U.S. patent application number 09/203567 was filed with the patent office on 2002-02-14 for integrated system for heating, cooling and heat recovery ventilation.
Invention is credited to BAILEY, LOUIS J., HAAN, RALPH.
Application Number | 20020017107 09/203567 |
Document ID | / |
Family ID | 22073969 |
Filed Date | 2002-02-14 |
United States Patent
Application |
20020017107 |
Kind Code |
A1 |
BAILEY, LOUIS J. ; et
al. |
February 14, 2002 |
INTEGRATED SYSTEM FOR HEATING, COOLING AND HEAT RECOVERY
VENTILATION
Abstract
An integrated compression based heating/cooling, humidification
and mid or high efficiency heat recovery ventilation system is
provided. The integrated system is a centralized apparatus that
offers a very efficient method for heating/cooling with more winter
and summer humidity control plus offering heat recovery ventilation
in a structure having a regulated indoor temperature and specific
ventilation/energy recovery rate. The heating and cooling section
of the apparatus would most commonly be configured as a forced air
geothermal or air-to-air heat pump. The heat recovery ventilation
section of the apparatus will incorporate a heat recovery chamber
complete with a primary passive cross flow heat recovery core.
Plus, a secondary refrigeration based high efficiency reversible
energy recovery evaporator/condenser coil. The integrated system
will also incorporate a humidification system designed to operate
during the winter heating season.
Inventors: |
BAILEY, LOUIS J.; (LIDERTON,
CA) ; HAAN, RALPH; (STRATHROY, CA) |
Correspondence
Address: |
R CRAIG ARMSTRONG
ARMSTRONG & ASSOCIATES
385 FOUNTAIN STREET SOUTH
CAMBRIDGE
N3H1J2
CA
|
Family ID: |
22073969 |
Appl. No.: |
09/203567 |
Filed: |
December 2, 1998 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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60067141 |
Dec 2, 1997 |
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Current U.S.
Class: |
62/238.7 ;
165/240; 165/54; 237/2B; 62/238.6; 62/90; 62/93 |
Current CPC
Class: |
F24F 5/0046 20130101;
F24F 3/14 20130101; F24F 6/14 20130101; F25B 30/06 20130101; F25B
2313/021 20130101; Y02B 30/56 20130101; F24F 2012/007 20130101;
Y02B 30/52 20130101; F24F 12/006 20130101; F25B 40/04 20130101;
F24F 5/001 20130101; Y02B 10/40 20130101; F25B 13/00 20130101; F24F
12/003 20130101; F25B 2313/02741 20130101; Y02B 30/563 20130101;
F24F 3/001 20130101 |
Class at
Publication: |
62/238.7 ;
165/54; 165/240; 62/90; 62/93; 62/238.6; 237/2.00B |
International
Class: |
F24H 003/02; F25D
017/06; F25B 027/00; F25B 029/00 |
Claims
What is claimed as the invention is:
1. An integrated forced air heating, cooling, and heat recovery
ventilation apparatus for a space, said apparatus comprising, in
combination within one system: a stale air return inlet connectable
to stale air return ducting, a stale air exhaust outlet connectable
to stale air exhaust ducting, a fresh air inlet connectable to
fresh air inlet ducting, a fresh air outlet connectable to an
indoor supply air duct, and an air-to-air heat exchanger connected
to said stale and fresh air elements to exchange heat between stale
air and fresh air; a mechanical vapor compression based heating and
cooling means positioned between an indoor return air duct and said
indoor supply air duct, for selectively heating or cooling air; and
a heat recovery ventilation system.
2. Apparatus as recited in claim 1, further comprising an
integrated humidification system.
3. Apparatus as recited in claim 1, where said system is
unitary.
4. Apparatus as recited in claim 1, where said system is split.
5. Apparatus as recited in claim 1, where said mechanical vapor
compression based heating and cooling means comprises a geothermal
closed loop means using a closed underground loop as an energy
source and transferred to the space through a vapor compression
heat pump system.
6. Apparatus as recited in claim 1, where said mechanical vapor
compression based heating and cooling means comprises a geothermal
open well means using an open well or water as an energy source and
transferred to the space through a vapor compression heat pump
system.
7. Apparatus as recited in claim 1, where said mechanical vapor
compression based heating and cooling means comprises a water
source using a pre-existing open or internal closed loop water
supply as an energy source and transferred to the space through a
vapor compression heat pump system.
8. Apparatus as recited in claim 1, where said mechanical vapor
compression based heating and cooling means comprises air to air
means using outdoor air as an energy source and transferred to the
space through a vapor compression heat pump system.
9. Apparatus as recited in claim 1, where said heat recovery
ventilation section comprises a primary passive heat exchanger
core.
10. A system as recited in claim 1, further comprising an
integrated humidification system.
11. Apparatus as recited in claim 1, further comprising a
reversible evaporator/condenser secondary heat exchanger.
12. Apparatus as recited in claim 10, further comprising a
reversible evaporator/condenser secondary heat exchanger.
13. Apparatus as recited in claim 1, further comprising a hot air
quick defrost system.
14. Apparatus as recited in claim 1, further comprising an
integrated condensate drain assembly for a vapor compression system
and a heat recovery ventilator.
15. Apparatus as recited in claim 1, having an air mixing chamber
to mix and distribute heated or cooled fresh air from a heat
recovery ventilation and vapor compression systems.
16. An integrated heating, cooling and heat recovery ventilation
system substantially as described in the preceding description and
in the drawings.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] This invention relates to systems for heating, cooling,
humidification and heat recovery ventilation.
[0003] 2. Description of the Prior Art
[0004] To date, heating, cooling, humidification and heat recovery
ventilation (HRV) have been accomplished by using three or even
four separate pieces of equipment. In the situation where four
pieces of equipment are used, the common method would include a
standard fossil fuel type furnace, a central or window air-to-air
type air conditioner, a duct mounted humidifier and a heat recovery
ventilator (HRV). When three pieces of equipment are used the
heating and cooling system would be one of the components,
generally referred to as a geothermal or air-to-air reversible heat
pump, while the humidification and heat recovery ventilation would
be accomplished with two separate pieces of equipment. In the
aforementioned instances the ducting, condensate draining, wiring,
fusing and controls are needed for each system individually. There
is no way to increase the efficiency with existing systems because
they are separate components, so the capital cost and operating
efficiencies which could be gained by integration are not
available.
[0005] The presently available HRV equipment commonly uses a
passive cross-flow core or a desiccant wheel core or a Freon-filled
direct exchange core, complete with various types of defrost
methods. The defrost methods presently available include an
electric defrost or various configurations of damper defrost. The
electric defrost element which is usually located in the fresh air
supply stream generally starts to operate at approximately -5
degrees C (23 degrees F). It will then cycle on and off until -15
degrees C (5 degrees F) at which time it is on until the
temperature warms up to above -15 degrees C (5 degrees F). The
electric defrost method is obviously inefficient from an operating
cost perspective because of the cost to run the electrical
elements. The damper type defrost is more widely accepted, as the
method of choice. However, there are drawbacks to the existing
systems. One method of damper defrost includes closing a damper on
the fresh air intake while opening a damper to draw pre-warmed air
from the inside of the space. As the pre-warmed air flows through
the HRV core, it defrosts the core. Since the exhaust motor still
continues to operate, this method causes an unbalanced system,
causing a negative pressure in the space while the system is in the
defrost mode. Another damper defrost method includes opening a
damper within the HRV and re-directing the stale air to the outside
to the fresh air intake section. Although this system does not
cause the unwanted negative pressure problem, it will cause a
problem where the stale exhaust air will be sent to the living area
of the space along with all odors common in stale air.
