U.S. patent application number 12/829060 was filed with the patent office on 2011-06-30 for heat exchange system.
This patent application is currently assigned to TRIEA SYSTEMS, LLC. Invention is credited to Matthew Ginalick, JR., James O'Brien.
Application Number | 20110154838 12/829060 |
Document ID | / |
Family ID | 44185812 |
Filed Date | 2011-06-30 |
United States Patent
Application |
20110154838 |
Kind Code |
A1 |
O'Brien; James ; et
al. |
June 30, 2011 |
HEAT EXCHANGE SYSTEM
Abstract
A modular heat exchange system having a refrigerant system for
cycling a refrigerant through a compressor, a condenser, an
expansion valve, and an evaporator, a heat source circulation
system which circulates a heat exchange fluid between a heat source
and the evaporator, a heat sink circulation system which circulates
a heat absorption fluid between a heat sink and the condenser, a
heat exchanger for exchanging thermal energy between one of the
heat exchange fluid or the heat absorption fluid; and a neutral
tank, wherein the one of the heat exchange fluid or the heat
absorption fluid is deposited in the neutral tank upon returning
from the heat exchanger.
Inventors: |
O'Brien; James; (Bethesda,
MD) ; Ginalick, JR.; Matthew; (Mount Airy,
MD) |
Assignee: |
TRIEA SYSTEMS, LLC
BETHESDA
MD
|
Family ID: |
44185812 |
Appl. No.: |
12/829060 |
Filed: |
July 1, 2010 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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12752585 |
Apr 1, 2010 |
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12829060 |
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12543268 |
Aug 18, 2009 |
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12752585 |
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Current U.S.
Class: |
62/132 ;
62/235.1; 62/238.6 |
Current CPC
Class: |
F25B 2400/24 20130101;
F28D 7/024 20130101; F28D 20/0034 20130101; F24D 11/0214 20130101;
F25B 2339/047 20130101; F24D 19/1066 20130101; F24D 17/02 20130101;
F25B 30/06 20130101 |
Class at
Publication: |
62/132 ;
62/238.6; 62/235.1 |
International
Class: |
F25B 49/00 20060101
F25B049/00; F25B 27/00 20060101 F25B027/00 |
Claims
1. A modular heat exchange system comprising: a refrigerant system
which cycles a refrigerant through a compressor, a condenser, an
expansion valve, and an evaporator; a heat source circulation
system which circulates a heat exchange fluid between a heat source
and the evaporator; a heat sink circulation system which circulates
a heat absorption fluid between a heat sink and the condenser; a
heat exchanger for exchanging thermal energy between one of the
heat exchange fluid or the heat absorption fluid; and a neutral
tank, wherein the one of the heat exchange fluid or the heat
absorption fluid is deposited in the neutral tank upon returning
from the heat exchanger.
2. The modular heat exchange system of claim 1, wherein the
refrigerant is R-410A.
3. The modular heat exchange system of claim 1, wherein the heat
exchange fluid is water.
4. The modular heat exchange system of claim 1, wherein the heat
absorption fluid is water.
5. The modular heat exchange system of claim 1, wherein the heat
source circulation system further comprises a fluid flow conduit
connecting the heat source to the evaporator.
6. The modular heat exchange system of claim 1, wherein the heat
exchanger comprises hydronic coils.
7. The modular heat exchange system of claim 1, wherein the heat
source is a body of water.
8. The modular heat exchange system of claim 7, wherein the body of
water is contained in a heat source storage tank.
9. The modular heat exchange system of claim 1, wherein the heat
sink is a body of water contained in a heat sink storage tank.
10. The modular heat exchange system of claim 1, further comprising
a thermal energy source, wherein thermal energy is transferred from
the thermal energy source to the heat exchange fluid when the core
temperature of the heat source falls below a threshold temperature
while the core temperature of the heat sink is maintained at a
constant temperature.
11. The modular heat exchange system of claim 10, wherein the heat
absorption fluid is cycled through the solar energy thermal unit to
maintain the core temperature of the heat sink.
12. The modular heat exchange system of claim 11, further
comprising a first valve and a second valve, wherein the first
valve and the second valve work in tandem to cycle only one of the
heat exchange fluid and the heat absorption fluid through the solar
energy thermal unit.
13. The modular heat exchange system of claim 1, wherein the heat
sink is one of a primary heat sink or a secondary heat sink.
14. The modular heat exchange system of claim 13, further
comprising a first sink valve and a second sink valve, wherein the
first sink valve and the second sink valve work in tandem to cycle
the heat absorption fluid to only one of the primary heat sink and
the secondary heat sink.
15. The modular heat exchange system of claim 14, wherein the heat
absorption fluid is cycled to the secondary heat sink when the core
temperature in the primary heat sink determined by the second
temperature gauge rises above a threshold temperature while the
core temperature of the heat source determined by the first
temperature gauge is maintained at a constant temperature.
16. The modular heat exchange system of claim 10, wherein the
thermal energy source is a solar energy thermal unit.
17. The modular heat exchange system of claim 1, wherein the heat
exchange fluid is supplied to the evaporator by the neutral
tank.
18. The modular heat exchange system of claim 1, wherein the heat
absorption fluid is supplied to the condenser by one of the neutral
tank or the heat sink.
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This is a Continuation-in-Part of application Ser. No.
