receiving said refrigerant from said refrigerant storage
container; a condenser operably connected to said turbine for
receiving said refrigerant from said turbine, said refrigerant
storage container being operably connected to said condenser for
receiving said refrigerant from said condenser; and said closed
loop system not including a compressor; and a heat source for
supplying heat to said closed loop system, said heat source being
disposed to provide heat to said refrigerant when said refrigerant
is in said turbine; and a heat sink for removing heat from said
closed loop system, said heat sink being disposed to remove heat
from said refrigerant when said refrigerant is in said
condenser.
11. The combination of claim 10, wherein said turbine comprises: a
housing; a shaft, at least a portion of said shaft being disposed
within said housing; a first rotor blade affixed to said shaft
within said housing; at least one first conduit disposed within
said housing, said at least one first conduit being disposed
downstream of said first rotor blade; and a second rotor blade
affixed to said shaft within said housing, said second rotor blade
being disposed downstream of said at least one first conduit.
12. The combination of claim 11, further comprising: a first flow
diverting member disposed with said housing between said first
rotor blade and said second rotor blade, said shaft passing through
said first flow diverting member.
13. The combination of claim 10, wherein said first rotor blade
extends a first distance radially from said shaft, and said second
rotor blade extends a second distance radially from said shaft,
said first distance being less than said second distance.
14. A method, comprising: (a) providing a turbine having a front,
upstream end and a rear, downstream end; (b) passing a refrigerant
through a first stage of said turbine so that said refrigerant
passes a first rotor blade affixed to a shaft and disposed in said
first stage; (c) after step (b), redirecting said refrigerant so
that said refrigerant passes a first point within said turbine
downstream of and forward of said first rotor blade; and (d) after
step (c), passing said refrigerant through a second stage of said
turbine so that said refrigerant passes a second rotor blade
affixed to said shaft and disposed in said second stage.
15. The method of claim 14, further comprising: (e) after step (d),
redirecting said refrigerant so that said refrigerant passes a
second point within said turbine downstream of and forward of said
second rotor blade; and (f) after step (d), passing said
refrigerant through a third stage of said turbine so that said
refrigerant passes a third rotor blade affixed to said shaft and
disposed in said second stage.
16. The method of claim 14, wherein step (b) comprises: passing
said refrigerant through said first stage of said turbine so that
said refrigerant passes said first rotor blade affixed to said
shaft and disposed in said first stage, said refrigerant having a
boiling point at 14.7 psi that is less than or equal to
approximately 100.degree. F.
17. The method of claim 14, wherein step (b) comprises: passing
said refrigerant through said first stage of said turbine so that
said refrigerant passes said first rotor blade affixed to said
shaft and disposed in said first stage, said refrigerant having a
boiling point at 14.7 psi that is less than or equal to
approximately 32.degree. F.
18. The method of claim 14, wherein step (b) comprises: passing
said refrigerant selected from the group consisting of R-11, R-12,
R-13, R-134a, R-142b, R-152A, R-290, R-410a, R-404a, R-600, R-600a,
a hydrofluorocarbon, a chlorofluorocarbon, CO.sub.2, ammonia,
nitrogen, freon, and combinations through said first stage of said
turbine so that said refrigerant passes said first rotor blade
affixed to said shaft and disposed in said first stage.
19. The method of claim 14, further comprising: after step (b) and
before step (d), passing said refrigerant through a heating section
so that said refrigerant comes into heat exchange contact with a
conduit disposed at said heating section.
20. The method of claim 19, further comprising passing water
through said conduit.
Description
BACKGROUND OF THE INVENTION
[0001] The present invention relates to electricity generation
using a turbine and, more particularly, to electricity generation
using a multi-stage turbine.
[0002] There has long been a desire to find alternative sources for
generating electricity. Solar power panels are known in the art but
are limited in their use, because they generate DC power only.
Windmills are also well known in the art and have been used for
generating AC power. Still, difficulties in finding appropriate
locations for windmills, and fluctuations in wind force and
direction limit their use and reliability.