[0006] Present day humidifiers use several methods of
humidification and controls. The most common type of humidifier
includes a return air duct mounted system complete with a
humidistat for control. For example, when the humidity level drops
to 45% in the winter, the humidistat sends power from an externally
mounted transformer to a small, slowly revolving 24V motor which is
attached to a wheel wrapped in a sponge-like material (sponge
wheel). The sponge wheel is slightly immersed in a water pan. The
water is normally taken from a saddle tee located on one of the
water lines close to the unit. The sponge wheel soaks up some of
the water from the pan as it is revolving. When the pan's water
level drops below a pre-set level, then a shut-off float mechanism,
mounted to the pan, opens to allow more water into the pan. As the
pan fills with water, the float closes and stops, allowing water to
flow into the pan. When the return air runs over the sponge wheel,
it pulls some of the water into the air stream, thus humidifying
the air stream and thereby increasing the humidity level within the
space. This system can cause moisture problems which generally
result from calcification of the float control and sponge wheel.
Control problems and water leakage into the furnace are common
within presently offered humidifiers.
[0007] It is presently well known that heating and cooling can be
accomplished with a geothermal or air-to-air compression-based
heating and cooling system, or a reversible, mechanical vapor
compression system, hereinafter referred to simply as "heat pumps".
These reversible, mechanical vapor compression systems or heat pump
systems have been utilized to accomplish the goal of efficiently
heating and cooling together within a unitary reversible system. An
air-to-air heat pump absorbs energy and rejects energy to the
outdoor air. The application for an air-to-air heat pump in
northern climates is limited because when the outdoor air
temperature drops below a prescribed level (usually 40 degrees F.),
the system cannot pump any further heat out of the air. The cooling
side of an air-to-air heat pump does not offer the highest
efficiency as achieved with a geothermal heat pump, but can be
effective in most temperature ranges. The capital cost of an
air-to-air heat pump is lower but again the operating efficiencies
suffer in comparison to a geothermal heat pump. Although the
capital cost is higher, the popularity of geothermal heat pumps has
grown dramatically over the years because of the constant
underground temperature and the much higher efficiency levels.
[0008] At present, a geothermal heat pump absorbs and rejects
energy from underground or fresh water source, in distinctly
different ways. It either uses a closed horizontal or vertical
ground or lake loop, or it can absorb or reject energy directly
from a domestic well or water source on the property. Together,
these are hereinafter referred to as "geothermal underground energy
sources".
[0009] If the geothermal underground energy source is based on a
horizontal closed loop method it includes the use of polyethylene
pipe, which is buried in trenches in a horizontal configuration in
rows or circuits approximately one foot below the frost level. A
closed lake or river loop uses the same polyethylene pipe, but
instead of burying the pipe underground as with a horizontal loop,
it is simply sunk to the bottom of the river or lake and adhered to
a pre-configured plastic fence matting material. A vertical closed
loop involves drilling bore holes down into the ground, all to the
same specific depths, inserting polyethylene pipe into the bore
holes and connecting them as circuits inside of a trench which
links each set of pipes. The circuits are designed to reduce
pressure drop to an acceptable level thereby causing the
appropriate flow rates. The loop is hooked to two three-way purging
valves at the unit. One or two low-voltage pumps are installed in
the loop to cause the flow of the liquid within the closed loop.
The fluid that is commonly used in a closed loop system includes a
mixture of an environment-friendly and government-approved
anti-freeze solution along with water. The water and anti-freeze
solution is pumped from and to a Freon-to-liquid
evaporator/condenser (hereinafter referred to as a "liquid heat
exchanger"), by the low voltage pumps at a specified flow rate,
causing specific energy absorption or rejection, depending on the
mode of operation. The liquid heat exchanger uses Freon within a
refrigeration system to pump the energy from the geothermal
underground energy source to the indoor Freon-to-air heat
exchanger.
[0010] If the geothermal energy source is based on an open-well
water source, or internal loop in a commercial building water
source, the common method of absorbing or rejecting energy is to
hook the liquid heat exchanger directly to the available water
source. The water is usually pumped in and out of the liquid heat
exchanger by the pre-existing water pressure system. In the case of
a commercial building which uses an internal closed loop system,
the water would be piped and pumped via the pre-existing system. In
the case of a residential application in a rural setting the
existing well pump would be used to pump water from the well into
and out of the Freon-to-liquid heat exchanger at a prescribed flow
rate. Then it is sent to a discharge point somewhere else on the
property but at the same aquifer level. When the discharge is
pumped out to the same aquifer level, it is generally believed that
the water will make its way underground back to the well after it
picks up energy from underground. In a situation where a geothermal
heat pump (sometimes called a water source heat pump) is used in a
high rise or a zoned commercial complex there are various methods
of taking advantage of the underground energy sources as well as
above-ground energy sources. In this case the geothermal or water
source heat pump is used as an energy transfer mechanism where a
unit is placed in each zone and tied to a common underground loop,
common internal loop, or open-well system. There are presently many
such applications in existence.
[0011] A geothermal heat pump is considered very reliable, given
that ground and underground water temperatures do not generally
fluctuate to the same extent as outdoor air temperatures. An
air-to-air heat pump offers a co-efficient of performance (COP)
compared to electric heating of approximately 1.8 to 1, depending
on outdoor temperature conditions. However, when the outdoor air
temperature drops below a specified level, then the heating side of
an air-to-air system switches over to straight electric, thereby
reducing the efficiency to a COP of 1 to 1. The same is true for an
air-to-air system in the cooling mode; when the air temperature
increases beyond 95 degrees F outdoors, the COP is lowered. A
geothermal heat pump offers a much higher COP, approximately 3.5 to
1, regardless of the outdoor temperatures.
[0012] Again, although the capital cost of a geothermal or water
source heat pump is higher than for an air-to-air heat pump, the
operating cost savings of geothermal make it a wise choice.
However, both systems make economic sense under the right
conditions. Both configurations are referred to herein as "heat
pump or reversible vapor compression systems, or reversible
compression based heating and cooling systems".
[0013] Regarding HRV systems, "sick building syndrome" has become a
common term within the building industry. It relates to the fact
that as the thermal envelopes of buildings are getting tighter
(higher R-values, better air barriers, therefore less air leakage),
the possibility of stale air causing health problems for the
occupants is much more prevalent and a major concern to designers.
A tight building will also cause a problem when humidity stays in
the building and is not properly ventilated. Humidity can cause
significant degradation to the building itself. Humidity problems
are well documented and generally accepted as a design issue in
most building codes (residential and commercial). Humidity will
come from several sources including the occupants. These problems
demand ventilation. As ventilation is incorporated into the
building designs, the recovery of energy becomes more and more
important, as a cost and efficiency issue and in most cases
necessary by the various municipal building codes. Although there
are many, many environmental benefits, the product must make
economic sense.
SUMMARY OF THE INVENTION
[0014] In view of the above, it is an object of the invention to
provide an integrated system for heating, cooling and heat recovery
ventilation, in which a heat pump or a reversible vapor compression
system or a compression based heating and cooling system is
integrated with a high efficiency heat recovery ventilation system,
and optionally with an on-board humidification system.
[0015] The heat recovery ventilation section of the equipment
offers either a base efficiency passive cross flow air-to-air heat
exchanger core (hereinafter referred to by the abbreviation
"PCMHEC") and if required, a secondary high-efficiency, active,
reversible refrigeration based evaporator/condenser heat exchanger.