12/752,585 filed Apr. 1, 2010, now pending, which is a
Continuation-in-Part of application Ser. No. 12/543,268 filed Aug.
18, 2009, now pending. The disclosures of the prior applications
are hereby incorporated by reference herein in their entirety.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] Aspects of the present invention relate to a portable and
scalable heat exchange system. More particularly, aspects of the
invention relate to a high-efficiency water-to-water heat exchange
system for providing an efficient, portable, and/or scalable
heating and/or cooling source.
[0004] 2. Background of the Technology
[0005] FIG. 1 shows an exemplary vapor-compression refrigeration
cycle 2 used in many heat exchange systems, in which a refrigerant
is circulated through a closed-loop compression and expansion
cycle. As shown in FIG. 1, the refrigerant begins as a vapor at
point A. During Phase 1 of the cycle, the refrigerant vapor is
compressed and circulated by a compressor 10, resulting in a
high-pressure, high-temperature refrigerant vapor. The
electro-mechanical energy of the compressor 10 is also converted
into heat energy carried by the refrigerant vapor, which exits the
compressor 10 as a superheated vapor. During Phase 2 of the cycle,
the superheated vapor passes through a condenser 20 where a heat
exchange process pulls heat energy from the superheated vapor,
causing the refrigerant to condense into a high-pressure liquid. As
shown at Phase 3 of the cycle, the hot liquid refrigerant is then
directed through a thermal expansion valve 30, which meters the
flow of refrigerant to the evaporator 40 and usually results in a
flash lowering of the pressure and temperature of the condensed hot
liquid refrigerant. As a result, the low-pressure, low-temperature
liquid or saturated liquid/vapor refrigerant enters the evaporator
40 during Phase 4 of the cycle, wherein a second heat exchange
process draws heat energy from a heat source, such as water or air,
to the refrigerant, causing the refrigerant to reach a saturation
temperature and returning the refrigerant to the vapor state at
point A. The cycle is repeated.
[0006] In many conventional residential heat pump systems, for
example, for supplying heat, the heat exchanging condenser 20
extracts heat energy from the superheated refrigerant vapor during
Phase 2 of the cycle by using a blower 50 to direct cool air across
condenser coils carrying the hot vapor (see FIG. 1). The cool air
conducts heat energy from the coils and the heated air is supplied
by the blower through ducting, for example, to directly heat the
home or residence. The evaporator, on the other hand, typically
relies on the air temperature outside the home for drawing heat
into the refrigerant during Phase 4 of the cycle.
[0007] For supplying cool air, the blower 50 may instead be used to
direct hot air across evaporator coils carrying the cooler fluid
refrigerant during Phase 4 of the cycle 2. The cooler fluid
refrigerant conducts heat energy from the hot air, and the
resulting cooler air may be supplied to the home. Under such
circumstances, the condenser 20 relies on the outside air to cool
the superheated vapor during Phase 2 of the vapor-compression cycle
2
[0008] In some conventional systems, the heat pump may be designed
with a reversible valve and specialized heat exchangers, for
example, allowing the vapor-compression cycle 2 to operate in
either direction, with each heat exchanger serving as either a
condenser or an evaporator. The cycle of the heat pump can thus be
reversed, so that, depending on the desired climate, a single
blower may be used to direct hot or cool air across coils, for
example, carrying the cooler refrigerant fluid or the superheated
refrigerant vapor, respectively.
[0009] A typical air-source heat pump, as described above, works
harder to transfer heat from a cooler place to a warmer place as
the temperature difference increases between the cooler and warmer
places. Accordingly, the performance of an air-source heat pump
deteriorates significantly, for example, during the winter months
in a very cold climate, as the temperature difference between the
air outside a home becomes significantly less than the desired
temperature inside the home.
[0010] A ground source heat pump system, which typically extracts
heat from the ground, or a body of water, may be used to counteract
the effect of significant temperature gradients between the heat
source and the heat sink. This is because the ground below a
certain depth, and water below a certain level, maintains a fairly
constant temperature year round, leading to generally lower
temperature differentials throughout significant periods of the
year, allowing for increased performance of the heat pump. As shown
in FIG. 2, the vapor-compression cycle 2 described in FIG. 1 may be
coupled with a ground source loop 3 that carries a heat exchange
fluid, such as water, for example. The heat exchange fluid conducts
heat while flowing through conduits 4 buried in the ground or sunk
under a body of water 5. A portion of the heat carried by the heat
exchange fluid in the conduits 4 is transferred to the cooler
liquid refrigerant by conduction through a heat exchange process
performed by the evaporator 40 during Phase 4 of the
vapor-compression cycle 2. The refrigerant is vaporized, and the
refrigerant vapor is then compressed during Phase 1 of the
vapor-compression cycle. As described previously, a blower 50 may
be used to direct cool air across condenser coils while carrying
the hot vapor during Phase 2 of the vapor-compression cycle 2 in
order to provide heat to the interior of a structure. Additionally,
a heat sink loop 6 may be coupled with the condenser 20 to capture
heat transferred from the heat exchange fluid during Phase 4 of the
vapor-compression cycle 2, along with heat that is added through
the electro-mechanical energy input by the compressor 10 during
Phase 1 of the vapor-compression cycle 2, into a heat sink 60,
which could be a tank of hot water, for example. The condensed
refrigerant exiting the condenser 20 is then expanded during Phase
3 of the vapor-compression cycle 2 and the cooler refrigerant
liquid enters the evaporator 40 once again to draw more heat from
the heat exchange fluid flowing through the ground source loop
3.