[0003] Turbines and multi-stage turbines are known in the art. In
gas turbines, compressed air is forced into an ignition chamber and
combined with fuel, and the fuel is ignited. The expanding, ignited
gases travel along the axis of the turbine shaft, imparting motion
to rotor blades affixed to the turbine shaft, thereby rotating the
shaft. Additional fuel, or after burner fuel, is sometimes added
downstream of the ignition chamber to increase the power output. In
steam turbines, water is boiled to generate steam, the steam is
passed through a throttle valve, and the expanding steam travels
along the axis of the turbine shaft, imparting motion to rotor
blades affixed to the turbine shaft, thereby rotating the shaft.
Additional steam is sometimes added downstream of the throttle
valve to increase the power output. Gas turbines and steam turbines
are capable of generating reliable A/C power but suffer from a
number of disadvantages. For example, these turbines require fuels
that are non-renewable or that are not readily renewable. The
extreme conditions typically encountered in these turbines also
adds to the cost and complexity of the equipment and materials of
construction that must be used. These extreme conditions also lead
to high maintenance cost, increased wear and tear, and short
equipment life. The high energy input needed to maintain the
extreme conditions also leads to high cost for power
generation.
[0004] Refrigeration cycles are also well known in the art. In a
typical refrigeration cycle, a refrigerant gas is compressed and
passed to a heat sink or condenser. As the heat sink removes heat
from the high temperature, high pressure gas, the gas condenses to
liquid form. The condensed liquid is passed through an expansion
valve so that it moves from a high pressure area to a low pressure
area. As the liquid moves from through the expansion valve, the
liquid expands and evaporates. The expanding, evaporating gas is
passed to a heat source, such as an interior of a refrigerator or
freezer. The heat required to convert the liquid to gas is drawn
from the heat source, thereby cooling the heat source. The
refrigerant gas is then returned to the compressor to repeat the
cycle. Refrigeration cycles have provided reliable cooling for
years. Still, the use of a compressor in a refrigeration cycle
increases the cost and complexity of the system and also increases
the energy consumption and therefore operation cost of the system.
Using a compressor can also add to the cost and complexity of
maintaining a refrigeration cycle.
SUMMARY OF THE INVENTION
[0005] It is therefore an object of the present invention to
provide an apparatus and method for efficiently generating
electricity.
[0006] It is a further object of the present invention to provide
an apparatus and method of the above type that is capable of using
a wide variety of heat sources and heat sinks to provide a reliable
source of A/C power.
[0007] It is a still further object of the present invention to
provide an apparatus and method of the above type that generates
A/C power using solar energy.
[0008] It is a still further object of the present invention to
provide an apparatus and method of the above type that combines
turbine technology and refrigeration cycle technology to provide a
safe and efficient way of generating electricity.
[0009] It is a still further object of the present invention to
provide an apparatus and method of the above type that uses a
refrigerant to drive a turbine.
[0010] It is a still further object of the present invention to
provide an apparatus and method of the above type that uses a
refrigerant to drive a multi-stage turbine.
[0011] It is a still further object of the present invention to
provide an apparatus and method of the above type that offers an
environmentally friendly way to generate electricity.
[0012] It is a still further object of the present invention to
provide an apparatus and method of the above type that operates
under more moderate conditions than traditional turbines.
[0013] It is a still further object of the present invention to
provide an apparatus and method of the above type that operates
without the need for the added cost and complexity of a compressor
such as typically used in a refrigeration cycle.
[0014] It is a still further object of the present invention to
provide an apparatus and method of the above type that provides a
safe, efficient closed loop system for generating electricity.
[0015] It is a still further object of the present invention to
provide an apparatus and method of the above type that may be
constructed using less costly materials of construction because of
the more moderate operating conditions.
[0016] It is a still further object of the present invention to
provide an apparatus and method of the above type that provides for
reduced operating and maintenance expenses and for increased
operating life.
[0017] It is a still further object of the present invention to
provide an apparatus and method of the above type that makes
efficient use of waste heat from other processes.
[0018] It is a still further object of the present invention to
provide an apparatus and method of the above type that allows waste
heat from a wide variety of sources to be used to provide a
reliable source of A/C power.