The preferred compression based heating and cooling system portion
uses geothermal energy, but the invention is also applicable to the
use of an air-to-air heat pump. Both systems make economic sense
under the right conditions.
[0016] Since only one supply air ducting system is used, the
integrated system offers every room in the occupied space a
proportionate amount of pre-mixed fresh air without the need for
two sets of ducts.
[0017] Besides offering the standard primary cross flow heat
exchange core, the integrated system can incorporate an optional,
high efficiency secondary active refrigerant based energy recovery
coil within the ventilation function of the system. The secondary
active refrigerant based energy recovery core would only be used
when the compression based heating, cooling system is
operating.
[0018] The capital cost and operating efficiencies will increase in
the heat recovery, heating and cooling modes over that which is
presently available as separate components because of the
integration. The system will very efficiently heat, cool and
ventilate at a prescribed rate while simultaneously extracting
energy prior to the stale air removal. Variously configured defrost
methods can be employed without causing the negative pressure
and/or odor transferring problems, as described in the prior art
section above. When the integrated system goes into the defrost
mode it can use the aforementioned damper control system, but the
associated problems can be eliminated because the exhaust fan can
be electronically turned on or off independently, which is a
feature not available in presently offered equipment.
[0019] The integration in the present invention allows for a
standard primary crossflow core and an active secondary refrigerant
exchanger core.
[0020] Since an aluminum and copper coil is used complete with a
drain pan and drain pan sensor within the compression based heating
and cooling portion of the integrated system, the associated
leakage problems common in the prior art, can be avoided, and the
general cost is reduced. The vapor is atomized upstream of the
coil, and then as it hits the warmed coil it immediately evaporates
because the air coil runs at a temperature well above the
evaporation point. The humidification section of the system only
operates when the heating and cooling section is operating in the
heating mode.
[0021] Such an integrated system offers some or all of the
following advantages over the prior art:
[0022] general efficiency increase
[0023] a generally healthier indoor environment
[0024] one system to install as compared to three or four
[0025] less installed space needed
[0026] one extra fan for the HRV as compared to three or four
[0027] more control over the operating fans
[0028] better mixing and supply of fresh and heated or cooled air
to each room
[0029] one control system as compared to three or four
[0030] increased efficiency in the heating mode
[0031] increased efficiency in the cooling mode
[0032] increased efficiency in the HRV Mode
[0033] better defrost without causing negative pressure or
transferring odor to space
[0034] better humidity control
[0035] one main power connection complete with internal down
fusing
BRIEF DESCRIPTION OF THE DRAWINGS
[0036] The invention will now be explained in greater detail, with
reference to the accompanying drawings of the preferred embodiment
by way of example, in which:
[0037] FIG. 1 is a three-dimensional cut-open perspective schematic
view of a home fitted with the best mode of the invention;
[0038] FIG. 2 includes four two-dimensional drawings of the best
mode of the integrated system, complete with a push-through coil
and a closed loop geothermal heat pump,
[0039] FIG. 2-1 being a front view,
[0040] FIG. 2-2 being a side view,
[0041] FIG. 2-3 being a back view, and
[0042] FIG. 2-4 being a side view;
[0043] FIG. 3 shows the electronic boards that are used to control
the integrated system;
[0044] FIG. 4 is an exploded view of a primary passive cross flow
air-to-air heat exchanger core (PCAAHEC), showing the two heat
exchange channels;
[0045] FIG. 5 is a cut-open schematic perspective view of a home
fitted with a split configuration of the invention, with a complete
split compressor section in the lower portion of the space and a
remote air handler in the upper section of the space, with a
push-through coil and a closed-loop geothermal heat pump;
[0046] FIG. 6 is a three-dimensional schematic of the optional high
efficiency secondary active reversible evaporator/condenser heat
exchanger;
[0047] FIG. 7 is a piping schematic for a "compression based
heating cooling system", in this case referring specifically to a
geothermal closed loop system, refrigeration piping and including
the optional high efficiency reversible evaporator/condenser
primary heat exchanger, plus a sub-section of FIG. 6;
[0048] FIG. 8 is a piping schematic for the "compression based
heating cooling system", in this case referring specifically to a
geothermal open-well system, refrigeration piping and including the
optional high efficiency reversible evaporator/condenser primary
heat exchanger, plus a sub-section of FIG. 6;
[0049] FIG. 9 is a piping schematic for the "compression based
heating cooling system", in this case referring specifically to an
"air-to-air" refrigeration piping and including the optional high
efficiency reversible evaporator/condenser primary heat exchanger,
plus a sub-section of FIG. 6;
[0050] FIG. 10 is an exploded view of the heat exchange chamber,
including both primary and secondary heat exchangers, plus the 70
degrees F warm or 100 degrees F pre-heated air quick defrost
damper-best mode;
[0051] FIG. 11 is an exploded view of the heat exchange chamber,
including both primary and secondary heat exchangers, plus the 70
degree F space air defrost damper-special applications mode;
[0052] FIG. 12 is an exploded view of the heat exchange chamber,
including both primary and secondary heat exchangers, plus the
exhaust air quick defrost damper-special application mode;
[0053] FIG. 13 is an exploded view of the on-board optional
humidification system;
[0054] FIG. 14 is an exploded view of the heat recovery ventilation
condensate drain assembly;
[0055] FIG. 15 is an exploded view of a typical outdoor weather
hood for exhaust air; and
[0056] FIG. 16 is an exploded view of a typical kitchen exhaust
register complete with grease catching filter.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0057] The preferred embodiment of the invention is shown
schematically in FIG. 1, and an alternative embodiment is shown in
FIG. 5. There are three main configurations of the preferred
embodiment, as shown in FIGS. 7, 8, and 9.
[0058] The best mode example, as illustrated in FIG. 7, is a
geothermal heat pump complete with a closed underground energy
absorption loop in the heating mode. In the cooling mode the
direction of flow is reversed by the internal four-way valve 41, as
activated by the electronic control system (FIG. 3). The four-way
valve is in the normally closed position when the system is in the
heating mode. The electronic control system (FIG. 3) causes the
solenoid on the four-way valve 41 to shift, resulting in a reverse
flow of refrigerant.
[0059] The integration of all the on-board systems within the
integrated system offers higher efficiencies. However, the
geothermal portion of the total system offers a co-efficient of
performance (COP) of 3-3.5 to 1. One part of the energy is taken
from the electrical components within the system, compressor 44 and
blower fan motor 54, loop pumps 36, plus any other electrical
components. The other 2 to 2.5 parts of the total energy is
absorbed from the ground, using a water and/or anti-freeze solution
at a suitable volume and flow rate. It should be noted that heat
energy always travels to cold. In the case of an open-well
geothermal heat pump, as illustrated in FIG. 8, no anti-freeze
would be used. A geothermal open-well system will offer
approximately 10% higher efficiencies than a closed loop geothermal
heat pump, although water quality problems can create maintenance
issues. As the energy is absorbed from the ground, a Freon-to-water
based, reversible water coil 6 (evaporator in heating
mode--condenser in cooling mode) will transfer the energy as heat
to the reversible indoor air coil 5 (condenser in heating
mode--evaporator in cooling mode) within the occupied space. The
flow rate will cause a delta t or difference in temperature at the
water inlet pipes 38a and 38b. In the heating mode, the temperature
will drop from incoming 38a to outgoing 38b. This drop in
temperature is calculated as the rate of absorption and all
internal and external components are designed to match the
compressor 44 and other component sizing. The internally sealed
Freon system 22 transfers the energy from the outside water closed
loop or an open well to the inside air coil 5, to be used for
heating. The reverse is true in the cooling mode, meaning that the
closed water loop is used to reject heat, therefore transferring
the colder temperature to the indoor air coil 5. In the cooling
mode, the electronic controls will cause the four-way valve 41 to
reverse the Freon flow to the opposite direction by sending 24-volt
power to the 24-volt solenoid which is attached to the four-way
valve 41. The solenoid pulls in, causing the pilot port on the
valve to redirect the high pressure from the high pressure line to
the low pressure side of the valve, causing it to slide and change
the Freon flow to the opposite direction. The differential
pressures hold the valve in position during the cooling mode
operation. The on-board electronic package also controls
appropriate time delays and control sequences.