[0011] A typical ground source system, such as the ground source
loop 3 described above, is expensive to construct and can be
extremely disruptive to install because thousands of feet of piping
may need to be placed in horizontally dug trenches or wells dug
vertically deep into the ground, to effectively tap into the
thermal energy contained therein. And although the thermal
conductivity of water is greater than that of the ground, generally
allowing for less piping to be placed into a body of water, access
to a body of water close enough to the home for the purpose of
creating a ground source system is often unfeasible.
[0012] There exists a need for a heat exchange system which
combines the efficiencies of the thermal conductivity of a fluid,
such as water and a specially tuned vapor-compression cycle to
produce an efficient, portable, and scalable heat exchange system
for simultaneously providing heating and/or cooling.
SUMMARY OF THE INVENTION
[0013] Aspects of the present invention provide for a heat exchange
system that combines a thermally conductive fluid and a specially
tuned vapor-compression cycle in an extremely efficient, modular,
portable, and scalable system for providing superior heat exchange
capabilities for heating and/or cooling in almost any environment.
As a result, the heat exchange system in accordance with aspects of
the present invention may be disassembled and assembled with ease
and without causing damage to the structural components of the
system to permit convenient installation in residential, commercial
and industrial settings. Aspects of the present invention include
operation of the system using a portable generator, allowing
deployment in remote locations, such as forward operating military
outposts, or to provide heating, cooling, hot water and chilled
water to people in need around the world, such as victims in
disaster relief centers and in refugee camps.
[0014] Aspects of the invention, and, in particular, the increased
performance of the efficiently designed heat exchange system,
including an automated fluid management system, permit enhanced
heating and cooling while creating a significantly reduced
footprint on the environment over conventional heating and cooling
systems that rely on fossil fuels to function.
[0015] Additional advantages and novel features of aspects of the
invention will be set forth in part in the description that
follows, and in part will become more apparent to those skilled in
the art upon examination of the following or upon learning by
practice of the invention.
BRIEF DESCRIPTION OF THE FIGURES
[0016] FIG. 1 shows an exemplary vapor-compression cycle as
typically used in heat exchange systems;
[0017] FIG. 2 shows an exemplary ground source heat pump system as
is known in the prior art;
[0018] FIG. 3 shows a system flow diagram of a heat exchange
system, in accordance with aspects of the present invention;
[0019] FIG. 4 shows a perspective view of an exemplary heat
exchange system, in accordance with aspects of the present
invention;
[0020] FIG. 5 shows an enlarged view of various components of the
exemplary heat exchange unit, in accordance with aspects of the
present invention;
[0021] FIG. 6 shows a cutaway view of an exemplary heat sink, in
accordance with aspects of the present invention;
[0022] FIG. 7 is a system flow diagram of an exemplary heat
exchange system with an integrated fluid management system; and
[0023] FIG. 8 is a system flow diagram of an exemplary heat
exchange system with an integrated fluid management system.
DETAILED DESCRIPTION
[0024] FIG. 3 is an exemplary flow diagram in accordance with
aspects of the present invention. The heat exchange system 100
comprises a vapor-compression refrigeration cycle having a
compressor 110, a condenser 120, an expansion valve 130, and an
evaporator 140. Although many different refrigerants may be used,
the refrigerant R-410A, a mixture of difluoromethane and
pentafluoroethane, is preferred for its thermodynamic properties
and because R-410A does not contribute to ozone depletion. As will
be described in further detail, R-410A typically operates at higher
pressures than most refrigerants, requiring increased strength in
certain components of the system.
[0025] As shown in FIGS. 3 and 4, a heat source 200, such as a tank
of water, may be provided to work in tandem with the heat exchange
system 100 to supply heat energy during Phase 4 of the
vapor-compression cycle 2. The heat source 200 may alternatively be
a nearby lake or stream, for example. The heat source 200 may be
connected to the heat exchange system 100 through a circulation
system 210, which may be a closed-loop or open-loop system for
circulating a heat exchange fluid, such as water. The circulation
system 210 may include a pump 215, for example, for circulating the
heat exchange fluid from the heat source 200, through the
evaporator 140 and back to the heat source 200. Fluid flow valves
216, such as ball or butterfly valves, may be installed on either
side of the pump 215, to allow for fluid flow to the pump 215 to be
shut off during assembly, or during repair and/or replacement of
the pump 215. Fluid flow conduits 217 for carrying the heat
exchange fluid 205 through the circulation system 210 may include
rigid and/or flexible tubing made of a thermally conductive
material, such as copper or a modified polyethylene, for example.
As shown in FIG. 4, the fluid flow conduits 217 may include
flexible tubing exterior to the heat exchange system 100, copper or
brass tubing, for example, inside of the heat exchange system 100,
and hard plastic tubing, for example, to form a coiled section of
the evaporator 140.
