U.S. patent application number 14/584062 was filed with the patent office on 2016-06-30 for air conditioning with auxiliary thermal storage.
This patent application is currently assigned to HY-SAVE LIMITED. The applicant listed for this patent is HY-SAVE LIMITED. Invention is credited to Calvin Becker.
Application Number | 20160187014 14/584062 |
Document ID | / |
Family ID | 54360339 |
Filed Date | 2016-06-30 |
United States Patent
Application |
20160187014 |
Kind Code |
A1 |
Becker; Calvin |
June 30, 2016 |
Air Conditioning with Auxiliary Thermal Storage
Abstract
A method of cooling includes cooling and compressing a
refrigerant into a liquid state using a compressor and outside air
handler then flowing the refrigerant in the liquid state through
heat transfer tubes that are situated within a thermal storage, the
thermal storage at least partially filled with a material, where
the refrigerant extracts heat from the material as the refrigerant
changes state from the liquid into a gas and the refrigerant in
gaseous form returns to the compressor. The refrigerant also flows,
in the liquid state, into an inside air handler where the
refrigerant in liquid form extracts heat from air flowing through
the inside air handler as the refrigerant changes into a gaseous
state, which then flows back to the compressor where the compressor
and outside air handler condenses the refrigerant back into the
liquid state.
Inventors: |
Becker; Calvin; (Wiltshire,
GB) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
HY-SAVE LIMITED |
Midsomer Norton |
|
GB |
|
|
Assignee: |
HY-SAVE LIMITED
Midsomer Norton
GB
|
Family ID: |
54360339 |
Appl. No.: |
14/584062 |
Filed: |
December 29, 2014 |
Current U.S.
Class: |
62/99 ; 62/324.1;
62/434 |
Current CPC
Class: |
F25B 25/005 20130101;
F28D 21/00 20130101; F24F 2005/0025 20130101; F25B 2400/24
20130101; Y02E 60/14 20130101; F28D 20/00 20130101; F24F 2005/0032
20130101; F25B 7/00 20130101; F24F 5/0017 20130101; F24F 1/14
20130101; F28D 2020/0078 20130101 |
International
Class: |
F24F 5/00 20060101
F24F005/00; F28D 21/00 20060101 F28D021/00; F24F 1/14 20060101
F24F001/14; F28D 20/00 20060101 F28D020/00 |
Claims
1. An air conditioning system comprising: a compressor; an outside
air handler in fluid communications with the compressor; a thermal
storage having a set of heat transfer tubes, a first end of each of
the heat transfer tubes in fluid communications with the outside
air handler through a high pressure line and a second end of the
heat transfer tubes in fluid communications with the compressor
through a suction line; an inside air handler interface to a
structure to be cooled and having an input that is in fluid
communications with the outside air handler through the high
pressure line and an output that is in fluid communications with
the compressor through the suction line; a fluid pump having an
input and an output, the input of the pump in fluid communications
with the first end of each of the heat transfer tubes and the
output of the pump in fluid communications with the input of the
inside air handler; whereas when the compressor runs, a refrigerant
is compressed into a liquid, cooled by the outside air handler and
flows through the high pressure line into the heat transfer tubes
where the refrigerant cools a material within the thermal storage,
the refrigerant also flows into the inside air handler where the
refrigerant evaporates, extracting heat from air from within the
structure to be cooled, and the refrigerant in gaseous form returns
to the compressor through the suction line; whereas, in a first
mode of operation, when cooling is needed, the pump operates and
circulates the refrigerant in liquid form from the first end of the
heat transfer tubes and into the inside air handler through the
high pressure line where the refrigerant extracts heat as it
evaporates into a gas and the refrigerant in gaseous form returns
to the thermal storage through the suction line and into the second
end of the heat transfer tubes where the refrigerant condenses back
into a cold liquid; and whereas in a second mode of operation, when
cooling is needed, the compressor operates and circulates the
refrigerant in liquid form from the outside air handler and into
the inside air handler through the high pressure line where the
refrigerant extracts heat as it evaporates into a gas and the
refrigerant in the gaseous form flows to the compressor through the
suction line where the refrigerant is compressed and cooled back
into a cold liquid.
2. The air conditioning system of claim 1, wherein the material is
a mixture of antifreeze and water.
3. The air conditioning system of claim 1, wherein the material is
a fluid that is derived from the vegetable beetroot.
4. The air conditioning system of claim 1, further comprising
thermal fins, each thermal fin comprising a first side and a second
side, each of the heat transfer tubes are sandwiched between the
first side and second side of a respective one of the thermal
fins.
5. The air conditioning system of claim 1, wherein a
cross-sectional shape of each of the heat transfer tubes is an oval
shape.
6. The air conditioning system of claim 1, further comprising a
valve between the input of the pump and the first end of each of
the heat transfer tubes, the valve opened in the first mode of
operation and closed in the second mode of operation.
7. The air conditioning system of claim 1, further comprising a
valve between the high pressure line and the first end of the heat
transfer tubes, the valve closed to prevent cooling of the thermal
storage.
8. The air conditioning system of claim 1, wherein the thermal
storage is enclosed in a container that provides a seal for
preventing loss of the material and that provides thermal
insulation.
9. A method of cooling comprising: cooling and compressing a
refrigerant into a liquid state using a compressor and outside air
handler; flowing the refrigerant in the liquid state through heat
transfer tubes that are situated within a thermal storage, the
thermal storage at least partially filled with a material, the
refrigerant extracting heat from the material as the refrigerant
changes state from the liquid into a gas and the refrigerant in
gaseous form returning to the compressor; and flowing the
refrigerant in the liquid state into an inside air handler where
the refrigerant in liquid form extracts heat from air flowing
through the inside air handler as the refrigerant changes into a
gaseous state, the refrigerant in the gaseous state then flows back
to the compressor where the compressor and outside air handler
condenses the refrigerant back into the liquid state.
10. The method of claim 11, further comprising stopping the cooling
and compressing and, when cooling is requested, circulating the
refrigerant in liquid form from the thermal storage to the inside
air handler, the refrigerant evaporating and extracting heat from
the air flowing through the inside air handler, and returning the
refrigerant in gaseous form back to the thermal storage, thereby
condensing of the refrigerant back into the liquid form.
11. The method of claim 10, wherein the refrigerant is a mixture of
antifreeze and water.
12. The method of claim 10, wherein the material is derived from
the vegetable beetroot.
13. An air conditioning system comprising: a compressor having an
input in fluid communications with a suction line and having an
output; an outside air handler, an input of the outside air handler
in fluid communications with the output of the compressor and an
output of the outside air handler in fluid communications with a
high pressure line; a thermal storage enclosed in a thermally
insulated housing and having heat transfer tubes that are at least
partially within a material, a first end of the heat transfer tubes
in fluid communications with the high pressure line and a second
end of the heat transfer tubes in fluid communications with the
suction line; an inside air handler having an input in fluid
communications with the high pressure line and having an output in
fluid communications with the suction line; a fluid pump having an
input of the pump in fluid communications with the first end of the
heat transfer tubes and the fluid pump having an output that is in
fluid communications with the high pressure line; whereas in a
first mode of operation when cooling is needed, the compressor
runs, a refrigerant is compressed into a liquid, cooled by the
outside air handler and flows into the first end of the heat
transfer tubes where the refrigerant evaporates, extracting heat
from the material within the thermal storage and the evaporated
refrigerant returns to the compressor through the suction line and,
in parallel, the refrigerant in liquid form flows into the inside
air handler where the refrigerant evaporates, extracting heat from
air and the evaporated refrigerant returns to the compressor
through the suction line; and whereas, in a second mode of
operation, when cooling is needed, the pump operates and circulates
a refrigerant in liquid form from the first end of the heat
transfer tubes into the inside air handler where the refrigerant
extracts heat as it evaporates into a gaseous form and the
refrigerant in the gaseous form returns to the second end of the
heat transfer tubes within the thermal storage where the
refrigerant condenses back into a cold liquid within the heat
transfer tubes.