[0060] When the indoor centrally located or zoned thermostat 76
calls for heating, the indoor closed loop Freon (R22) refrigeration
system starts in the heating mode. The four-way valve 41 will be in
the off or normally closed position. In the heating mode the indoor
air coil 5 will act as a condenser and the water coil 6 will be in
the evaporative mode. If the optional high efficiency
evaporator/condenser heat exchanger, as shown in FIG. 6, is
installed, it will be in the same mode as the water coil. In the
heating mode the optional high efficiency evaporator/condenser heat
exchanger air coil 10 acts as an evaporator and it acts as a
condenser in the cooling mode, the same as the water coil 6.
[0061] The on-board electronics as shown in FIG. 3 will cause the
following sequence of events at heating mode start up. The HRV
section would already be running continuously, therefore the main
indoor blower 12 will already be running on low speed operation.
The thermostat 76 will call for heat, sending a 24-volt supply to
the system. Since the system is completely integrated, the
electronics will immediately set up for operational sequencing. As
the thermostat 76 calls, the system will immediately turn on the
loop pumps 36 on a closed loop system (FIG. 7), or open the 24-volt
motorized zone valve 80 (FIG. 8) for a well system or start the
outdoor blower fan 85, on an air-to-air system (FIG. 9). The
on-board electronics control all functions within the integrated
system and include a series of LEDs for on-board diagnostics. All
inputs and all outputs are monitored.
[0062] The system differs from prior art systems in that the loop
pumps are installed internally and are electronically controlled
and pre-fused within the integrated system.
[0063] If the optional desuperheater 61 is installed, the
desuperheater pump 71 will also turn on immediately upon the
heating call from the thermostat 76 and pull a quantity of water
directly from the brass cross 34 attached to the domestic hot water
tank 32. As the water flows into the hot water connection 61-1, it
flows past the desuperheater high limit sensor 77, which is
attached to the incoming desuperheater water line 78. The sensor 77
measures the temperature and if the temperature is below 130
degrees F the desuperheater pump 71 will continue to operate.
However, if the temperature is above 130 degrees F, the
desuperheater pump 71 will shut off.
[0064] Then there will be a 16- to 24-second time delay and the
compressor 44 will start. The indoor blower 12 will already be on
at low speed because the HRV section will be on continuous
operation. The indoor blower fan 12 will jump to high speed
operation after the compressor 44 has been on for 8 seconds. This
quick response system is built into the on-board electronics, FIG.
3. It allows the compressor to warm up before the blower 12 starts
to transfer energy to the indoor space, reducing the opportunity
for cool air to be transferred to the indoor space. This feature
helps to encourage creature comfort.
[0065] In the cooling mode the blower 12 will jump to high speed
immediately. When the indoor blower 12 jumps to high speed it will
draw more air through the weighted modulating air damper device 27.
The device 27 will allow the air flow through the PCAAHEC 13 to
increase by approximately 10%, increasing the positive pressure
within the space by approximately 10%. As well as modulating air
flow through the PCAAHEC 13, one of the functions of the modulating
device 27 is to adjust this amount.
[0066] The compressor 44 will start, causing the Freon to be
compressed and flow throughout the refrigeration closed loop
system. As the Freon is compressed it will heat up.
[0067] As soon as the compressor 44 starts, the Freon will flow
from the compressor 44 to the 44-1 as a hot high pressure gas. It
will then travel to the desuperheater 61 at the entry point 61-4.
If the desuperheater 61 is calling to offer heat to the domestic
hot water tank 32, cool water will run through the desuperheater 61
from the water entry point 61-1, taking approximately 6,000 and
10,000 BTU's (depending on the system size) from the condensing hot
gas by way of heat exchange and then send the heated water back to
the domestic hot water tank 32 through the exiting point 61-2 on
the water side of the desuperheater 61. After the Freon has been
slightly cooled by desuperheater 61, it then travels to the Freon
exiting point 61-3 and flows towards and then enters the four-way
valve 41 at the entry point 41-4 as a hot gas.
[0068] Although the desuperheater 61 will take some of the energy
off in the heating mode, it actually increases the efficiency of
the system 22 by increasing the sub cooling. In the cooling mode
the desuperheater 61 will offer free hot water to the occupants
because it will simply reduce the need to reject the heat energy
out to the ground, taking advantage of the process.
[0069] The hot gas then travels through the four-way valve 41 and
exits at the exiting point 41-1 and travels towards the indoor air
coil 5. It enters the indoor air coil at the entry point 5-1. As
the hot gas enters the indoor air coil 5, a heat exchange occurs
because the indoor distribution blower 12 will have been turned on.
The air that is traveling across the indoor coil will be
approximately 70 to 73 degrees F, depending on the fresh air coming
into the mixing chamber 14 for the PCAAHEC 13. The temperature of
the Freon traveling through the Freon side of the indoor air coil 5
will be approximately 150 degrees F., so a heat exchange will
occur. The heat from the Freon will transfer to the air, to supply
the space with heated air, and the Freon temperature will drop. As
the Freon temperature drops it will condense and change the state
of the Freon from a hot high pressure gas to a warm saturated high
pressure liquid. It will exit the indoor air coil 5 at the exiting
point 5-2.
[0070] The Freon will then travel to the air coil side T 75 and run
in two directions, if the secondary high efficiency active
reversible evaporator/condenser heat exchanger 10 is installed, as
illustrated in FIG. 6. For this section of the description, it is
assumed that the secondary active reversible evaporator/condenser
heat exchanger 10 is not installed. The secondary refrigerant flow
will be covered at the end of this section.
[0071] In this case, the warm saturated high pressure Freon will
travel to the sight glass and moisture indicator 43, then through
the reversible filter/drier 42 where any contaminants or moisture
will be removed. The Freon will then travel to the bi-flow TX valve
40a entry point 40a-1. As the warm saturated high pressure liquid
enters the bi-flow TX valve 40a, it will be atomized, essentially
releasing the saturated energy, causing the Freon to drop down to
an extremely cold temperature. As the Freon travels through the
bi-flow TX valve 40a and is atomized based on a reduction in
orifice size as dictated by the bi-flow TX valve 40a temperature
sensing bulb 40b that is attached to the suction gas line, it will
change state from a warm saturated high pressure liquid to an
un-stable super cooled vapor, hereinafter referred to as flash gas.
The flash gas will exit the bi-flow TX valve 40a the exiting point
40a-2 and the pipe will double or triple volumetrically. Then it
will travel to and enter the entry point 6-1 at the water coil 6.
As the flash gas enters the water coil 6, it will be super-cooled
and will look for heat to be transferred. The water or anti-freeze
solution will be traveling counter flow through the heat exchanger
simultaneously at a higher temperature. The Freon will absorb heat
from the water or anti-freeze solution, thereby cooling the water
and increasing the temperature of the Freon.