[0026] As indicated by the longer arrows in the enlarged view of
FIG. 5, the heat exchange fluid 205 is forced by the pump 215 to
flow through the stacked coil section 142 of the evaporator 140 in
a specified direction. The heat exchange function of the evaporator
140 is accomplished by concurrently running a cold refrigerant
conduit 132, which exits the expansion valve 130, through the
stacked coil section 142 of the evaporator 140. The cold
refrigerant conduit 132 enters the evaporator 140 at an evaporator
entrance junction 134 and exits the evaporator at an evaporator
exit junction 136. The cold refrigerant conduit 132 follows, and is
contained within, the stacked coil section 142 of the evaporator
140. The cold refrigerant conduit 132 is ideally situated to permit
the entire outer surface area of the cold refrigerant conduit 132
to be in direct contact with the warmer heat exchange fluid 205
flowing through the stacked coil section 142. Accordingly,
increased thermal conduction from the heat exchange fluid during
Phase 4 of the vapor-compression cycle 2 is provided by the
aforementioned arrangement of the structural components.
[0027] As shown in FIG. 5, the refrigerant flow entering the
evaporator 140 has just completed Phase 3 of the vapor-compression
cycle, in which the hot refrigerant fluid has passed through the
expansion valve 130 and experienced a rapid decrease in pressure
and temperature. As shown with the smaller arrows in FIG. 5, the
cooler refrigerant fluid flows through the cold refrigerant conduit
132 in the same direction as the warmer heat exchange fluid flows
through the stacked coil section 142 of the evaporator 140. The
concurrent tubular flow creates a variable temperature gradient
over the length of the stacked coil section 142, in which the
refrigerant absorbs the heat energy of the heat exchange fluid at a
greater rate nearer the evaporator entrance junction 134 than
towards the evaporator exit junction 136. The cold refrigerant
conduit 132 follows, and is contained within, the stacked coil
section 142 of the evaporator 140. The refrigerant and the heat
exchange fluid both approach an equilibrium temperature as the
fluids flow in parallel through the respective conduits in the
evaporator 140. The refrigerant has thus completed Phase 4 of the
vapor-compression cycle, and, as a vapor, is now ready to enter the
compressor 110.
[0028] As shown in FIGS. 3 and 4, the compressor 110, which may be
a reciprocating or scroll compressor, for example, supplies the
electro-mechanical energy to compress the vapor into a superheated
vapor during Phase 1 of the vapor-compression cycle 2. A heat sink
300, such as a tank of water, may be provided to work in tandem
with the heat exchange system 100 to store the amplified heat
energy extracted from the heat exchange fluid during Phase 4 of the
vapor-compression cycle 2. The heat sink 300 may be connected to
the heat exchange system 100 through a heat sink circulation system
310, which may be a closed-loop or open-loop system for circulating
a heat absorption fluid 305, such as water. The heat sink
circulation system 310 may include a pump 315, for example, for
circulating the heat absorption fluid from the heat sink 300,
through the condenser 120 and back to the heat sink 300. Fluid flow
valves 316, such as ball or butterfly valves, may be installed on
either side of the pump 315, to allow for fluid flow to be shut off
to the pump 315 during assembly, or during repair and/or
replacement of the pump 315. Fluid flow conduits 317 for carrying
the heat absorption fluid through the heat sink circulation system
310 may include rigid and/or flexible tubing made of a thermally
conductive material, such as copper or a modified polyethylene, for
example. As shown in FIG. 4, the fluid flow conduits 317 may
include rigid copper tubing, for example, insulated to protect heat
loss during circulation of the heat absorption fluid through the
heat sink circulation system 310.
[0029] As indicated by the longer arrows in the enlarged view of
FIG. 5, the heat absorption fluid is forced by the pump 315 to flow
through the stacked coil section 122 of the condenser 120 in a
specified or predetermined direction. The heat exchange function of
the evaporator 120 is accomplished by concurrently running a hot
refrigerant conduit 112, which exits the compressor 110, through
the stacked coil section 122 of the condenser 120. The hot
refrigerant conduit 112 enters the condenser 120 at a condenser
entrance junction 114 and exits the condenser at a condenser exit
junction 116. The hot refrigerant conduit 112 follows, and is
contained within, the stacked coil section 122 of the condenser
120. The hot refrigerant conduit 112 is ideally situated to permit
the entire outer surface area of the hot refrigerant conduit 112 to
be in direct contact with the cooler heat absorption fluid flowing
through the stacked coil section 122 of the condenser 120. This
enables increased thermal conduction from the superheated
refrigerant vapor during Phase 2 of the vapor-compression cycle
2.
[0030] As shown in FIG. 5, the refrigerant flow entering the
condenser 120 has just completed Phase 1 of the vapor-compression
cycle, in which the refrigerant vapor was compressed by the
compressor 110 and experienced a rapid increase in temperature. As
shown with the smaller arrows in FIG. 5, the superheated
refrigerant vapor flows through the hot refrigerant conduit 112 in
an opposite direction relative to the cooler heat absorption fluid
flowing through the stacked coil section 122 of the condenser 120.
The countercurrent tubular flow maintains a nearly constant
temperature gradient over the length of the stacked coil section
122, in which heat is conducted from the superheated refrigerant
vapor into the cooler heat absorption fluid at nearly the same rate
near the condenser entrance junction 114 as at the condenser exit
junction 116. Particularly with the use of water as the heat
absorption fluid, for example, which has a relatively high thermal
conductivity, the countercurrent flow in the condenser 120 allows
efficient transfer of a substantial portion of the heat energy
drawn from the heat exchange fluid, as well as the work energy
input from the compressor 110, into the heat sink 300.