14. The air conditioning system of claim 13, wherein the material
is a mixture of antifreeze and water.
15. The air conditioning system of claim 13, wherein the material
is derived from the vegetable beetroot
16. The air conditioning system of claim 13, further comprising
thermal fins, each of the heat transfer tubes are thermally and
physically coupled to a respective one of the thermal fins.
17. The air conditioning system of claim 16, wherein the thermal
fins comprise two sides and the heat transfer tubes are sandwiched
between the two sides of the thermal fins.
18. The air conditioning system of claim 13, whereas, in a third
mode of operation, when cooling is needed, a valve is closed
preventing flow of the refrigerant in liquid form into the thermal
storage and the compressor operates and circulates a refrigerant in
liquid form from the compressor and outside air handler into the
inside air handler where the refrigerant extracts heat as it
evaporates into a gaseous form and the refrigerant in the gaseous
form returns to the compressor where the refrigerant is compressed
and condensed back into a cold liquid.
19. The air conditioning system of claim 13, whereas, in a fourth
mode of operation, when cooling of the thermal storage is needed,
the compressor operates and circulates a refrigerant in liquid form
from the compressor and outside air handler into the into the first
end of the heat transfer tubes where the refrigerant extracts heat
from the material as it evaporates into a gaseous form and the
refrigerant in the gaseous form returns to the compressor where the
refrigerant is compressed and condensed back into a cold
liquid.
20. The air conditioning system of claim 19, further comprising
valves, the valves preventing flow of the refrigerant through into
the inside air handler when cooling is not performed.
Description
FIELD
[0001] This invention relates to air conditioners, and more
particularly, to a thermal storage air conditioner in which a cold
heat is produced and stored in a thermal storage device and later
used for cooling a room or refrigerator, etc.
BACKGROUND
[0002] Air conditioning systems have been in place for many years.
Typically, such systems comprise an outdoor heat exchanger that
includes a compressor and evaporator, an expansion device, and an
indoor heat exchanger where cooled refrigerant (e.g. liquefied
refrigerant) changes phase to a gas, extracting heat from the air
within the structure to make such a phase change.
[0003] In general, when the temperature within an air conditioned
area reaches a predetermined temperature such as a setting on a
thermostat, the compressor and air handler energize to cool the air
conditioned area, until the temperature within the air conditioned
area reaches another predetermined temperature, typically a few
degrees below that set by the thermostat. In this way, an amount of
hysteresis is provided to reduce start/stop cycles of the
compressor and air handler, providing improved efficiency,
operating life, and user experience.
[0004] Although there are many factors that affect efficiency and
cost of operation, a few factors are considered here within. One
factor that affects cost is the overall cost of electricity used in
operating the compressor and air handler. These devices are
motor-driven and typically consume many kilowatt hours per day. In
some parts of the world, electricity prices are tiered, in that,
during business hours (e.g. when businesses consume the most
energy), the electricity rates are higher than during the hours
that many businesses are closed and most people are sleeping. This
presents an advantage in operating the air conditioning during
these off-peak hours, but unfortunately, with conventional air
conditioning systems, this would result in the air conditioned
areas becoming too cold.
[0005] Another factor that needs consideration is temperature
differential between the area being air conditioned and the outside
ambient air. For example, when cooling an air conditioned area, the
higher the ambient air temperature, the more the compressor needs
to work to compress the refrigerant, and therefore, the more energy
consumption. Generally, at night, the ambient air temperature
cools, but the same situation occurs as above, in that, it is not
practical to reduce the temperature in the air conditioned area
beyond a certain low temperature.
[0006] Being that the compressor usually consumes a major portion
of the overall electricity budget and the compressor will operate
more efficiently when outside ambient air is lowest, there are many
advantages to operating the compressor during off-peak hours, but
to do so, an efficient way to store the cold heat is needed that
does not require the compressor to run during peak (warmer)
hours.
[0007] Prior systems utilizing thermal storage required the
compressor operate to access the cold heat stored in the thermal
storage. Further, such systems generally store cold heat (e.g.
extract heat) in a fluid by decreasing the temperature of the fluid
which has limited efficiency.
[0008] What is needed is a system that will efficiently store cold
heat and retrieve the cold heat when conditions indicate a need to
do such.
SUMMARY
[0009] In one embodiment, an air conditioning system is disclosed
including a compressor and an outside air handler that is in fluid
communications with the compressor. A thermal storage has a set of
heat transfer tubes, a first end of which are in fluid
communications with the outside air handler through a high pressure
line and a second end which are in fluid communications with the
compressor through a suction line. An inside air handler for
cooling a structure has an input that is in fluid communications
with the outside air handler through the high pressure line and an
output that is in fluid communications with the compressor through
the suction line. A fluid pump has an input and an output; the
input being in fluid communications with the first end of each of
the heat transfer tubes and the output being in fluid
communications with the input of the inside air handler. When the
compressor runs, a refrigerant is compressed into a liquid, cooled
by the outside air handler and flows through the high pressure line
into the heat transfer tubes where the refrigerant cools a material
within the thermal storage and, in parallel, flows into the inside
air handler where the refrigerant evaporates, extracting heat from
air from within the structure to be cooled, and the refrigerant in
gaseous form returns to the compressor through the suction line. In
a first mode of operation, when cooling is needed, the pump
operates and circulates the refrigerant in liquid form from the
first end of the heat transfer tubes into the inside air handler
through the high pressure line where the refrigerant extracts heat
as it evaporates into a gas and the refrigerant in gaseous form
returns to the thermal storage through the suction line where the
refrigerant condenses back into a cold liquid. In a second mode of
operation, when cooling is needed, the compressor operates and
circulates the refrigerant in liquid form from the outside air
handler and into the inside air handler through the high pressure
line where the refrigerant extracts heat as it evaporates into a
gas and the refrigerant in the gaseous form flows to the compressor
through the suction line where the refrigerant is compressed and
cooled back into a cold liquid.
[0010] In another embodiment, a method of cooling is disclosed
including cooling and compressing a refrigerant into a liquid state
using a compressor and outside air handler then flowing the
refrigerant in the liquid state through heat transfer tubes that
are situated within a thermal storage, the thermal storage at least
partially filled with a material, where the refrigerant extracts
heat from the material as the refrigerant changes state from the
liquid into a gas and the refrigerant in gaseous form returns to
the compressor. Also flowing the refrigerant in the liquid state
into an inside air handler where the refrigerant in liquid form
extracts heat from air flowing through the inside air handler as
the refrigerant changes into a gaseous state, which then flows back
to the compressor where the compressor and outside air handler
condenses the refrigerant back into the liquid state.
[0011] In another embodiment, an air conditioning system is
disclosed including a compressor having an input in fluid
communications with a suction line and also having an output. An
outside air handler has an input that is in fluid communications
with the output of the compressor and has an output that is in
fluid communications with a high pressure line. A thermal storage
enclosed in a thermally insulated housing has heat transfer tubes
that are at least partially within a material (e.g., submerged). A
first end of the heat transfer tubes are in fluid communications
with the high pressure line and a second end of the heat transfer
tubes are in fluid communications with the suction line. An inside
air handler has an input that is in fluid communications with the
high pressure line and has an output that is in fluid
communications with the suction line. An input of a fluid pump is
in fluid communications with the first end of the heat transfer
tubes and an output of the fluid pump is in fluid communications
with the high pressure line. When the compressor runs, a
refrigerant is compressed into a liquid, cooled by the outside air
handler and flows into the first end of the heat transfer tubes
where the refrigerant evaporates, extracting heat from the material
within the thermal storage and the evaporated refrigerant returns
to the compressor through the suction line. In parallel, the
refrigerant in liquid form flows into the inside air handler where
the refrigerant evaporates, extracting heat from air and the
evaporated refrigerant returns to the compressor through the
suction line. In a first mode of operation, when cooling is needed,
the pump operates and circulates a refrigerant in liquid form from
the second end of the heat transfer tubes into the inside air
handler where the refrigerant extracts heat as it evaporates into a
gaseous form and the refrigerant in the gaseous form returns to the
second end of the heat transfer tubes within the thermal storage
where the refrigerant condenses back into a cold liquid within the
heat transfer tubes.