[0019] Toward the fulfillment of these and other objects and
advantages, the present invention comprises a multi-stage,
refrigerant driven turbine, a closed loop system into which it is
incorporated, and a method of operating the system. A multi-stage
refrigerant driven turbine is incorporated into a closed loop
system to generate electricity. Heat transfer conduits and optional
flow diverting members are disposed between the rotor blades of
each stage of the turbine. The closed loop system also includes a
condenser, pump, refrigerant storage container, refrigerant, and
expansion valve. A heat source and heat sink are also provided. The
expansion valve introduces a saturated refrigerant mist into the
turbine, and the refrigerant expands as it flashes to a gas,
thereby rotating the rotor blades and turbine shaft. Heat from the
heat source is added between stages to increase the portion of
refrigerant converted to gas. The gas is passed from the turbine,
condensed, and passed as a liquid to storage or to repeat the
cycle. The blending of refrigeration cycle and turbine technologies
allows electricity to be generated in a closed loop system under
moderate conditions.
BRIEF DESCRIPTION OF THE DRAWINGS
[0020] The above brief description, as well as further objects,
features and advantages of the present invention will be more fully
appreciated by reference to the following detailed description of
the presently preferred but nonetheless illustrative embodiments in
accordance with the present invention when taken in conjunction
with the accompanying drawing, wherein:
[0021] FIG. 1 is a schematic representation of a system of the
present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0022] Referring to FIG. 1, reference numeral 10 refers in general
to a refrigerant system of the present invention. The system
includes an expansion valve 12, a turbine 14, a condenser 16, a
pump 18, and refrigerant 20 and may include a refrigerant storage
reservoir or container 22. A heat source 24 and heat sink 26 are
also provided.
[0023] The expansion or throttling valve 12 of the refrigerant
system 10 may take the form of any number of different commercially
available throttle valves or spray nozzles. The valve 12 has speed
or load governing controls, and the size and capacity of the valve
depend upon a variety of system parameters, such as size and
operating conditions. Multiple valves 12 may be used and may be
positioned at different locations to help control load. The valve
12 may also admit refrigerant 20 directly to the turbine 14, or may
admit the refrigerant to an evaporator or heat exchanger before the
refrigerant 20 is passed to the turbine 14.
[0024] In a preferred embodiment, the turbine 14 is an axial flow,
multi-stage turbine. The housing or casing 28 has a front, upstream
end 30 and a rear, downstream end 32. An outer wall of the housing
28 generally diverges from front to back. A turbine shaft 34 is
disposed partially within the housing 28, and rotor blades 36a,
36b, 36c are affixed to the shaft 34, positioned along the length
of the shaft 34 so that they are disposed in different stages of
the turbine 14. Steam turbines operating at relatively high
velocities, pressures, and temperatures are subject to blade
impingement from entrained moisture in the steam, and rotor blades
can be permanently damaged by the water. As a result, rotor blades
in steam turbines must be of very rugged construction, placing
significant restrictions on the types of materials from which the
blades may be constructed. In contrast, due to the relatively
modest velocities, pressures and temperatures in which the present
turbine 14 should operate many fewer restrictions are placed on the
materials of construction of the rotor blades 36a, 36b, 36c and
other components. The rotor blades 36a, 36b, and 36c may be
constructed of any number of materials, including but not limited
to aluminum, composites, plastics, or various blends or
combinations of those and other components. For example, the blades
36a, 36b, and 36c may comprise at least approximately 20% of a
material selected from the group consisting of aluminum,
composites, plastics, and combinations thereof. Further, because of
the more moderate operating conditions, the rotor blades 36a, 36b,
and 36c will not require the closely machined tolerances or
shrouded blade tips typically required in steam turbines. The
turbine 14 stages and reduction gearing may be arranged as in any
conventional turbine design, with the number of stages and the
reduction ratio dependent upon the specific system flow
capabilities. Due to the relatively moderate temperatures within
the turbine 14, the reduction gears may be disposed within the
housing between each stage.