[0031] In accordance with aspects of the present invention, a
second condenser (not shown) may be provided between the condenser
120 and the expansion valve 130. In this region of the
refrigeration cycle, sometimes referred to as the sub cool region,
the refrigerant may still retain a certain amount of thermal energy
that was not transferred to the heat absorption fluid during the
exchange process in the first condenser 120. Accordingly, the
second condenser may be provided to draw additional thermal energy
from the refrigerant into a fluid that may be circulated back to
the heat source 200. The warm fluid may thus transfer the
additional thermal energy back into the heat source 200 for storage
and further use as described above.
[0032] The heat exchange system of the present invention draws on
the thermal energy contained in the heat source 200, which may be a
tank of water at ambient temperature, for example, and by way of
the vapor-compression cycle 2, deposits the withdrawn thermal
energy efficiently into the heat sink 300, which may be another
tank of water, for example. The heat sink 300 may thus reach
temperatures of more than 150.degree. F. As shown in FIG. 4, the
hot water in the heat sink 300 may be drawn and pumped through
pipes 400 to a radiant heating system, for example, or a hydronic
coil and blower arrangement that is connected to a ducting system,
in order to provide a constant and efficient source of heat for the
interior of a structure. In addition, a domestic hot water storage
tank 500 may be connected to the heat sink 300 to heat exchange
thermal energy into the hot water storage tank 500 for potable
water use.
[0033] FIG. 6 shows an enlarged cutaway view of an exemplary heat
sink 300 in accordance with aspects of the present invention. The
fluid flow conduits 317, which may be wrapped in insulating
material to prevent the escape of thermal energy to the
environment, may run from the heat sink 300 to the heat exchange
system 100 and back to complete a closed loop, for example.
Additionally, a heat exchange coil 318, comprised of copper, or any
other suitable material having high thermal conductivity, may be
provided inside the heat sink 300 to facilitate heat exchange from
the hot water in the fluid flow conduits 317 into the heat sink
300. The hot water may then be drawn into the pipes 400 to supply a
radiant heating system, for example.
[0034] As shown in FIG. 6, the domestic hot water storage tank 500
may connect to the heat sink 300 by pipes 502, which may be
insulated, to conduct heat from the hot water in the heat sink 300
by way of heat exchange coils 504, also placed in the heat sink
300. As such, the domestic hot water system may be completely
separate from the heat sink circulation system 310, the efficient
heat exchange system thus providing the thermal energy for potable
hot water use in a safe and cost-effective manner.
[0035] As shown in FIGS. 3 and 4, in accordance with aspects of the
present invention, an electronic control unit (ECU) 540 may be
provided to control operation of the compressor 110 and the
circulation pumps 215 and 315. The ECU 540 may operate with one or
more thermostats, for example, to maintain the system in an
efficient operating range. For instance, the ECU 540 may set the
compressor 110 and the circulation pumps 215 and 315 to run if the
temperature of the water in the heat sink 300 drops below a certain
efficiency threshold temperature, for example, or alternatively, if
the temperature of the water in the heat source 200 rises above a
certain efficiency threshold temperature. In another aspect of the
present invention, as shown in FIG. 3, a thermal energy source 220
may provide supplemental thermal energy to the heat source cycle
when a temperature gauge in the heat source 200 indicates to the
ECU 540 that the temperature of the heat source 200 has dropped
below a predetermined efficiency threshold. The thermal energy
source 220 may be any suitable source for heating the heat exchange
fluid 205, such as a conventional hot water heating element of a
predetermined wattage, for example, placed within the fluid flow
conduit 217. Other exemplary thermal energy sources in accordance
with aspects of the present invention may include the abundant heat
sources in restaurants from which the thermal energy can be drawn
upon and deposited, through heat exchangers, for example, into the
heat source 200. Using a hydronic coil, piping and pumps, for
example, the heat retained in the elevator penthouses of buildings
can be transferred into the heat source cycle. Any ready source of
heat that can be practically transferred into the heat source 200
may be used as the thermal energy source 220, including "hot spots"
found in swimming pools, drain pipes, transformer rooms, data
centers, computer rooms, and the upper space in certain
high-ceiling rooms, to name just a few. The techniques to capture
and transfer the thermal energy from a thermal energy source 220
may typically include hydronic systems, but any suitable method of
transferring thermal energy from a secondary source of heat to the
heat source 200 is contemplated herein.
[0036] As shown in FIG. 4, in accordance with aspects of the
present invention, the heat exchange system 100 may be fitted with
an electronic pressure control unit 550. In combination with one or
more pressure transducers 552, the electronic pressure control unit
550 may be set up to monitor the sensed pressure at any point in
the system, including the intake (suction) pressure and the
discharge (head) pressure of the compressor 110. Accordingly,
measurement of the evaporator pressure and/or the condenser
pressure can provide valuable insight into the efficiency of the
system and whether the refrigerant charge is too low or excessive,
for example. As shown in FIGS. 3 and 5, a sight glass 135 may also
be used to aid in the inspection of the refrigerant charge level,
as bubbles in the line generally indicate an undercharge. The sight
glass 135 is preferably located on the high-pressure liquid side of
the compressor 110. In another aspect of the present invention, as
shown in FIG. 3, a filter drier 137 may be installed in the
refrigerant path, preferably on the high-pressure liquid side of
the compressor 110, to adsorb unwanted moisture in the refrigerant
cycle.