[0012] In another embodiment, an air conditioning system is
disclosed including a compressor and an outside air handler that is
in fluid communications with the compressor. The system includes a
thermal storage having a first set of heat transfer tubes and a
second set of heat transfer tubes. A first end of the first set of
heat transfer tubes are in fluid communications with the outside
air handler and a second end of the first set of heat transfer
tubes are in fluid communications with the compressor. An inside
air handler has an input and an output and a fluid pump having an
input and an output. The input of the pump is in fluid
communications with a second end of the second set of heat transfer
tubes and the output of the pump is in fluid communications with
the input of the inside air handler. The output of the inside air
handler is in fluid communications with a first end of the second
set of heat transfer tubes. When the compressor runs, a first
refrigerant is compressed into a liquid, cooled by the outside air
handler and flows into the first set of heat transfer tubes where
the first refrigerant evaporates, extracting heat from a material
within the thermal storage and the evaporated refrigerant returns
to the compressor. When cooling is needed, the pump operates and
circulates a second refrigerant in liquid form from the second end
of the second set of heat transfer tubes into the inside air
handler where the refrigerant extracts heat as it evaporates into a
gas and the refrigerant in gaseous form returns to the thermal
storage where the refrigerant condenses back into a cold
liquid.
[0013] In another embodiment, a method of cooling is disclosed
including cooling and compressing a first refrigerant into a liquid
state using a compressor and outside air handler, then flowing of
the first refrigerant in the liquid state through a first set of
heat transfer tubes that are situated within a thermal storage. The
thermal storage is at least partially filled with a material (e.g.,
antifreeze and water solution). The first refrigerant extracts heat
from the material as the first refrigerant changes state from the
liquid into a gas and then the first refrigerant in gaseous form
returns to the compressor. A second refrigerant flows from a second
set of heat transfer tubes that are also situated within the
thermal storage. The second refrigerant flows into an inside air
handler where the refrigerant in liquid form extracts heat from air
flowing through the inside air handler as the second refrigerant
changes into a gaseous state. The second refrigerant in the gaseous
state then flows back to the second set of heat transfer tubes
where temperatures within the thermal storage condense the second
refrigerant back into the liquid state.
[0014] In another embodiment, air conditioning system is disclosed
including a compressor having an input and an output and an outside
air handler. An input of the outside air handler is in fluid
communications with the output of the compressor. A thermal storage
that is enclosed in a thermally insulated housing has a first set
of heat transfer tubes and a second set of heat transfer tubes that
are at least partially within a material (e.g. at least partially
submerged within a material such as a solution of antifreeze and
water). A first end of the first set of heat transfer tubes are in
fluid communications with the output of the outside air handler and
a second end of the first set of heat transfer tubes in fluid
communications with the compressor. The system includes an inside
air handler having an input and an output and a fluid pump also
having an input and an output. The input of the pump is in fluid
communications with a second end of the second set of heat transfer
tubes, the output of the pump is in fluid communications with the
input of the inside air handler, and the output of the inside air
handler is in fluid communications with a first end of the second
set of heat transfer tubes. When the compressor runs, a first
refrigerant is compressed into a liquid, cooled by the outside air
handler and flows into the first set of heat transfer tubes where
the first refrigerant evaporates, extracting heat from the material
within the thermal storage and the evaporated refrigerant returns
to the compressor. When cooling is needed, the pump operates and
circulates a second refrigerant in liquid form from the second end
of the second set of heat transfer tubes into the inside air
handler where the refrigerant extracts heat as it evaporates into a
gas and the refrigerant in gaseous form returns to the thermal
storage where the refrigerant condenses back into a cold liquid
within the second set of heat transfer tubes.
BRIEF DESCRIPTION OF THE DRAWINGS
[0015] The invention can be best understood by those having
ordinary skill in the art by reference to the following detailed
description when considered in conjunction with the accompanying
drawings in which:
[0016] FIG. 1 illustrates a perspective view of a first in-line air
conditioning system with in-line thermal storage.
[0017] FIG. 1A illustrates a perspective view of a second in-line
air conditioning system with in-line thermal storage.
[0018] FIG. 2 illustrates a perspective view of an air conditioning
system with auxiliary thermal storage.
[0019] FIG. 3 illustrates a perspective view of the internals of
the auxiliary thermal storage.
[0020] FIG. 4 illustrates a perspective view of the internals of
the in-line thermal storage.
[0021] FIG. 5 illustrates a perspective partially open view of the
auxiliary thermal storage.
[0022] FIG. 6 illustrates a perspective partially open view of the
in-line thermal storage.
[0023] FIG. 7 illustrates a schematic view of the first in-line air
conditioning system with in-line thermal storage.
[0024] FIG. 7A illustrates a perspective view of the second in-line
air conditioning system with in-line thermal storage.
[0025] FIG. 8 illustrates a schematic view of the air conditioning
system with auxiliary thermal storage.
[0026] FIG. 9 illustrates a schematic view of an exemplary
processing device as used in conjunction with the air conditioning
system with thermal storage.
[0027] FIG. 10 illustrates a flow chart of an exemplary software
system running on processing device as used in conjunction with the
air conditioning system with thermal storage.
[0028] FIG. 11 illustrates a perspective view of an exemplary
thermal fin design.
DETAILED DESCRIPTION
[0029] Reference will now be made in detail to the presently
preferred embodiments of the invention, examples of which are
illustrated in the accompanying drawings. Throughout the following
detailed description, the same reference numerals refer to the same
elements in all figures.
[0030] Note that throughout this description, an air conditioning
system is described. In such, an air conditioning system is any
system that conditions air with a temperature change, either making
the air cooler (traditional) or warmer (reversed system). There is
no limitation on the location of the air being conditioned such as
within a building or room, within a chiller or "refrigerator,"
within a passenger compartment of a vehicle, within a cargo section
of a tractor trailer or train, etc.
[0031] The system described provides air conditioning in any such
scenario with the added benefit of performing extra work (e.g.
drawing extra energy or electricity) during certain time periods to
reduce the amount of work (e.g. drawing less energy or electricity)
during other time periods. This is very useful in locations that
have tiered energy costs (e.g., lower costs during evening hours),
but also is very useful in locations that have constant energy
costs but potentially wide outside ambient air temperatures (and/or
humidity). For example, even in a location with constant energy
costs, it is advantageous to operate the high energy consumption
component (e.g. compressor) during the evening hours when the
outside temperature is the coldest and then saving the cool heat in
a storage cell for use during the daytime hours when the outside
temperature is the warmest which requires more energy by the
compressor to cool the target area. Likewise, in a vehicle, there
are times when energy (e.g. from the fossil-fuel engine) is wasted
such as while waiting for a traffic light, while there are times
when very little surplus energy is available for cooling such as
while accelerating or climbing a hill. There are many advantages in
storing cool heat (e.g. running the compressor) while idling and
utilizing the stored cool heat (without running the compressor)
when other demands are made upon the vehicle's engine.
[0032] Although the air conditioning system describe is shown with
an outside air handler 70 (see FIGS. 1-3), any known condensing
system is anticipated including, for example, water-based in which
water is circulated over the fins to cool the refrigerant (instead
of air), or heat-pump systems which rely on the temperatures
beneath the surface to cool the refrigerant.
[0033] Referring to FIGS. 1 and 1A, perspective views of an in-line
air conditioning system 10 with thermal storage 120 is shown. Many
of the components of the in-line air conditioning system 10 are
similar to components of a conventional air conditioning system,
but are used in a different manner.