[0072] In an air-to-air system as illustrated in FIG. 7 the outdoor
air coil 7 absorbs the energy from the outside air and transfers it
to the Freon. As suggested herein, an air-to-air configuration
would not be the most efficient manner of absorption or rejection.
However there are applications where an air-to-air system is
appropriate.
[0073] As the temperature of the Freon increases, it will once
again change state from a flash gas to a vapor, hereinafter
referred to as suction gas. The suction gas will exit the water
coil at exit point 6-2 then travel toward the four-way valve 41.
The suction gas will return to the entry point 41-3 and then come
out of the four-way valve 41 exiting point 41-2 and then travel
towards the accumulator 66 which is an optional piece of equipment,
depending on the compressor 44 specifications. (Not all compressors
require accumulators.) If an accumulator is installed, the suction
gas will enter the accumulator 66 at entry point 66-2. Since liquid
cannot be compressed and will damage a compressor 44, any liquid
that may still be in the suction gas will drop out at the
accumulator 66, allowing only suction gas to return to the
compressor 44. The suction gas will then travel out of the
accumulator 66 exiting point 66-1 and travel back to the suction
entry point 44-2 at the compressor 44 where the suction gas is then
re-compressed by the compressor 44 for another run through the
system. This is the complete refrigeration process, which is a
constant flow type system.
[0074] In the air conditioning mode all refrigeration flows are
reversed. When the thermostat 76 calls for air conditioning, the
four-way valve 41 is activated by on-board electronic control
system (FIG. 3), and it shifts from a normally closed position to
the opposite position. The indoor air coil 5 will then be acting as
an evaporator and the water coil 6 will be acting as a condenser.
The indoor mixed return and fresh air will push through the indoor
air coil 5 and since it is a condenser, it will absorb the heat
from the indoor air. Simultaneously, the geothermal fluid will
absorb heat from the water coil 6 because it will be acting as a
condenser. In the case of an air-to-air system, the outdoor coil
will be acting as a condenser. When the outdoor air temperature
flows across the outdoor coil 86, as best shown in FIG. 9, at a
cooler temperature, it will absorb the heat from the outdoor coil,
for rejection to the outdoor air. When the optional secondary, high
efficiency, active reversible evaporator/condenser heat exchanger,
as shown in FIG. 6, the secondary heat recovery air coil would act
as a condenser when the compression based heating and cooling
system 22 is on in the cooling mode. The exhaust air travels
through the secondary coil 10 at a lower temperature and absorbs
heat from the Freon that is flowing through the secondary coil 10
and helps to increase the efficiency by offering extra heat
rejection.
[0075] If the optional secondary coil 10 is installed, it would
work within the active refrigeration system in the heating mode, in
the following manner.
[0076] In the case where, compression based 22 system is on in the
heating mode and the active 10 is installed, the second direction
that the high pressure liquid Freon would flow from the piping T 75
to the sight glass 43 as described earlier in this section and the
second direction would be to the TX valve 67a, entry point 67a-2,
as shown in FIG. 6. As the warm saturated high pressure liquid
enters the bi-flow TX valve 67a, it will be atomized, essentially
releasing the saturated energy causing the Freon to drop down to an
extremely cold temperature. As the Freon travels through the
bi-flow TX valve 67a and is atomized based on a reduction in
orifice size as dictated by the bi-flow TX valve 67a temperature
sensing bulb 67b that is attached to the suction gas line, it will
change state from a warm saturated high pressure liquid to an
un-stable super cooled vapor, hereinafter referred to as flash gas.
The flash gas will exit the bi-flow TX valve 67a the exiting point
67a-1 and the pipe will double or triple volumetrically, then it
will travel to and enter the entry point 10-1 at the secondary air
coil 10. As the flash gas enters the secondary air coil 10, it will
be super cooled and will look for heat to be transferred into it.
After transfer has occurred in the PCAAHEC 13 core the exhaust air
is simultaneously traveling out of the PCAAHEC 13 simultaneously
and through the secondary air coil 10, typically at a higher
temperature. The Freon will absorb extra heat from exhaust air,
thereby further cooling the exhaust air at the outgoing exhaust air
channel 90 and increasing the Freon temperature.
[0077] As the temperature of the Freon increases it will once again
change state from a flash gas to a vapor, hereinafter referred to
as suction gas. The suction gas will exit the secondary air coil 10
at exit point 10-2, then travel toward into the bi-flow accumulator
65 at entry point 65-1. The Freon will drop any liquid in the
accumulator allowing only suction gas to exit at the exiting point
65-2. The suction gas will travel to the water coil side T 74 and
flow into the suction gas that will be flowing simultaneously from
exit point 60-2 from the water 6. The suction gas will exit the
water side coil T 74 and travel toward the four-way valve 41 along
with the suction gas that exits the compression based 22, water
coil 6. The suction gas will flow to the four-way valve 41, entry
point 41-3 and then come out of the four-way valve 41 exiting point
41-2 and then travel towards the accumulator 66 which is an
optional piece of equipment, depending on the compressor 44
specifications, if installed at the accumulator 66 entry point
66-2. Since liquid cannot be compressed and will damage a
compressor 44, any liquid that may still be in the suction gas will
drop out at the accumulator 66, allowing only suction gas to return
to the compressor 44. The suction gas will then travel out of the
accumulator 66 exiting point 66-1 and travel back to the suction
entry point 44-2 at the compressor 44 where the suction gas is then
re-compressed by the compressor 44 for another run through the
system. This is the complete refrigeration process which, is a
constant flow type system.
[0078] The Geothermal Section:
[0079] A geothermal heat pump is known to be the most efficient
method of heating and cooling today. Since there are no fossil
fuels being burned to generate space heat, there is no flame or
chimney in the living space. The environmental benefits are
obvious. The geothermal heat pump uses renewable energy in that the
system uses energy, which is constantly available under ground.
Electricity has a 1 to 1 co-efficient of performance (COP). When
you turn on an electric resistance heater you will get heat out, in
exactly the same rate as you put energy in 1 to 1. However, a
geothermal heat pump offers between 3 and 4 to 1 COP. If it costs
one dollar to turn on the compressor you will get that one dollar
worth of energy plus, you will get another 2 to 3 dollars worth of
energy from the ground. Therefore you will end up with a COP of 3
or 4 to 1. In other words you will have received three or four
units of usable energy for the cost of one unit of energy. The
incorporation of an optional desuperheater to heat domestic hot
water will also help to increase the efficiency. The common savings
with a desuperheater will be approximately 60 to 70% over that of a
standard electric hot water heater. It would be coupled directly
with a standard hot water tank. The technology has proven itself
over and over again with thousands of installations as proof.
Geothermal is a "compression based technology", so the integration
of a humidifier and a heat recovery ventilation system further
helps to decrease the capital cost and increase the operating
efficiency of the heating and cooling system. The integrated system
offers unparalleled efficiency and efficacy.
[0080] The HRV Section:
[0081] An HRV is very common in extreme temperature and humid
climates. HRV's are used to ventilate at a specific rate with very
low energy loses. As, energy costs are rising, building
technologies have followed pace and become tighter and tighter. The
tighter the building the more the need to ventilate for the benefit
of the building structure and the health of the occupants. The HRV
section would normally be running on a continuous basis. However,
the HRV can be turned on and off if required, based on a
unit-mounted humidistat 45 that is located within the indoor return
and fresh air mixing chamber 14. In most cases the humidistat 45
would not be used and the HRV will operate on a continuous basis.
For this example, it is assumed that the HRV is on continuous
operation.