[0025] An axially aligned, frustoconical inner turbine wall 38a
diverging from front to back is positioned in close proximity to
the rotor blades 36a in the first stage of the turbine 14. Each
rotor blade 36a extends a distance radially from the shaft 34, and
that distance increases with distance from the front of the stage
so that an outer edge of each rotor blade 36a is maintained in
close proximity to the diverging inner turbine wall 38a. The rear
end of the first diverging turbine wall 38a is aligned at or near
the last rotor blade 36a of the first stage.
[0026] A flow diverting member 40a is centrally positioned in the
housing, disposed between the rotor blades 36a of the first stage
and the rotor blades 36b of the second stage, the shaft 34 passing
through an opening in the member 40a. Front portions of the member
40a are disposed between the inner turbine wall 38a and the outer
turbine wall 28, and forward portions of the member 40a extend
forward and downstream of the back end of the inner wall 38a and
forward and downstream of at least one of the rotor blades 36a in
the first stage. The flow diverting member 40a is affixed within
the turbine 14 so that it does not move relative to the inner
turbine wall 38a.
[0027] Heat transfer conduits 42a, 42b, and 42c, such as a tube
bank, are disposed along or within the turbine 14 between each
stage to create a regeneration area. In a preferred embodiment,
tubes extend into the flow path of the refrigerant 20, aligned
generally transverse to the flow path. It is of course understood
that the conduits 42a, 42b, and 42c may take any number of forms,
such as one or more tubes or jackets lining the housing or
extending into the flow path within the housing 28. The heat
transfer conduits 42a, 42b, and 42c will typically be sized and
disposed to provide for greater heat transfer to later stages
within the turbine 14. The regeneration areas assist in eliminating
the need for a compressor, as is typically used in convention
refrigeration cycles. The use of saturated vapor and regeneration
areas helps to compensate for the low enthalpy of the refrigerant
20 as compared to steam.
[0028] A second axially aligned, frustoconical inner turbine wall
38b diverging from front to back is positioned in close proximity
to the rotor blades 36b in the second stage of the turbine 14. Each
rotor blade 36b in the second stage extends a distance radially
from the shaft 34, and that distance increases with distance from
the front of the stage so that an outer edge of each rotor blade
36b is maintained in close proximity to the diverging inner turbine
wall 38b. The rear end of the second diverging turbine wall 38b is
aligned at or near the last rotor blade 36b of the second stage.
The rotor blades 36b of the second stage generally extend a greater
distance radially from the axis than do the rotor blades 36a of the
first stage.
[0029] A second flow diverting member 40b is centrally positioned
in the housing 28, disposed between the rotor blades 36b of the
second stage and the rotor blades 36c of the third stage, the shaft
34 passing through an opening in the member 40b. Front portions of
the member 40b are disposed between the inner turbine wall 38b and
the outer turbine wall 28, and forward portions of the member 40b
extend forward and downstream of the back end of the inner wall 38b
and forward and downstream of at least one of the rotor blades 36b
in the second stage.
[0030] Similar to the regeneration area between the first and
second stages, heat transfer conduits 42b, such as a tube bank, are
disposed along or within the turbine 14 between the second and
third stages to create a second regeneration area.
[0031] Additional stages are provided as needed. For example,
another axially aligned, frustoconical inner turbine wall 38c
diverging from front to back is positioned in close proximity to
the rotor blades 36c in the third stage of the turbine 14. Each
rotor blade 36c in the third stage extends a distance radially from
the shaft 34, and that distance increases with distance from the
front of the stage so that an outer edge of each rotor blade 36c is
maintained in close proximity to the diverging inner turbine wall
38c. The rear end of the third diverging turbine wall 38c is
aligned at or near the last rotor blade 36c of the third stage. The
rotor blades 36c of the third stage generally extend a greater
distance radially from the axis than do the rotor blades 36a and
36b of the first and second stages. Additional flow diverting
members and regeneration areas are provided for the additional
stages as needed.