[0037] According to aspects of the present invention, the
refrigerant charge in the vapor-compression cycle 2 may be
precisely determined in accordance with a length of the refrigerant
run and the desired characteristics of a well-balanced heat
exchange system. The R-410A refrigerant charge may be intentionally
set to a level that allows the system to continue to operate at
maximum efficiency, while increasing the discharge temperature of
the superheated vapor discharged from the compressor 110. The
unexpected results of the present invention call for a
substantially lower refrigerant charge than normal to achieve the
desired results of an efficient heat transfer between the heat
source 200 and the heat sink 300.
[0038] The use of R-410A enhances the ability to increase the
temperature on the discharge side of the compressor 110, but
requires much higher pressures to operate compared to previously
used refrigerants. For example, to achieve a condensing temperature
value of 140.degree., an R-410 high-side pressure must approach 550
psi. In other words, for the heat absorption fluid running through
the condenser coil section 122, which is generally maintained at a
temperature of 140.degree. or higher, to condense the superheated
vapor of the refrigerant in the conduit 116, the pressure on the
condenser side of the heat exchanger must approach 550 psi or
higher. By using a scroll compressor 110 rated to handle 650 psi
before disengaging, and using tubes and fittings rated to withstand
the elevated temperatures and pressures of an R-410A charged
system, the heat exchange system 100 can handle the higher
pressures required to produce the higher compressor discharge
temperatures necessary to ensure heat exchange occurs in the
condenser at temperatures above 140.degree. F.
[0039] As heat energy is transferred from the heat source 200 to
the heat sink 300, the temperature of the heat source 200 lowers.
Depending on the heat load demand, and the size of the body of
water, for example, that is serving as the heat source 200, the
temperature of the heat source 200 may drop significantly. Due to
the parallel, concurrent tubular flow design of the evaporator 140,
and the ability to generally maintain the heat source 200 in an
ambient environment, the liquid refrigerant typically draws enough
latent heat to effectively boil the liquid refrigerant and deliver
vapor with enough pressure to the compressor 110 to function highly
efficiently. In fact, a slight lowering of the refrigerant charge
so that the intake side pressure is slightly lowered, while still
preventing liquid refrigerant from being delivered to the
compressor 110, may slightly elevate the compression ratio of the
compressor 110. The higher compression ratio in turn may transfer
more compression energy to the refrigerant during compression
resulting in an even higher discharge temperature so that the heat
absorption fluid can be heated to even higher temperatures.
[0040] The colder heat source 200 may also be used as a cooling
medium for chilling water or providing cool air by employing the
same water-to-water or water-to-air heat transfer means discussed
above with respect to the hot water side. For example, hydronic
coils, which draw upon the cold water created in the heat source
200, may be used in combination with a fan to blow hot air across
the hydronic coils to produce cooler air for the air conditioning
of a particular structure. Similarly, as in the case of a domestic
hot water tank, a separate cold water heat exchange system and
storage tank, for example, can provide chilled water for a variety
of uses.
[0041] Features in accordance with aspects of the present invention
include configuring the components of the heat exchange system 100
to be compact, modular and/or portable, for example. As shown in
FIG. 4, a housing unit 600 may have multiple shelves 601 and 602
for vertically stacking and/or creating compartments for the
storage and mounting of the various components of the heat exchange
system 100, such as the compressor 110, the condenser 120, the
expansion valve 130, and the evaporator 140. Various quick install
features may be included to enable the easy installation and/or
disassembly of the heat source 200 and/or the heat sink 300,
including hose bibs (not shown), for example, for quickly
connecting/disconnecting the fluid flow conduits 217 and 317 to the
heat exchange system 100. Mounting brackets may be provided to
allow for quick and efficient mounting of the various components,
such as the compressor 110, the condenser 120, the evaporator 140
and the circulation pumps 215 and 315. Rubber padding, insulation,
panels, doors and/or a cover may be provided that permit easy
assembly/disassembly and access to the interior components for
maintenance, while reducing the vibration, sound and heat loss that
may be generated during operation of the heat exchange system 100.
The housing unit 600 may be provided with a surface for mounting an
integrated electric panel. As such, the heat exchange system may be
prewired and ground to the integrated electric panel to provide a
single, efficient connection to an external power source. Light
Emitting Diode (LED) panels may be mounted to the housing unit to
provide visible operational feedback to an observer with respect to
various aspects or components of the heat exchange system 100.
[0042] By maintaining the modularity and portability of the heat
exchange system 100, the unit 100 may be transported to and
employed easily in remote locations. A generator may be used for
producing the electricity needed by the compressor 110 and the
circulation pumps 215 and 315, and access to a water source may
provide both a heat source 200 and a heat sink 300 for heating and
cooling purposes.