[0082] Regarding the HRV defrost methods, although there are many
methods (configurations) of PCAAHEC 13 defrost that are available,
the three most common will be described herein. Since the
integrated system offers independent control of the dedicated stale
air exhaust fan 17, all three defrost methods, as described herein,
eliminate the opportunity for the defrost mode to cause a negative
pressure within the building as described in the prior art section
above. The preferred, best mode, 70 degrees F warm or 100 degrees F
pre-heated air defrost method, as shown in FIG. 10 and the 70
degrees F space air defrost method, as shown in FIG. 11, also
eliminate the opportunity for odor transfers from the stale air
areas to the fresh supply air, also as described in the prior art
section above. The first 70 degrees F warm or 100 degrees F
pre-heated air defrost method would also offer a fast acting
defrost capability which is not available in prior art. All defrost
methods will only be used when the compression based heating and
cooling system 22 is in the heating mode. Frosting/icing of the
PCAAHEC 13 would only be possible in the winter operation in cold
that have an average winter temperatures below 23 degrees F.
Frosting/icing would only occur on the fresh air side of the
PCAAHEC 13, as cold, humid fresh incoming air crosses the warmer
exhaust. At approximately 23 degrees F, and when the humidity level
is above 60% relative humidity (RH), the difference in temperature
and humidity between the incoming fresh air and the 70, 50% RH
indoor stale air, being exhausted. The humidity from the incoming
fresh air, will condense on the surface at the entrance of the
fresh side of the PCAAHEC 13, causing first frosting then after a
period of time icing. Excessive frosting/icing will block the
PCAAHEC 13, reducing and eventually blocking airflow from the 87,
89 and 68, thereby reducing or eliminating heat recovery
ventilation.
[0083] The first defrost method that is available within the
integrated system is the 70 degrees F warm or 100 degrees F
pre-heated air defrost method (configuration), as shown in FIG. 10
which would include the use of a defrost damper 56a, as shown in
FIG. 10. With this method, the defrost damper 56a, normally closed
vertical position would be blocking the optional positive pressure
defrost port 94 which is located directly behind the defrost damper
56a. The positive pressure defrost port 94, between the back
vertical wall in the HRV exchange chamber 16 and it is directly
lined up with a port located in the indoor air coil positive
pressure chamber 70, as shown in FIG. 10, offering warm 70 degree F
or 100 degree F air flow from indoor positive pressure chamber 70,
to the fresh air incoming channel 87, when the system is in the
defrost mode. When the outdoor temperature drops to 23 degrees F as
sensed by the defrost sensor 19 which is located in the incoming
fresh air channel 87, the sensor 19 will activate a 15-minute
defrost time out period, as dictated by the on-board electronic
system, as shown in FIG. 3. During the defrost time out period, the
HRV will operate as usual. During the defrost time out period, the
PCAAHEC 13 can experience some slight surface ice lensing (light
surface coating). After the time out period, the dedicated stale
air exhaust fan 17 will shut off and the defrost damper 56a will
shift from the normally vertical position to the horizontal
position shutting off the incoming fresh air from entering the
incoming fresh air channel 87. If the compression based system 22
is not operating in the heating mode, the shift in the damper 56a
will cause the indoor 70 degree F space air, from the indoor air
coil positive pressure chamber 70 to be drawn through the defrost
bypass port 94 to the incoming fresh air channel 87. If the
compression based system 22 is operating in the heating mode the
shift in the damper 56a will cause the pre-heated 100 degree F,
from the indoor air coil positive pressure chamber 70 to be drawn
through the defrost bypass port 94 to the incoming fresh air
channel 87. The 70 or 100 degree F warm space air will then enter
the fresh air heat recovery core particulate filter 21 and then
travel through the fresh air side of the PCAAHEC 13 and will
defrost the PCAAHEC 13. The air will then travel through the
PCAAHEC 13 and then into the incoming fresh air channel 89, after
which, it will then travel past the adjustable, weighted,
modulating pressure differential air balancing device 27 and into
the fresh air induction port 68 and into the indoor return and
fresh air mixing chamber 14 and past all the components therein to
be sent back to the indoor coil positive pressure chamber 70. The
air will then re-circuit back through the same process for the
prescribed time period. Since the 70 or 100 degree F warm air will
hit the surface of the PCAAHEC 13 it turn to liquid and drain off
the PCAAHEC 13 and run into the HRV drain pan 51 and then drain to
the condensate tubing 53 for discharge to the condensate discharge
point 58 and sent to the drain. If the compression based system 22
is not operating, then the defrost mode will operate for
approximately 3 minutes. If the compression based heating cooling
system 22 is operating the defrost mode will operate for 1 to 1.5
minutes, as dictated by the on-board electronic system, as shown in
FIG. 3. After the appropriate defrost operation period is completed
(1.5 or 3 minutes) the PCAAHEC 13 should be completely ice free and
the defrost damper 56a will shift from the horizontal position back
to its normal vertical position and the dedicated stale air fan 17
will turn back on, thereby allowing fresh outdoor air to travel
into the incoming fresh air channel 87 and back through the fresh
air core filter 19, through the PCAAHEC 13 and into the air while
the dedicated air fan 17 will cause the stale air to travel through
the HRV system as normal operating condition dictates. If the
temperature stays below 23 degrees F then the defrost process will
continue to cycle on after a 15-minute period. The defrost mode
will continue to cycle off and on until the temperatures rises
above the prescribed 23 degrees F. With this method there is no
possibility of transferring odors or causing a negative pressure in
the space, therefore this method would be considered as the
standard configuration this method is preferred.
[0084] The second 70 degrees F space air method of defrost
(configuration) that is available within the integrated system is
the, 70 degrees F space return indoor air import defrost method
which would include the use of a defrost damper 56b, as shown in
FIG. 11. With this method, the defrost damper 56b, normally closed
vertical position would be blocking the optional 70 degrees F space
indoor air import defrost port 93, as located on the HRV exchange
chamber door 16-1, covering the HRV chamber 16. The defrost damper
56b would be in a position to allow the air to flow from the 70
degrees F inside space air to flow into the fresh air channel while
the dedicated stale air fan is off.
[0085] When the outdoor temperature drops to 23 degrees F as sensed
by the defrost sensor 19 which is located in the incoming fresh air
channel 87. The sensor 19 will activate a 15-minute defrost time
out period, as dictated by the on-board electronic system, as shown
in FIG. 3. During the defrost time out period, the HRV will operate
as usual. During the defrost time out period, the PCAAHEC 13 can
experience some slight surface ice lensing (light surface coating).
After the time out period, the dedicated stale air exhaust fan 17
will shut off and the defrost damper 56b will shift from the
normally vertical position to the horizontal position shutting off
the incoming fresh air from entering the incoming fresh air channel
87 and causing the indoor 70 degree F space air, surrounding the
system to be to be drawn through the optional 70 degree F space air
import defrost bypass port 93 to the incoming fresh air channel 87.