[0032] It is of course understood that most common turbine designs
may be used, including but not limited to radial flow, axial flow,
horizontal, vertical, and with or without pressure and velocity
compounding. Casing or housing pressure requirements will depend on
factors such as the type of refrigerant 20 used and the maximum
operational pressures and temperatures expected. The casing may
also be designed as a hermetic unit with an internal casing
dividing the stages rated at system differential pressure, and an
outer casing rated at overall system pressure.
[0033] The downstream or discharge end of the multistage turbine 14
is connected to a condenser 16. The condenser 16 may take the form
of any number of commercially available condensers. The condenser
16 is sized for the expected operating parameters of the particular
system to provide sufficient heat transfer to condense the
refrigerant gas into liquid. The condenser 16 cooling may be of the
direct type, in which the refrigerant 20 in the closed loop system
is cooled directly by the heat sink 26, or of the indirect type, in
which a cooling medium such as water is used to transfer heat
between the condenser 16 and the heat sink 26. As used herein,
"direct" cooling or heating is not intended to mean or imply direct
contact between the refrigerant 20 and the heating or cooling
fluid. Under rare circumstances, such direct contact or commingling
may be used, but not in the preferred embodiment.
[0034] A line 44 connects the condenser 16 to the refrigerant
reservoir 22, and a feed pump 18 is provided in the line 44 for
transferring liquid refrigerant 20 to the reservoir 22 or expansion
valve 12, depending on system load requirements. The pump 18 is
sized as needed to meet the pressure and flow requirements of the
particular system. The refrigerant 20 may take the form of any
number of different commercially available refrigerants. The
refrigerant 20 preferably has a boiling point at 14.7 psi that is
less than or equal to approximately 10.degree. F. and more
preferably has a boiling point at 14.7 psi that is less than or
equal to approximately 32.degree. F. The refrigerant 20 is most
preferably selected from the group consisting of R-11, R-12, R-13,
R-134a, R-142b, R-152A, R-290, R-410a, R-404a, R-600, R-600a, a
hydrofluorocarbon, a chlorofluorocarbon, CO.sub.2, ammonia,
nitrogen, freon, and combinations thereof. Because of the
refrigerant or refrigerants being used, the refrigerant system 10
is preferably a closed loop system. The refrigerant system 10 may
be designed as hermetic or semi-hermetic depending upon the
application.
[0035] The heat source or heating system 24 is preferably an
indirect heat collection system 24 that uses a secondary medium,
such as water, to collect and transfer heat from the heat source 24
to the refrigerant system 10. The heating system 24 is connected to
the heat transfer conduits 42a, 42b, and 42c in the refrigerant
system 10. The heating system 24 will have relatively moderate
operating conditions. For example, there are relatively low
pressure requirements since the transfer medium is merely
circulating. Accordingly, lower cost materials, such as plastic and
PVC pipe and tubing may be used. Using this indirect heating system
24 allows great flexibility in positioning and configuring the
refrigerant system 10 relative to the heat source 24.
[0036] The heat source 24 may take any number of forms ranging from
solar panels to a heat exchanger used to dissipate or disperse
waste heat from large-scale industrial activities. Any number of
different conventional sources of heat, or combinations thereof,
may be used, including heat sources 24 that have heretofore not
been used for generating AC power. Water is preferably used to
acquire heat from the heat source 24 and to transfer that heat to
the refrigerant 20 in the refrigerant system 10. Pump 46 circulates
the water between the heat source 24 and the heat transfer conduits
42a, 42b, and 42c of the refrigerant system 10.
[0037] The heat sink or cooling system 26 is preferably an indirect
heat collection system that uses a secondary medium, such as water,
to absorb heat from the condenser 16 and transfer it to the heat
sink 26. The heat sink 26 is connected to the cooling coils 48 in
the condenser 16. The cooling system 26 will have relatively
moderate operating conditions. For example, there are relatively
low pressure requirements since the transfer medium is merely
circulating. Accordingly, lower cost materials, such as plastic and
PVC pipe and tubing may be used. Using this indirect cooling system
26 allows great flexibility in positioning and configuring the
refrigerant system 10 relative to the heat sink 26.