[0034] In the in-line air conditioning system 10 with thermal
storage 120, the thermal storage 120 has two banks of thermal fins
84a/84b (see FIGS. 4 and 6) having heat transfer tubes 82a/82b for
transferring cold heat to/from a refrigerant there within. A first
set of the heat transfer tubes 82a transfer refrigerant to/from the
compressor(s) 40 and a second set of heat transfer tubes 82b
transfer refrigerant to/from the inside air handler 70. In this
way, two independent types and chemistries of refrigerant are
allowed, though in some embodiments, the refrigerant flowing
through the first set of heat transfer tubes 82a is the same
refrigerant flowing through the second set of heat transfer tubes
82b.
[0035] The in-line air conditioning system 10 includes thermal
storage 120 that will be further described with FIGS. 4 and 6. The
in-line air conditioning system 10 includes one or more typical
compressors 40 (two are shown as an example), typically driven by
an electric motor for home and office, but there is no limitation
to the type of compressor(s) 40 and the way the compressor(s) 40
is/are driven (e.g., by a gasoline engine). The compressor(s) 40
have a low pressure suction line (vapor inlet line) 25 through
which warm, gaseous refrigerant is received from the thermal
storage 120. The compressors 40 then compress this gaseous
refrigerant into a liquid state at a high pressure which is then
passed through the outside air heat exchanger 50 where the liquid
refrigerant is cooled by a flow of outside air over a series of
fins (not shown), as known in the industry. The now cold, liquid
refrigerant, under pressure, flows through the high pressure line
24 to the thermal storage 120. As the cold, liquid refrigerant
flows through the first set of the heat transfer tubes 82a within
the thermal storage 120, the refrigerant changes state from a
liquid to a gas (evaporates), extracting heat (thermal energy) from
the material 90 within the thermal storage 120, lowering the
temperature of the material 90. At a certain temperature (freezing
point of the material 90 based upon the physical properties of the
material 90), the material 90 changes phase from a liquid to a
solid. This phase change requires cooling energy above that needed
to simply lower the temperature of the material 90, and therefore,
stores that additional energy until the now solid material 90 warms
above a certain temperature (melting point based upon the physical
properties of the material 90). For completeness, an optional
thermal expansion valve 21 is shown
[0036] Note that many typical components of a traditional air
conditioning compressor 40 and outside air exchanger 50 such as
reversing valves, thermal expansion devices, check valves,
fans/motors to flow air over the fins, fins, etc., are not shown
for clarity purposes as they are well known in the art.
[0037] An inside air handler 70 (coils, fins, motors not shown for
clarity reasons) is located in the structure to be cooled such as
in a living space, freezer compartment, refrigerator, vehicle
passenger compartment, etc. The inside air handler 70 is similar or
the same as such known in the industry.
[0038] In the example of FIG. 1, the compressor 40 is operated at a
time desired (e.g. when electricity rates are lower) until the
material 90 within the thermal storage 120 achieves the desired
temperature. While the compressor 40 runs, cold first refrigerant
from the compressor 40 and outside air handler 50 flows through the
first set of heat transfer tubes 82a within the thermal storage 120
and cools and/or freezes the material 90 within the thermal storage
120. Once the desired temperature of the material 90 within the
thermal storage 120 is achieved, the compressor 40 is stopped,
requiring little or no further power.
[0039] Now, as the second refrigerant in gaseous form enters the
thermal storage 120, the second refrigerant contacts the cold
second set of heat transfer tubes 82b and condenses into a liquid.
The condensed, cold liquefied second refrigerant flows through
tubes 22 into a storage tank 60 (preferably insulated storage tank
60 or a Liquid Refrigerant Receiver 60 as known in the industry).
As any of the second refrigerants within the storage tank 60
evaporate, the gaseous second refrigerant flows through another
tube 26 into the thermal storage 120 where is it then condensed as
described above.
[0040] The liquefied second refrigerant within the storage tank 60
is in fluid communications with a pump 34 through a tube 30. When
cooling is required within the structure as determined by, for
example, a thermostat or other temperature sensing device, the
condensed, liquefied second refrigerant from the storage tank 60 is
pumped into the inside air handler 70 through a high pressure line
74 and optionally, a thermal expansion valve 73. The inside air
handler 70 receives the cooled, liquid second refrigerant through
the second high-pressure line 74 and the liquid second refrigerant
evaporates (changes state to a gas refrigerant) within the coils of
the inside air handler 70, extracting heat from air flowing through
the inside air handler 70. The now gaseous second refrigerant exits
the inside air handler 70 through a second suction line 72 and
returns to the storage tank 60, and eventually to the thermal
storage 120 where it is again cooled and liquefied.
[0041] As the temperature of the material 90 within the thermal
storage 120 rises, determinations are made as to whether the
compressor 40 should be run. For example, if the outside air
temperature is at an ideal temperature or if electricity rates are
low, the compressor is run to cool the material 90 to the desired
temperature. If the conditions are not right (e.g. electricity
rates are high or outside air temperatures are not ideal), running
of the compressor 40 is suppressed until cooling is no longer
possible with the remaining cold heat energy stored in the thermal
storage 120.
[0042] In the example of FIG. 1A, the compressor 40 is operated as
in FIG. 1, at a time desired (e.g. when electricity rates are
lower) until the material 90 within the thermal storage 120
achieves the desired temperature. While the compressor 40 runs, a
first refrigerant (cold) from the compressor 40 and outside air
handler 50 flows through the first set of heat transfer tubes 82a
within the thermal storage 120 and cools and/or freezes the
material 90 within the thermal storage 120. Once the desired
temperature of the material 90 within the thermal storage 120 is
achieved, the compressor 40 is stopped, requiring little or no
further power.
[0043] Now, as the second refrigerant in gaseous form enters the
thermal storage 120, the second refrigerant contacts the cold
second set of heat transfer tubes 82b and condenses into a liquid
form of the second refrigerant.
[0044] When cooling is required within the structure as determined
by, for example, a thermostat or other temperature sensing device,
the condensed, liquefied second refrigerant from the thermal
storage 120 is pumped into the inside air handler 70 through a high
pressure line 74 and optionally. The inside air handler 70 receives
the cooled, liquid second refrigerant through the second
high-pressure line 74 and the liquid second refrigerant evaporates
(changes state to a gas refrigerant) within the coils of the inside
air handler 70, extracting heat from air flowing through the inside
air handler 70 to provide cool air within the structure (e.g.,
home, office, refrigerator). The now gaseous second refrigerant
exits the inside air handler 70 through a second suction line 72
and returns to the thermal storage 120 where it is again cooled and
liquefied.
[0045] Again, as the temperature of the material 90 within the
thermal storage 120 rises, determinations are made as to whether
the compressor 40 should be run. For example, if the outside air
temperature is at an ideal temperature or if electricity rates are
low, the compressor is run to cool the material 90 to the desired
temperature. If the conditions are not right (e.g. electricity
rates are high or outside air temperatures are not ideal), running
of the compressor 40 is suppressed until cooling is no longer
possible with the remaining cold heat energy stored in the thermal
storage 120. For example, when outdoor temperatures are 23 F or
below, the condenser 40 and fans will operate, cooling the material
90 to, for example, the freezing point of the material 90. During
this time, the pump 34 will operate as needed to maintain the
desired temperature within the structure. Any surplus cooling due
to lower ambient outside temperatures will be stored in the thermal
storage 120. As the outside temperature increases above 23 F, the
system will favor extracting cold heat from the thermal storage 120
by operating only the pump 34 until the temperature within the
thermal storage 120 increases to a point at which the compressor(s)
40 need be operated.
[0046] In a preferred embodiment, the liquid pump 34 is an LPA
(Liquid Pressure Amplification) pump 34. Although a single thermal
storage 120 is shown in FIGS. 1 and 1A, smaller, larger, serial
and/or parallel thermal storage 120 are anticipated.