[0043] FIG. 7 depicts aspects of an exemplary fluid management
system 700 in accordance with the present invention that may be
integrated with various aspects the heat exchange system 100 to
provide precision balance and control for efficiently managing the
varying heating and cooling load demands for an enclosed structure,
for example. The housing unit 600 may house the primary components
of the vapor compression cycle 2, such as the compressor 110, the
condenser 120, the expansion valve 130, the evaporator 140, the
pumps 215 and 315, and/or the ECU 540. The heat source circulation
system 210 includes the heat source 200, which may be a 225 gallon
water tank, for example, connected to the evaporator 140 in the
housing unit 600 by fluid flow conduits 217. The heat sink
circulation system 310 includes the heat sink 300, which may be a
55 gallon water tank, for example, connected to the condenser 120
in the housing unit 600 by fluid flow conduits 317. The heat sink
circulation system 310 may include a secondary heat sink 350, which
may be a 160 gallon water tank, for example, also connected to the
condenser 120 in the housing unit 600. Three way valves 360 and 365
may be provided to control the fluid flow between the primary and
secondary heat sinks, 300 and 350 respectively. The valves 360 and
365 are controlled to operate in tandem so that when the valve 360
shuts off fluid flow in the direction of the heat sink 300 and
instead directs the fluid flow to the secondary heat sink 350, the
valve 365 opens to receive the fluid flow from the secondary heat
sink 350 and is closed to receiving fluid flow from the heat sink
300. Similarly, when the valve 360 shuts off the fluid flow in the
direction of the secondary heat sink 350 and instead directs the
fluid flow to the heat sink 300, the valve 365 opens to receive the
fluid flow from the heat sink 300 and is closed to receiving fluid
flow from the secondary heat sink 350. In this manner, the heat
exchange system 100 may select either the heat sink 300 or the
secondary heat sink 350 into which to deposit the thermal energy
drawn from the heat source 200.
[0044] The components of the fluid management system 700, in
conjunction with the components of the heat exchange system 100,
must be sized appropriately to achieve a symbiotic balance between
the thermal mass of the heat sinks 300 and 350, any associated hot
side heat exchange systems, the thermal mass of the heat source
200, and any associated cold side heat exchange systems, while
accommodating the varying heating and cooling load demands. Factors
such as ambient outdoor temperatures during summer and winter
months, construction materials used for building the structure,
including insulation and windows, and the habits of inhabitants or
tenants, for example, may have a large impact on the various system
configurations used to calibrate the heat exchange system in
response to the required heating and cooling load demands.
[0045] As shown in FIG. 7, a heat source temperature gauge 230 may
be provided to monitor a core temperature of the heat source 200.
Similarly, temperature gauges 302 and 352 may be provided to
respectively monitor core temperatures of the heat sink 300 and the
secondary heat sink 350. The various temperature gauges 230, 302
and 352 may communicate with the ECU 540 by a set of relay
switches, or any suitable circuit devices, including wireless
thermostats, for example.
[0046] In this manner, the fluid management system 700 operates in
balanced synchronization with the heat exchange system 100 by
monitoring the core temperatures of the heat source 200 and the
heat sinks 300 and 350. For example, under normal temperate
conditions, the temperature of the heat source 200 may be
maintained to have a core temperature reading between 45 and
60.degree. F. by cycling the heat exchange system 100 as required
while the heat sink 300 maintains a temperature of 140.degree. F.
However, during colder winter months in many areas, the increased
draw of stored thermal energy from the heat source 200 in order to
keep the heat sink 300 at a particular temperature, 140.degree. F.
for example, may drop the temperature of the heat source 200 below
a threshold temperature, impacting the efficiency of the heat
exchange system 100. In particular, the ability for the heat
exchange process in the evaporator 140 to function efficiently may
be impacted. As such, the fluid management system 700 may be set to
signal the ECU 540 to turn on the heater 220 when the heat source
temperature gauge 230 reads a core temperature below 38.degree. F.,
for example. Under these circumstances, the ECU 540 may be
programmed, for example, to continue operation of the heat exchange
system 100 until the heater 220 provides enough supplemental
thermal energy to the fluid flow to raise the core temperature of
the heat source 200 to a preset threshold winter temperature,
45.degree. F. for example.
[0047] Another feature in accordance with aspects of the present
system may be the inclusion of a supplemental solar heating system
800 to provide yet another source of thermal energy during peak
heating demand, such as during the winter months and/or during
times of peak hot water demand, for example. As shown in FIG. 7,
the supplemental solar heating system 800 may be configured to
operate in tandem with either the heat sink 300 or the heat source
200 through a heat exchange process in which solar thermal units
convert solar energy into thermal heat energy that is supplied to
the fluid flow of the heat exchange system 100. Three way valves
810 and 820 may be provided to control the fluid flow between the
solar heating system 800 and either the heat sink 300 or the heat
source 200, respectively. The valves 810 and 820 are controlled to
operate in tandem so that when the valve 810 shuts off fluid flow
in the direction of the heat sink 300 and instead directs the fluid
flow to the heat source 200, the valve 820 opens to receive the
fluid flow from the heat source 200 and is closed to receiving
fluid flow from the heat sink 300. Similarly, when the valve 810
shuts off the fluid flow in the direction of the heat source 200
and instead directs the fluid flow to the heat sink 300, the valve
820 opens to receive the fluid flow from the heat sink 300 and is
closed to receiving fluid flow from the heat source 200. In this
manner, the heat exchange system 100 may select either the heat
sink 300 or the heat source 200 as the beneficiary of the thermal
energy produced by the solar thermal units of the supplemental
solar heating system 800.