[0038] The heat sink 26 may take any number of forms such as
reservoirs, streams, bodies of water, the atmosphere, buried pipes,
cooling towers, other things and systems typically used to
dissipate or disperse heat, and combinations thereof. Water is
preferably used to absorb heat from the condenser 16 and to
transfer that heat to the heat sink 26. Pump 50 circulates the
water between the heat sink 26 and the condenser 16 of the
refrigerant system 10.
[0039] In operation, pump 46 passes a heating medium, such as
water, through line 52 and through the heat source 24. The water
absorbs heat and passes through line 54 to the heat transfer
conduits 42a, 42b, and 42c, located in the regeneration areas of
the refrigerant system 10, to transfer heat to the refrigerant 20
passing through the turbine 14. The water then passes through line
56 and back through the pump 46 to begin another cycle. It is of
course understood that any number of heating systems 24 and heating
mediums may be used and that any number of things may serve as the
heat source 24.
[0040] Refrigerant 20 passes through the expansion or throttling
valve 12 and expands through the diverging inner turbine wall 38a
as it flashes to a gas, thereby rotating the first set of rotor
blades 36a and the turbine shaft 34. The refrigerant 20 exits this
first stage in the form of a heavily saturated mist. A first flow
diverting member 40a redirects the refrigerant 20 so that it passes
downstream of but forward of at least one of the first set of rotor
blades 36a, through a first regeneration area. Heat transfer
conduits 42a in the first regeneration area transfer heat to the
gas, increasing the portion of the refrigerant 20 that is converted
to gas. Some of the entrained refrigerant droplets boil, or flash
off into vapor before being directed through the second diverging
inner turbine wall 38b and through the second set of turbine blades
36b. A second flow diverting member 40b redirects the refrigerant
20 so that it passes downstream of but forward of at least one of
the second set of rotor blades 36b, through a second regeneration
area. Heat transfer conduits 42b in the second regeneration area
transfer additional heat to the gas, increasing the portion of the
refrigerant 20 that is converted to gas. The refrigerant 20 is then
directed through the third diverging inner turbine wall 38c and
third set of turbine blades 36c. Additional stages are used as
desired. The rotating shaft 34 is used to perform work, such as to
generate AC power. It is of course understood that the system may
be used to generate DC power or to perform work in any number of
different forms.
[0041] Upon leaving the final turbine stage, the refrigerant 20 is
in the form of a high temperature, high pressure gas. The
refrigerant 20 is then directed to the condenser 16. In the
condenser 16, the water in the cooling coils 48 absorbs heat from
the refrigerant 20 and transfers it to the heat sink 26. Sufficient
heat is removed to cause the refrigerant 20 to condense into liquid
form and gather at the bottom of the condenser 16. Feed pump 18
then transfers the liquid refrigerant 20 via line 44 to the
reservoir 22 or back to the throttle valve 12, depending upon the
load on the refrigerant system 10.
[0042] Pump 50 passes a cooling medium, such as water, through line
58 and through the cooling coils 48 of the condenser 16. The water
absorbs heat in the condenser 16 and then passes through line 60 to
the heat sink 26 for cooling. The water then passes through line 62
and back through the pump 50 to begin another cooling cycle. It is
of course understood that any number of cooling systems 26 and
cooling mediums may be used and that any number of things may serve
as the heat sink 26.
[0043] Other modifications, changes and substitutions are intended
in the foregoing, and in some instances, some features of the
invention will be employed without a corresponding use of other
features. For example, the heating system 24 and cooling system 26
may be open loop, closed loop, or hybrids of the same. Although it
is preferred that the refrigerant system 10 be closed loop, it is
understood that the refrigerant system 10 may also be open loop,
closed loop, or hybrids of the same. Further, the heating system
24, refrigerant system 10, and cooling system 26 may but are not
required to have associated reservoirs for accommodating
fluctuating loads. Further still, the turbine 14 may or may not
include flow diverter members disposed therein, and, if included,
any number of different shapes, configurations, and flow patterns
may be used. It is of course understood that all quantitative
information is given by way of example only and is not intended to
limit the scope of the present invention.
* * * * *