[0047] In some embodiments, the material 90 within the thermal
storage is a chemical-based antifreeze material such as ethylene
glycol or a mixture of such antifreeze and water for achieving the
desired phase change temperature (e.g., freezing point). In some
embodiments, the material 90 is made of a non-global warming fluid
that is processed from the vegetable beetroot. There is no
limitation to the material 90. By varying the antifreeze
concentration level of the material 90, the antifreeze eutectic
freezing temperature is set as desired. For example, a higher
eutectic freezing temperature is used in air conditioning for
chilling in the range of 25 F to 30 F, while a medium eutectic
freezing temperature is used in air conditioning for chilling in
refrigerators in the range of 15 to 20 F as needed for fresh meats,
dairy products, and a low eutectic freezing temperature is used in
air conditioning for chilling in refrigerators in the range of 35 F
to -18 F, typically in freezers for frozen meats, fish, poultry,
etc.
[0048] It is fully anticipated that the first refrigerant be the
same or different to the second refrigerant and either refrigerant
is any know refrigerant in the industry. As a first example, the
first refrigerant is Co2 fluid (R-744) and the second refrigerant
is propane or ammonia (Nh3). As a second example, both the first
refrigerant and second refrigerant is Co2 fluid (R-744).
[0049] Referring to FIG. 2, a perspective view of an air
conditioning system 10 with auxiliary thermal storage 20 is shown.
The auxiliary air conditioning system 10 adds thermal storage 20 to
an air conditioning system and, therefore, it is anticipated that
in some embodiments, the thermal storage 20 is integrated or
retrofitted into any existing air conditioning system.
[0050] The exemplary auxiliary air conditioning system includes
thermal storage 20 that will be further described with FIGS. 3 and
5. The auxiliary air conditioning system includes one or more
typical compressors 40 (two are shown as an example), typically
driven by an electric motor for home and office, but there is no
limitation to the type of compressor(s) 40 and the way the
compressor(s) 40 is/are driven (e.g., by a gasoline engine). The
compressor(s) 40 have a low pressure suction line (vapor inlet
line) 72 through which warm, gaseous refrigerant is received from
the thermal storage 20 and/or the inside air handlers 70. The
compressors 40 then compress this gaseous refrigerant into a liquid
state at a high pressure which is then transferred to the outside
air heat exchanger 50 through high pressure pipes 42 where the
liquid refrigerant is cooled by a flow of outside air over a series
of fins, as known in the industry. The now cold, liquid
refrigerant, under pressure, flows through the high pressure line
74 to both the thermal storage 20 and the evaporators 70.
[0051] In one mode of operation, the cold, liquid refrigerant flows
through the heat transfer tubes 82 within the thermal storage 20.
As the refrigerant changes state from a liquid to a gas
(evaporates) within the heat transfer tubes 82, heat is extracted
from the material 90 within the thermal storage 20, lowering the
temperature of the material 90. At a certain temperature (freezing
point of the material 90 based upon the physical properties of the
material 90), the material 90 changes phase from a liquid to a
solid. This phase change requires cooling energy above that needed
to simply lower the temperature of the material 90, and therefore,
stores that additional energy until the now solid material 90 warms
above a certain temperature (melting point based upon the physical
properties of the material 90).
[0052] Note that many typical components of a traditional air
conditioning compressor 40 and outside air exchanger 50 such as
reversing valves, thermal expansion devices, check valves,
fans/motors to flow air over the fins, fins, etc., are not shown
for clarity purposes as they are well known in the art.
[0053] The inside air handler 70 (coils, fins, motors not shown for
clarity reasons) is located in the structure to be cooled such as
in a living space, freezer compartment, refrigerator, vehicle
passenger compartment, etc. When the compressor 40 is operating,
the inside air handler receives cooled, liquid refrigerant through
the second high-pressure line 74. The liquid refrigerant evaporates
(changes state to a gas refrigerant) within the coils of the inside
air handler 70 thereby extracting heat (e.g., cooling) air that
flows through the coils. The now gaseous refrigerant exits the
inside air handler 70 through the suction line 72 and is again
compressed by the compressor(s) 40, etc.
[0054] When the compressor 40 is operating, thereby phase changing
and compressing the refrigerant from a gaseous state to a high
pressure, cold state and routing the high pressure, cooled
refrigerant through the first high-pressure line 74 and into the
inside air handler 70. At the same time, some of the cooled
refrigerant enters the thermal storage 20, either further cooling
the material 90 or cooling the material 90 sufficiently to cause at
least some of the material 90 to phase change into a solid. In some
embodiments, a valve 31 (e.g. solenoid valve 31) is opened when
conditions are right for charging the thermal storage 20 such as
when electricity rates are low or when outside ambient temperatures
are favorable. When the valve 31 is closed, all high pressure,
cooled refrigerant is directed to the air handler 70 to cool the
structure. In embodiments, the valve 31 is closed when electricity
rates are high or when outside ambient temperatures are not
favorable.
[0055] At such times when sufficient cold heat is stored in the
thermal storage 20 and it is determined that it is not favorable to
operate the compressor(s) 40 (e.g. during high cost electricity
periods or higher outside ambient temperatures), instead of
operating the compressor(s) 40, a pump 34 (e.g., a LPA Liquid
Pressure Amplification) pump 34) is operated to pump liquid
refrigerant through a collection tube 22 from the thermal storage
and into the high pressure line 74 through a high pressure
connecting tube 28. This liquid refrigerant enters the inside air
handler 70 and evaporates in the coils within the inside air
handler 70, thereby extracting heat from air passing over these
coils (e.g., cooling). The now gaseous refrigerant flows back into
the thermal storage 20 through the low pressure tube 72, where it
interacts with the low temperatures within the material 90 of the
thermal storage 20, thereby condensing back into a liquid
refrigerant.
[0056] Referring to FIGS. 3 and 5, perspective views of the
internals of the auxiliary thermal storage 20 are shown. Within the
thermal storage 20, are a series of thermal fins 84 having one or
more heat transfer tubes 82. An example of the construction of such
thermal fins 84 and heat transfer tubes 82 are shown in FIG.
11.
[0057] At a lower end of the heat transfer tubes 82 (lower with
respect to gravity) is a high-pressure thermal storage collection
tube 86 through which, cool liquid refrigerant is collected by the
plurality of heat transfer tubes 82 through forces of gravity.
[0058] The volume of thermal battery is determined by application,
for example, in some embodiments, the volume is one square
meter.
[0059] In the embodiment shown, the heat transfer tubes 82 are
mounted on plates 84 and the heat transfer tubes 82 are thermally
interfaced to the plates 84, although in other embodiments it is
anticipated that the heat transfer tubes are without plates 84. By
thermally interfacing the heat transfer tubes 82 to the plates 84,
cool heat flows readily between the two and into the material 90
within the thermal storage 20.
[0060] The material 90 is contained within an outer shell 92 that,
preferably, includes a good thermal insulator. It is also preferred
that the outer shell 92 be water tight so the material 90 does not
exit and, for when materials 90 expand and contract, it is also
preferred that the outer shell 92 be structurally sound as to not
break under pressure of the material 90. It is anticipated that in
some embodiments, the outer shell 92 be a set of layers of sealing
materials, thermally insulating materials, and/or structural
materials in any order, composition, and combination.
[0061] Within the thermal storage 20, are a series of thermal fins
84 having one or more heat transfer tubes 82. At a lower end of the
heat transfer tubes 82 (lower by gravity) is a high-pressure
thermal storage distribution tube 86 through which, cool liquid
refrigerant is distributed to the plurality of heat transfer tubes
82. At an upper end of the heat transfer tubes 82 is a low-pressure
exit collection tube 80.
[0062] The heat transfer tubes 82 are mounted on plates 84 and the
heat transfer tubes 82 are thermally interfaced to the plates 84.
By thermally interfacing the heat transfer tubes 82 to the plates
84, cool heat flows readily between the two (e.g., low thermal
resistance).
[0063] The heat transfer tubes 82 and plates 84 are within a
material 90 (e.g., at least partially submerged) and the material
is contained in an enclosure 92 that is preferably thermally
insulated, thereby keeping cool heat stored within the material 90
from escaping to the ambient outside of the enclosure 92.