The warm space air will then enter the fresh air heat recovery core
particulate filter 21 and then travel through the fresh air side of
the PCAAHEC 13 and will defrost the PCAAHEC 13. The air will then
travel through the PCAAHEC 13 and then into the incoming fresh air
channel after the incoming fresh air channel after the PCAAHEC 89,
after which it will then it will travel past the adjustable,
weighted modulating pressure differential air balancing device 27
and into the fresh air induction port 68 and into the indoor return
and fresh air mixing chamber 14 and past all the components therein
to be sent to the indoor coil positive pressure chamber 70. The air
will then re-circuit back through the same process for the
prescribed time period. Since the warm air will hit the surface of
the PCAAHEC 13 it will turn to liquid and drain off the PCAAHEC 13
and run into the HRV drain pan 51 and then drain to the condensate
tubing 53 for discharge to the condensate discharge point 58 and
sent to the drain. The defrost mode will operate for approximately
3 minutes, no matter whether the compression based heating cooling
system 22 is operating or not. After the 3 minutes defrost
operation period is completed the PCAAHEC 13 should be completely
ice free and the defrost damper 56 a will shift from the horizontal
position back to its normal vertical position and the dedicated
stale air fan 17 will turn back on, thereby allowing fresh outdoor
air to travel into the incoming fresh air channel 87 and back
through the fresh air core filter 19, through the PCAAHEC 13 and
into the air while the dedicated air fan 17 will cause the stale
air to travel through the HRV system as normal operating condition
dictates. If the temperature stays below 23 degrees F then the
defrost process will continue to cycle on after a 15-minute period.
The defrost mode will continue to cycle off and on until the
temperatures rises above the prescribed 23 degrees F. With this
method there is the possibility of transferring odors, therefore in
a standard configuration this method is not preferred, however, in
certain applications, this method would prove useful.
[0086] The third special application method of defrost that is
available within the integrated system is the exhaust air bypass
defrost method which would include the use of the defrost damper
56c configuration, as shown in FIG. 12. With this defrost
configuration, when the HRV system is operating normally, the
defrost damper 56c would be blocking the defrost bypass port 92.
When the outdoor temperature drops to 23 degrees F as sensed by the
defrost sensor 19 which is located in the incoming fresh air
channel 87. The sensor 19 will activate a 15-minute defrost time
out period, as dictated by the on-board electronic system, as shown
in FIG. 3. During the defrost time out period, the HRV will operate
as usual. During the defrost time out period, the PCAAHEC 13 can
experience some slight surface ice lensing (light surface coating).
After the time out period has finished, the dedicated stale air
exhaust fan 17 will shut off and the defrost damper 56c will shift
from the normally vertical position to the horizontal position
shutting off the incoming fresh air from entering the incoming
fresh air channel 87 and causing the normally exhausted air at 70
degrees F to be drawn through the optional defrost bypass port 92
to the incoming fresh air channel 87. The warm air will then enter
the fresh air heat recovery core particulate filter 21 and then
travel through the fresh air side of the 13 and will defrost the
PCAAHEC 13. The air will then travel through the core 13 and then
into the incoming fresh air channel after the core 89, then it will
travel past the adjustable, weighted modulating pressure
differential air balancing device 27 and into the fresh air
induction port 68 and into the indoor return and fresh air mixing
chamber 14 and past all the components therein to be sent to the
indoor coil positive pressure chamber 70. The air will then
re-circuit back through the same process for the prescribed time
period. Since the warm air will hit the surface of the PCAAHEC 13
it will turn to liquid and drain off the PCAAHEC 13 and run into
the HRV drain pan 51 and then drain to the condensate tubing 53 for
discharge to the condensate discharge point 58 and sent to the
drain. The defrost mode will operate for approximately 3 minutes,
no matter whether the compression based heating cooling system 22
is operating or not. After the 3 minutes defrost operation period
is completed the PCAAHEC 13 should be completely ice free and the
defrost damper 56 a will shift from the horizontal position back to
its normal vertical position and the dedicated stale air fan 17
will turn back on, thereby allowing fresh outdoor air to travel
into the incoming fresh air channel 87 and back through the fresh
air core filter 19, through the PCAAHEC 13 and into the air while
the dedicated air fan 17 will cause the stale air to travel through
the HRV system as normal operating condition dictates. If the
temperature stays below 23 degrees F then the defrost process will
continue to cycle on after a 15 minute period. The defrost mode
will continue to cycle off and on until the temperatures rises
above the prescribed 23 degrees F. With this method there is the
possibility of transferring odors, therefore in a standard
configuration this method is not preferred, however, in certain
applications, this method would prove useful.
[0087] Issues Related the HRV and Humidification Sections:
[0088] Stale air is drawn from strategically located vents 28 and
62 within the living area and is sent outside while fresh air is
simultaneously being pulled into the building at the same rate. The
heat in the stale air is transferred to the fresh incoming air.
Differing rates of ventilation can cause problems with negative or
positive pressure in the living space. The rates of ventilation or
air changes are initially balanced. The specific rates of
ventilation are listed in the local building codes. At start-up the
balancing is done by using the manual balancing dampers 52, located
in the indoor stale air duct 1 and the other 33, located in the
fresh air intake duct 23. For example a restaurant, pub or tavern
will have a very different rate than a residence. We use a
dedicated stale air exhaust fan 17 because the mixing of the fresh
and stale air can cause a problem with odors being transferred from
the moist air areas to the rest of the living space, which is
obviously undesirable. Although some cross leakage will occur the
amount as a percentage of the total is quite low. The two air
streams do not cross paths in the same air passage. The two air
streams are separated by a passive cross flow heat exchange core
(PCAAHEC) 13. The stale air is drawn from stale air registers 35
and 62 which are commonly located in the kitchen 62, bathrooms 35,
laundry rooms 35 and other moist air areas within the residence.
This will cause a slight negative pressure in those areas within
the living space thereby causing odors to stay in those areas for
exhaust, as compared to wafting throughout the other living spaces.
In certain climates where the temperature is low and cool,
re-humidification will be desirable because the HRV's constant
operation can dry the air in the winter. The geothermal or
compression based heating, cooling system 22 will have little
affect on a relative humidity increase or decrease because it is
already designed with longer run periods with low differential
temperatures at the coil. This will be accomplished by installing
an atomizing humidification system, as shown in FIG. 13 within the
integrated package. The humidification system would include an
atomizing tube 49 connected to a solenoid valve 50 which opens and
closes based on a low humidity level, as sensing by the unit
mounted humidistat 45 in the winter. Re-humidification would only
be used in the heating season where dehumidification would be
accomplished in the summer months by the evaporator air coil 5 and
the HRV system. However, since a refrigeration based condensing air
coil 5 is used in the heating mode within the compression based
heating, cooling system 22, re-humidification can be accomplished
by simply atomizing a small quantity of water on the down stream
side of the coil, but again only when the heating system 22 is
operating. The atomized water will flow to the coil and evaporate
because the air coil will be warmed at least 25 degrees F above the
incoming air temperature. A difference of 25 degrees F in air
temperature will cause immediate vaporization or evaporation when
the cool water heats the warm coil. In the summer the
humidification system would not be required because a continuous
running HRV will actually help to reduce air conditioning run times
by dehumidifying the air.
[0089] Every living space environment has odors, fumes and
humidity. In addition to recovering heat, the integrated system can
add or expel excess moisture as needed. This will help to maintain
a comfortable humidity level inside the house during the colder
winter months, while preventing excess humidity from entering in
the summer months. The heat exchange process recovers heat in the
winter months while rejecting heat in the summer months. It also
will cause humidity to drop out and be sent to the condensate drain
for removal from the indoor environment.
[0090] As best illustrated in FIGS. 1 and 2, stale air is drawn
into the indoor stale air registers 35 located in the bathrooms,
and other moist air areas by a dedicated stale air exhaust fan 17.