[0048] During peak summer months in many areas, for example, where
the need for cool air may drive a peak demand on the heat exchange
system 100 for chilled water, the fluid management system 700 may
be programmed to maintain the core temperature of the heat source
200 at a lower threshold summer temperature, 38.degree. F. for
example. Under these circumstances, the amount of thermal energy
drawn from the heat source 200 may raise the core temperature of
the heat sink 300 to levels too high for the condenser heat
exchange process to function efficiently. To keep the condenser
section operating at lower temperatures, the fluid management
system 700 may thus be controlled to open the valve 360 in the
direction of the secondary heat sink 350 to direct fluid from the
condenser 120 to the larger secondary heat sink 350 rather than the
heat sink 300. Concurrently, the fluid management system 700 is
controlled to open the valve 365 to receive fluid from the
secondary heat sink 350 rather than from the heat sink 300. In this
manner, the secondary heat sink 350 may serve as a large depository
of excess thermal energy during peak cooling demand, allowing the
system to maintain the core temperature of the heat source 200 at a
lower desirable temperature without distressing the efficiency of
the system.
[0049] Another feature in accordance with aspects of the present
invention may include providing a further mechanism for drawing off
excess thermal energy in the event that the secondary heat sink 350
also reaches a core temperature considered too elevated for the
efficient operation of the condenser 120 of the heat exchange
system 100. A pipe or conduit may be provided so that fluid can be
pumped from the secondary heat sink 350 to an area where a fan
and/or hydronic coils may be used to transfer the excess energy to
an ambient air environment external to the structure, for
example.
[0050] Another feature in accordance with aspects of the present
invention may include providing a neutral tank to the configuration
of the heat exchange system 100. For example, as shown in FIG. 8, a
neutral tank 900 may be configured to operate in combination with
the fluid management system 700 to serve as a temperature buffer
for the heat sinks 300 and 350 and the heat source 200. Because
many aspects of the heat exchange system 100 and the fluid
management system 700 will function as described above, a majority
of the structure and functional aspects of the heat exchange system
100 and the fluid management system 700 are not repeated here.
[0051] The piping of the heat exchange system 100 and fluid
management system 700 may be modified, for example, to accommodate
the introduction of the neutral tank 900. As shown in FIG. 8, the
neutral tank 900 may be configured to respectively segregate the
fluid flow to the heat exchangers 120 and 140 from the fluid flow
returning from the heat exchange system, such as a hydronic coil
and air handling system, or other secondary heat exchangers, used
to heat and/or cool an objective space. For example, the heat
source circulation system 210 may be configured so that the heat
exchange fluid is supplied to the evaporator 140 from the neutral
tank 900, with the heat exchange fluid being returned from the
evaporator 140 directly to the cold tank. Similarly, the heat sink
circulation system 310 may be configured so that the heat
absorption fluid is supplied to the condenser 120 from one of the
heat sinks 300, 350 or the neutral tank 900, or a combination of
the heat sinks 300, 350 and the neutral tank 900, and the heat
absorption fluid is returned from the condenser 120 directly to the
heat sink 300 or 350. Moreover, the heat exchange fluid returning
from the hydronic coils, for example, that is used to heat or cool
the objective space may be deposited directly into the neutral tank
900. In this manner, both the heat sinks 300, 350 and the heat
source 200 may be spared from the influence of the reduced or
elevated temperature of the fluid returning from the heat exchange
process (e.g., hydronic coils and air handler) that resulted in the
respective heating or cooling of the objective space.
[0052] For example, during cool months, the temperature of the
fluid supplied from the heat sink(s) 300, 350 to the hydronic coils
is reduced through the heat exchange process in order to supply
heat to the objective space. As a result, the neutral tank 900
permits the cooler fluid returning from the hydronic coils to be
deposited into the neutral tank 900, rather than back into the heat
sink(s) 300, 350. Similarly, during warmer months, the temperature
of the fluid supplied from the heat source 200 to the hydronic
coils is elevated through the heat exchange process (e.g., hydronic
coils and air handler) in order to cool the objective space. As a
result, the neutral tank 900 permits the warmer fluid to be
deposited into the neutral tank 900, rather than back into the heat
source 200. In this manner, the heat sinks 300, 350 and the heat
source 200 may deliver fluid at temperatures that have not been
tempered by fluid returning from the heat exchange process used to
heat or cool the objective space. Thus, the fluid delivered to the
hydronic coils, for example, may be maintained at temperatures that
are more effective for heating or cooling of the structure, while
the temperatures of the fluids in the heat sinks 300, 350 and heat
source 200 may be more consistently controlled, enhancing the
operation and efficiency of the system. The neutral tank 900 may
thus buffer the heat sinks 300, 350 and the heat source 200 from
large fluctuations in temperatures that may be associated with peak
system demand, for example. In turn, the operation and efficiency
of the heat exchangers 120 and 140 may be effectively controlled
due to the consistent maintenance of the temperatures of the heat
exchange fluids supplied from the heat sinks 300,350 and the heat
source 200. Although described above as a tank, the neutral tank
900 may be any suitable receptacle for the storage and maintenance
of a heat exchange medium in accordance with aspects of the present
invention.
[0053] While this invention has been described in conjunction with
the exemplary aspects outlined above, various alternatives,
modifications, variations, improvements, and/or substantial
equivalents, whether known or that are or may be presently
unforeseen, may become apparent to those having at least ordinary
skill in the art. Accordingly, the exemplary aspects of the
invention, as set forth above, are intended to be illustrative, not
limiting. Various changes may be made without departing from the
spirit and scope of the invention, including increasing the size of
various components, including the heat source, the heat sinks,
and/or the neutral tank, for example, to scale the system
appropriately for different applications. Therefore, the invention
is intended to embrace all known or later-developed alternatives,
modifications, variations, improvements, and/or substantial
equivalents.
* * * * *