[0064] Although any number of heat transfer tubes 82 and plates 84
are anticipate, thereby dictating the overall volume and size of
the enclosure 92, in one embodiment the thermal storage 20 is
approximately three square meters in size. In some embodiments,
each plate 84 has 3 parallel heat transfer tubes 82 and a
conductance square surface area of around 900 square millimetres on
each side. In some embodiments, the heat transfer tubes 82 are made
from 3/8'' standard refrigeration soft drawn copper tube and are
pressed between the plates and bonded as described in FIG. 11. A
modular framework holds the plates 84.
[0065] The volume of thermal battery is determined by application,
for example, in some embodiments, the volume is one square
meter.
[0066] In the embodiment shown, the heat transfer tubes 82 are
mounted on plates 84 and the heat transfer tubes 82 are thermally
interfaced to the plates 84, although in other embodiments it is
anticipated that the heat transfer tubes are without plates 84. By
thermally interfacing the heat transfer tubes 82 to the plates 84,
cool heat flows readily between the two and into the material 90
within the thermal storage 20.
[0067] The material 90 is contained within an outer shell 92 that,
preferably, includes a good thermal insulator. It is also preferred
that the outer shell 92 be water tight so the material 90 does not
exit and, for when materials 90 expand and contract, it is also
preferred that the outer shell 92 be structurally sound as to not
break under pressure of the material 90.
[0068] Referring to FIGS. 4 and 6, internals of the in-line thermal
storage 120 are shown. As discussed with FIGS. 3 and 5, within the
thermal storage 120, are a series of thermal fins 84a/84b having
one or more heat transfer tubes 82a/82b. There are two independent
sets of thermal fins 84a/84b and respective heat transfer tubes
82a/82b. The first set of thermal fins 84a and heat transfer tubes
82a interface to the compressor(s) 40 and outside air handler 50
and, while the compressor(s) 40 operates, the first refrigerant in
a liquid state is flows into the first set of heat transfer tubes
82a from the high pressure line 24 and heat is extracted from the
material 90 within the thermal storage 120. As heat is extracted,
the first refrigerant evaporates within the first set of heat
transfer tubes 82a and exits into the suction tube 25 to return to
the compressor(s) 40 and outside air handler 50.
[0069] The second set of thermal fins 84b and heat transfer tubes
82b interface to the pump 34, an optional storage tank 60, and an
inside air handler 70. When cooling is required and the pump 34
operates, the second refrigerant in a liquid state collects (e.g.,
by gravity) and flows out of the second set of heat transfer tubes
82b to high pressure line 22 which is in fluid communication with
either the pump 34 or the storage tank 60. The pump 34 forces the
cold, second refrigerant into the inside air handler 70 through
high pressure tubes 74 where the second refrigerant evaporates as
it extracts heat from air flowing through the inside air handler
70. The now gaseous second refrigerant then flows through the low
pressure line 72 back into the second set of thermal fins 84b where
the second refrigerant condenses due to the cold temperatures of
the material 90.
[0070] The heat transfer tubes 82a/82b are mounted on thermal fins
84a/84b and the heat transfer tubes 82a/82b are thermally
interfaced to the thermal fins 84a/84b, providing lower thermal
resistance between the refrigerants and the material 90 within the
thermal storage 120. Although not required, it is preferred that
the first set of thermal fins 84a alternate with the second set of
thermal fins 84b to equally cool the material 90 within the thermal
storage 120 and to equally extract cold heat from the material 90
within the thermal storage 120. Although shown as an equal number
of the first thermal fins 84a and the second thermal fins 84b,
there is no requirement for an equal number. For example, in some
embodiments there are three of the first thermal fins 84a and four
of the second thermal fins 84b, etc.
[0071] The heat transfer tubes 82a/82b and thermal fins 84a/84b are
within a material 90 (e.g., at least partially submerged) and the
material is contained in an enclosure 92 that is preferably
thermally insulated, thereby keeping cool heat stored within the
material 90 from escaping to the ambient outside of the enclosure
92.
[0072] Although any number of heat transfer tubes 82a/82b and
thermal fins 84a/84b are anticipate, thereby dictating the overall
volume and size of the enclosure 92, in one embodiment the thermal
storage 120 is approximately one square meters in size. In some
embodiments, each thermal fin 84a/84b has 3 parallel heat transfer
tubes 82a/82b and a conductance square surface area of around 900
square millimetres on each side. In some embodiments, the heat
transfer tubes 82a/82b are made from 3/8'' standard refrigeration
soft drawn copper tube and are pressed between the plates and
bonded as shown in FIG. 11. It is anticipated, though not required,
that a modular framework supports the thermal fins 84a/84b,
maintaining proper location and separation.
[0073] The material 90 is selected, for example, as an antifreeze
and water solution of a specific concentration that will provide
the desired freezing and operating temperature.
[0074] Referring to FIGS. 7 and 7A, schematic views of in-line air
conditioning system 10a with in-line thermal storage 120 are shown.
In the in-line air conditioning system 10 with thermal storage 120,
the thermal storage 120 has two banks of heat transfer tubes
82a/82b for transferring cold heat to/from a refrigerant there
within. The first set of the heat transfer tubes 82a transfer
refrigerant to/from the compressor(s) 40 and outside air handler
50. The second set of heat transfer tubes 82b transfer refrigerant
to/from the inside air handler 70 by way of the pump 34. In this
way, two independent types and chemistries of refrigerant are
allowed, though in some embodiments, the refrigerant flowing
through the first set of heat transfer tubes 82a is the same
refrigerant flowing through the second set of heat transfer tubes
82b.
[0075] The in-line air conditioning system includes thermal storage
120 as described with FIGS. 4 and 6. The in-line air conditioning
system includes one or more typical compressors 40. The
compressor(s) 40 have a low pressure suction line (vapor inlet
line) 25 through which warm, gaseous refrigerant is received from
the thermal storage 120. The compressors 40 then compress this
gaseous refrigerant into a liquid state at a high pressure which is
then travels through tubes 42 and through the outside air heat
exchanger 50 where the liquid refrigerant is cooled by a flow of
outside air over a series of fins (not shown), as known in the
industry. The now cold, liquid refrigerant, under pressure, flows
through the high pressure line 24 and into the thermal storage 120.
As the cold, liquid refrigerant flows through the first set of the
heat transfer tubes 82a within the thermal storage 120, the
refrigerant changes state from a liquid to a gas (evaporates),
extracting heat (thermal energy) from the material 90 within the
thermal storage 120, lowering the temperature of the material 90.
At a certain temperature (freezing point of the material 90 based
upon the physical properties of the material 90), the material 90
changes phase from a liquid to a solid. This phase change requires
cooling energy above that needed to simply lower the temperature of
the material 90, and therefore, stores that additional energy until
the now solid material 90 warms above a certain temperature
(melting point based upon the physical properties of the material
90). For completeness, an optional thermal expansion valve 21 is
shown
[0076] An inside air handler 70 (coils, fins, motors not shown for
clarity reasons) is located in the structure to be cooled such as
in a living space, freezer compartment, refrigerator, vehicle
passenger compartment, etc. The inside air handler 70 is similar or
the same as such known in the industry.
[0077] In the example of FIG. 7, the compressor 40 is operated at a
time desired (e.g. when electricity rates are lower) until the
material 90 within the thermal storage 120 achieves the desired
temperature. While the compressor 40 runs, cold first refrigerant
from the compressor 40 and outside air handler 50 flows through the
first set of heat transfer tubes 82a within the thermal storage 120
and cools and/or freezes the material 90 within the thermal storage
120. Once the desired temperature of the material 90 within the
thermal storage 120 is achieved, the compressor 40 is stopped,
requiring little or no further power.
[0078] Now, as the second refrigerant in gaseous form enters the
thermal storage 120, the second refrigerant contacts the cold
second set of heat transfer tubes 82b and condenses into a liquid
and collects at the bottom of the heat transfer tubes 82b into a
transfer tube 22 by gravitational force.
[0079] When cooling is required within the structure as determined
by, for example, a thermostat or other temperature sensing device,
the condensed, liquefied second refrigerant from the thermal
storage 120 is pumped from the transfer tube 22 and into the inside
air handler 70 through a high pressure line 74. The inside air
handler 70 receives the cooled, liquid second refrigerant through
the second high-pressure line 74 and the liquid second refrigerant
evaporates (changes state to a gas refrigerant) within the coils of
the inside air handler 70, providing cool air within the structure
(e.g., home, office, refrigerator). The now gaseous second
refrigerant exits the inside air handler 70 through a second
suction line 72 and returns to the thermal storage 120 where it is
again cooled and liquefied.
[0080] Again, as the temperature of the material 90 within the
thermal storage 120 rises, determinations are made as to whether
the compressor 40 should be run. For example, if the outside air
temperature is at an ideal temperature or if electricity rates are
low, the compressor is run to cool the material 90 to the desired
temperature. If the conditions are not right (e.g. electricity
rates are high or outside air temperatures are not ideal), running
of the compressor 40 is suppressed until cooling is no longer
possible with the remaining cold heat energy stored in the thermal
storage 120.
[0081] In the example of FIG. 7A, the compressor 40 is operated at
a time desired (e.g. when electricity rates are lower) until the
material 90 within the thermal storage 120 achieves the desired
temperature (e.g., phase changes into a solid). While the
compressor 40 runs, cold first refrigerant from the compressor 40
and outside air handler 50 flows through the first set of heat
transfer tubes 82a within the thermal storage 120 and cools and/or
freezes the material 90 within the thermal storage 120. Once the
desired temperature of the material 90 within the thermal storage
120 is achieved, the compressor 40 is stopped, requiring little or
no further power.
[0082] Now, as the second refrigerant in gaseous form enters the
thermal storage 120, the second refrigerant contacts the cold
second set of heat transfer tubes 82b and condenses into a liquid.
The condensed, cold liquefied second refrigerant collects by
gravity and flows through tubes 22 into a storage tank 60
(preferably insulated storage tank 60 or a Liquid Refrigerant
Receiver 60 as known in the industry). As any of the second
refrigerants within the storage tank 60 evaporate, the gaseous
second refrigerant flows through another tube 26 back into the
thermal storage 120 where is it then condensed as described
above.
[0083] The liquefied second refrigerant within the storage tank 60
is in fluid communications with a pump 34 through a tube 30. When
cooling is required within the structure as determined by, for
example, a thermostat or other temperature sensing device, the
condensed, liquefied second refrigerant from the storage tank 60 is
pumped into the inside air handler 70 through a high pressure line
74 and optionally, a thermal expansion valve 73. The inside air
handler 70 receives the cooled, liquid second refrigerant through
the second high-pressure line 74 and the liquid second refrigerant
evaporates (changes state to a gas refrigerant) within the coils of
the inside air handler 70. The now gaseous second refrigerant exits
the inside air handler 70 through a second suction line 72 and
returns to the storage tank 60, and eventually to the thermal
storage 120 where it is again cooled and liquefied. Again, an
optional thermal expansion valve 73 is shown for completeness.
[0084] As the temperature of the material 90 within the thermal
storage 120 rises, determinations are made as to whether the
compressor 40 should be run. For example, if the outside air
temperature is at an ideal temperature or if electricity rates are
low, the compressor is run to cool the material 90 to the desired
temperature. If the conditions are not right (e.g. electricity
rates are high or outside air temperatures are not ideal), running
of the compressor 40 is suppressed until cooling is no longer
possible with the remaining cold heat energy stored in the thermal
storage 120.
[0085] In a preferred embodiment, the liquid pump 34 is an LPA
(Liquid Pressure Amplification) pump 34. Although a single thermal
storage 120 is shown in FIGS. 1 and 1A, smaller, larger, serial
and/or parallel thermal storage 120 are anticipated.
[0086] In some embodiments, the material 90 within the thermal
storage is a chemical-based antifreeze material such as ethylene
glycol or a mixture of such antifreeze material and water for
achieving the desired phase change temperature (e.g., freezing
point). In some embodiments, the material 90 is made of a
non-global warming fluid that is processed from the vegetable
beetroot. There is no limitation to the material 90. By varying the
antifreeze concentration level of the material 90, the antifreeze
eutectic freezing level is set as desired. For example, a higher
eutectic freezing temperature is used in air conditioning for
chilling in the range of 25 F to 30 F, while a medium eutectic
freezing temperature is used in air conditioning for chilling in
refrigerators in the range of 15 to 20 F as needed for fresh meats,
dairy products, and a low eutectic freezing temperature is used in
air conditioning for chilling in refrigerators in the range of 35 F
to -18 F, typically in freezers for frozen meats, fish, poultry,
etc.
[0087] It is fully anticipated that the first refrigerant be the
same or different to the second refrigerant and either refrigerant
is any know refrigerant in the industry. As a first example, the
first refrigerant is Co2 fluid (R-744) and the second refrigerant
is propane or ammonia (Nh3). As a second example, both the first
refrigerant and second refrigerant is Co2 fluid (R-744).
[0088] Referring to FIG. 8, a schematic view of the air
conditioning system 10 with auxiliary thermal storage 20 is shown.
It is envisioned that, in some embodiments, the auxiliary air
conditioning system 10 adds thermal storage 20 to an existing air
conditioning system and, therefore, it is anticipated that the
thermal storage 20 be integrated into any new or existing air
conditioning system.
[0089] The compressor 40 receives warm, gaseous refrigerant from
the thermal storage 20 through the low pressure suction line (vapor
inlet line) 72 and/or the inside air handlers 70. The compressor 40
then compress this gaseous refrigerant into a liquid state at a
high pressure which is then transferred to the outside air heat
exchanger 50 through high pressure pipes 42 where the liquid
refrigerant is cooled by a flow of outside air over a series of
fins, as known in the industry. The now cold, liquid refrigerant,
under pressure, flows through the high pressure line 74 to both the
thermal storage 20 and the evaporators 70.
[0090] In one mode of operation, the cold, liquid refrigerant flows
through the heat transfer tubes 82 within the thermal storage 20.
As the refrigerant changes state from a liquid to a gas
(evaporates) within the heat transfer tubes 82, heat is extracted
from the material 90 within the thermal storage 20, lowering the
temperature of the material 90. At a certain temperature (freezing
point of the material 90 based upon the physical properties of the
material 90), the material 90 changes phase from a liquid to a
solid. This phase change requires cooling energy above that needed
to simply lower the temperature of the material 90, and therefore,
stores that additional energy until the now solid material 90 warms
above a certain temperature (melting point based upon the physical
properties of the material 90), at which time the cool heat energy
is released.
[0091] The inside air handler 70 (coils, fins, motors not shown for
clarity reasons) is located in the structure to be cooled such as
in a living space, freezer compartment, refrigerator, vehicle
passenger compartment, etc. When the compressor 40 is operating,
the inside air handler receives cooled, liquid refrigerant through
the high-pressure line 74. The liquid refrigerant evaporates
(changes state to a gas refrigerant) within the coils of the inside
air handler 70 thereby cooling air that flows through the coils.
The now gaseous refrigerant exits the inside air handler 70 through
the suction line 72 and is again compressed by the compressor 40,
etc.
[0092] When the compressor 40 is operating, thereby phase changing
and compressing the refrigerant from a gaseous state to a high
pressure, cold state and routing the high pressure; cooled
refrigerant flows through the first high-pressure line 74 and into
the inside air handler 70. At the same time, some of the cooled
refrigerant enters the thermal storage 20, either further cooling
the material 90 or cooling the material 90 sufficiently to cause at
least some of the material 90 to phase change into a solid.
[0093] At such times when sufficient cold heat is stored in the
thermal storage 20 and it is determined that it is not favorable to
operate the compressor 40 (e.g. during high cost electricity
periods or higher outside ambient temperatures), instead of
operating the compressor 40, a optional valve 30 (e.g. solenoid
valve 30) is opened and a pump 34 (e.g., a LPA Liquid Pressure
Amplification pump 34) is operated to pump liquid refrigerant
through a collection tube 22 from the thermal storage 20 and into
the high pressure line 74 through a high pressure connecting tube
28. This liquid refrigerant enters the inside air handler 70 and
evaporates in the coils within the inside air handler 70, thereby
extracting heat from air passing over these coils (e.g., cooling).
The now gaseous refrigerant flows back into the thermal storage 20
through the low pressure tube 72, where it interacts with the low
temperatures within the material 90 of the thermal storage 20,
thereby condensing back into a liquid refrigerant.
[0094] Although one valve 30 is shown, any number of valves are
anticipated to control the flow of the refrigerant. For example, in
some embodiments, a valve is inserted in the high pressure line 24
between the high pressure line 74 and the thermal storage 20 to
prevent cold, liquid refrigerant from flowing into the thermal
storage 20 during periods of high electricity costs, and opened
when conditions are right for storing cold heat in the thermal
storage 20. Likewise, it is anticipated that in some embodiments,
another valve or a check valve is inserted in the high pressure
line 74 towards the outside air handler 50 to prevent the cold,
liquid refrigerant from flowing from the pump 34 back into the
outside air handler 50.
[0095] Referring to FIG. 9, a schematic view of an exemplary
processing device 100 as used within the air conditioning system 10
with thermal storage 20/120 is shown. The exemplary processing
device 100 represents a typical processor system as used with the
air conditioning system 10 with thermal storage 20/120, though it
is known in the industry to utilize logic in place of processors
and vice versa. This exemplary processing device 100 is shown in
its simplest form. Different architectures are known that
accomplish similar results in a similar fashion and the air
conditioning system 10 with thermal storage 20/120 is not limited
in any way to any particular system architecture or implementation.
In this exemplary processing device 100, a processor 170 executes
or runs programs from a random access memory 175. The programs are
generally stored within a persistent memory 174 and loaded into the
random access memory 175 when needed. The processor 170 is any
processor, typically a processor designed for portable devices. The
persistent memory 174, random access memory 175 interfaces through,
for example, a memory bus 172. The random access memory 175 is any
memory 175 suitable for connection and operation with the selected
processor 170, such as SRAM, DRAM, SDRAM, RDRAM, DDR, DDR-2, etc.
The persistent memory 174 is any type, configuration, capacity of
memory 174 suitable for persistently storing data, for example,
flash memory, read only memory, battery-backed memory, magnetic
memory, etc. In some exemplary processing devices 100, the
persistent memory 174 is removable, in the form of a memory card of
appropriate format such as SD (secure digital) cards, micro SD
cards, compact flash, etc.
[0096] Also connected to the processor 170 is a system bus 182 for
connecting to peripheral subsystems such as output drivers 184 and
inputs 189/192 such as inputs from a temperature sensor 140 or
other controls, etc. The output drivers 184 receive commands from
the processor 170 and control the operation of the various
components of the air conditioning system 10 with thermal storage
20/120, for example, the compressor 40, the air handler 70 and the
pump 34.
[0097] In general, some portion of the memory 174 is used to store
programs, executable code, and data. In some embodiments, other
data is stored in the memory 74 such as tables and settings,
etc.
[0098] The peripherals and sensors shown are examples and other
devices are known in the industry such as Global Positioning
Subsystems, speakers, microphones, USB interfaces, Bluetooth
transceivers 94, Wi-Fi transceivers 96, image sensors, temperature
sensors, etc., the likes of which are not shown for brevity and
clarity reasons.
[0099] In some embodiments, the exemplary processing device 100
interfaces to a wireless transmitter or transceiver (e.g.,
Bluetooth radio transceiver 94, a Wi-Fi radio transceiver 96, or
both) for communication with local wireless devices such as
personal computers and wireless sensors/thermostats.
[0100] Referring to FIG. 10, a flow chart of an exemplary software
system running on processing device 100 as used in conjunction with
the air conditioning system 10 with thermal storage is shown
20/120.
[0101] In this exemplary flow, the system 10 waits 202 until there
is a need for cooling (e.g., a temperature within the structure
being cooled raises above a programmed temperature as measured by a
temperature sensor 140). Once the need for cooling is determined
202, a test 204 is made to determine if it is better to use stored
cold heat or to capture cold heat from the outside ambient air. As
an example, it is better to use stored cold heat when the outside
ambient air temperature is above a certain point or when energy
rates (e.g. electricity costs) are high (e.g., in areas in which
rates vary by time-of-day). If the test 204 concludes that it is
best to use stored cold heat, another test 220 is performed to
determine is sufficient cold heat is available in the thermal
storage 20/120. If either the test 204 determines that it is better
to use stored cold heat or the test 220 determines there is not
sufficient cold heat is available in the thermal storage 20/120,
the compressor 40, outside air handler 50, and inside air handler
70 are operated 206 until the need for cooling abates 208 (e.g., a
temperature within the structure being cooled goes below above a
second programmed temperature as measured by a temperature sensor
140), at which time the compressor 40, outside air handler 50, and
inside air handler 70 are shut off.
[0102] If the second test 220 determines that there is sufficient
cold heat is available in the thermal storage 20/120, instead of
operating the compressor 40, the pump 34 and inside air handler 70
are turned on 222 and operate until it is determined 224 that the
need for cooling has stopped (e.g., a temperature within the
structure being cooled goes below above a second programmed
temperature as measured by a temperature sensor 140), at which time
the pump 34 and inside air handler 70 are turned off 226.
[0103] Note, flows shown are examples, as it is known to include
additional steps to sequence operations (e.g., starting the fans in
the air handlers 50/70 before starting the compressor 40) and
delaying operation of the compressor 40 for a period of time after
the compressor 40 is stopped to prevent failures. It is also
anticipated that any system based on a processor 100 is equally
feasible implemented as logic, for example, in a logic array,
etc.
[0104] Referring to FIG. 11, a perspective view of an exemplary
thermal fin design is shown. In this example, three parallel
thermal fins 84 are shown comprising two complimentary aluminum
sheets 84x/84y. The connecting tube 80 connects individual heat
transfer tubes 82. The heat transfer tubes 82 are sandwiched
between the complimentary aluminum sheets 84x/84y, thereby
providing good thermal conductance between the heat transfer tubes
82/82a/82b and the thermal fins 84/84a/84b. In some embodiments,
the heat transfer tubes are 3/8'' standard refrigeration soft drawn
copper tubes pressed between the complimentary aluminum sheets
84x/84y and bonded. In some embodiments, the heat transfer tubes
are copper tubes that are oval in cross-sectional shape instead of
the expected round cross-sectional shape.
[0105] Although any suitable materials are anticipated, examples of
materials for the heat transfer tubes 82/28a/82b are copper or
aluminum. Likewise, examples of materials for the thermal fins
84/84a/84b are also copper or aluminum.
[0106] It is anticipated that, in some embodiments, the thermal
fins 84/84a/84b are supported by a modular framework.
[0107] Although described in the above examples as a system for
cooling, it is known to reverse such systems and the described
examples operate in reverse as expected.
[0108] Equivalent elements can be substituted for the ones set
forth above such that they perform in substantially the same manner
in substantially the same way for achieving substantially the same
result.
[0109] It is believed that the system and method as described and
many of its attendant advantages will be understood by the
foregoing description. It is also believed that it will be apparent
that various changes may be made in the form, construction and
arrangement of the components thereof without departing from the
scope and spirit of the invention or without sacrificing all of its
material advantages. The form herein before described being merely
exemplary and explanatory embodiment thereof. It is the intention
of the following claims to encompass and include such changes.
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