The kitchen stale air register 62 would include a grease catcher
filter 51 right at the register 28. The stale air is drawn through
the flexible non-insulated indoor stale air ducting 1, then travels
over the dedicated stale air fan 17, pulling any energy that is
available by the nature of the dedicated stale air fan 17
operation. The stale air then travels through a basic particulate,
stale air heat recovery core filter 20 continuing through the
primary passive cross flow air-to-air heat exchanger core (PCAAHE)
13. As the stale air flows through the PCAAHE 13, its heat energy
is transferred to the cooler fresh air, which is passing
simultaneously on the opposite side of the PCAAHE 13. The stale air
transfers a majority (approximately 70%, depending on outdoor air
temperatures) of its pre-heated or pre-cooled energy to the fresh
incoming air.
[0091] The stale air would then travel through the secondary active
reversible evaporator/condenser coil 10, if it is installed for
high efficiency operation. The stale air would transfer energy to
the cooler evaporator coil 10, offering higher efficiencies to the
22 (see "High Efficiency Secondary Active Evaporator/Condenser Heat
Exchanger Coil" below).
[0092] It is then transferred through the insulated stale air
exhaust ducting 24. Then through the bird screen 4-1 within the
outdoor stale air exhaust weather hood 4 to the outdoors.
[0093] As the stale air is flowing through the system, the fresh
outdoor air is simultaneously being drawn in through a bird screen
7-1, located in the outdoor fresh air intake vent hood 7. The fresh
air then flows into the insulated fresh air intake duct 23 from
outside by the negative pressure created by the indoor air
distribution blower 12. The fresh air is drawn at the same rate as
the stale air, modulated by a weight adjustable modulating pressure
differential air balancing device 27, located at the entrance to
the indoor return and fresh air mixing chamber (mixing chamber) 14.
The fresh air travels in from outside and into the insulated fresh
air intake duct 24, then travels into the heat recovery ventilation
(exchange) chamber 16, then travels through the basic particulate
fresh air heat recovery core filter 21, then into the fresh air
side of PCAAHE 13. The fresh air picks up heat (energy) from the
stale air as it crosses through the PCAAHE 13. The fresh air
travels to the indoor return and fresh air mixing chamber 14 and
picks up any available energy as it travels over the compressor and
other electrical components. It is mixed with air that is drawn in
from the main indoor return air duct 3 from the living space. After
the fresh and return air has been thoroughly mixed, it then travels
through the air coil 5. If the living space thermostat is calling
for heating or cooling. The air is then heated or cooled at the
indoor reversible evaporator/condenser, Freon to air, direct
exchange, air coil 5 and then transferred to the supply air duct 2
and sent to each room via the indoor supply air registers 28. The
pre-mixed fresh and heated or cooled air is then sent evenly to
each room in the residence through the supply air registers 28
located in each room of the living space.
[0094] High Efficiency Secondary Active Evaporator/Condenser Heat
Exchanger Coil
[0095] If the optional, high efficiency secondary active
evaporator/condenser heat exchanger coil 10 is installed, and the
compression based heating cooling system 22 is in the heating mode.
The sensible temperature of 10 would be at approximately 30 degrees
F, while the stale air would be at a higher temperature. Therefore
any available heat that is left in the stale air would transfer via
the Freon within the compression-based heating and cooling system
22 for further recovery and would be sent directly to the
compressor 44 within the compression based heating and cooling
system 22, and ultimately transferred to the space. If the outdoor
temperature drops below a preset limit as measured by the
temperature sensor 19 located in the fresh air supply area of the
HRV chamber 16, a bypass valve will switch 10 off while 22 is
operating. The common outdoor temperatures in the various
geographical locations would dictate the positioning of 10. If the
optional high efficiency secondary active evaporator/condenser heat
exchanger coil 10 is installed. And the compression based heating
cooling system 22 is off, then 10 will have no effect as it is
designed for active operation only.
[0096] The Heating Mode:
[0097] As best illustrated in FIG. 1, when the central wall mounted
thermostat 76 calls for heating the compression based
heating/cooling system 22 will start in the heating mode. The
heating mode will start all necessary components to cause heating
and air flow. The HRV will already be on in continuous operating
mode. The occupied space air at approximately 70 degrees F, is
drawn to the compression based heating, cooling or geothermal heat
pump 22 by a negative pressure that is caused by the indoor air
distribution blower 22 and the main blower motor 54 within the
refrigeration chamber 63. The air is drawn from high or low mounted
return air registers 29, then follows inside the return air duct 3,
leading to the return air filter 30. The room air then enters the
indoor return and fresh air mixing chamber 14. The air will then
flow across the refrigeration components within the refrigeration
chamber 63. The air will then mix within the mixing chamber 14, it
will turbulate and mix with the fresh air that is flowing in from
the fresh air induction port 68. As best illustrated in FIGS. 2, 7,
8 and 9, as the air is mixing it will flow across and around the,
compressor 44, the four-way valve, filter/drier 42 and sight glass
moisture indicator 43, taking any heat or energy that is available
to the air stream prior to being heated or cooled. Flowing across
the aforementioned components will heat the air up by approximately
3 degrees F. The air will also flow past the unit mounted
humidistat 45, as shown in FIG. 2. The air will also flow across
the fan blower motor 54 as it enters the main fan blower 12. The
air will then be then sent to the indoor positive pressure chamber
70 to be heated by the compression based heating and cooling system
as shown in FIGS. 7, 8 and 9.
[0098] If the sensor on the unit mounted humidistat 45 senses the
humidity level below 45%, it will send a signal to the humidifier
solenoid 50, and the solenoid will open. This will cause water to
flow in from the external connection for humidifier 57, through the
humidifier solenoid 50, and will fill the humidifier atomizing
tube(s) 49. Thereby adding humidity to the air stream prior to
flowing through the indoor air coil. Since the system is in the
heating mode, the indoor air coil 5 will be in the condensing mode
and will be warmed to approximately 100 degrees F causing the
atomized water to immediately evaporate and transfer to the heated
air.
[0099] The 70 to 73 degree F air, with or without added humidity,
will then be forced through the indoor air coil 5. The air will be
heated to approximately 100 degrees F. Then if necessary, the
heated and/or pre-humidified air will travel through the hydronic
or electric backup/emergency heat cavity 48, for second stage
heating. The air will then travel through the main indoor supply
duct 2 and will travel inside the ducting to the supply air
registers 28 located in each room or zone of the space.
[0100] Exhaust and Energy Recovery:
[0101] A dedicated stale air exhaust fan 17, draws indoor stale air
into the stale air indoor duct 1. Via strategically located indoor
supply air registers 28, located in the bathroom, laundry room,
(moist/stale air areas), and also located in the kitchen 62
complete with a grease catching filter 18 and any other ducted
sources of pollutants. Then the stale air flows into the indoor
stale air duct 1 through the indoor stale air filter 18, then
travels into the heat (energy) exchange chamber 16. Then when the
compression based liquid-to-liquid or air-to-air heating/cooling
chamber (heating cooling system) 22 is on in the heating mode the
air enters the heat (energy) exchange chamber 16. The stale air
will travel through the liquid to air evaporator/condenser primary
heat exchanger 10 which will be in the evaporative mode. The liquid
to air evaporator/condenser primary heat exchanger 10 (evaporator)
will be much cooler then the stale air therefore the heat will
travel from the stale air to the cold Freon within the evaporator
and will carry the heat to the indoor evaporator/condenser (liquid
to air--heating/cooling) 5, which will be in the condenser mode and
send it into the occupied space air thereby increasing the
efficiency of the heating/cooling system 22. After the stale air
has traveled through the liquid to air evaporator/condenser primary
heat exchanger 10 it will then travel through the energy exchange
stale air channel 26 (see FIG. 3), and then any remaining heat will
be transferred to the fresh air via the energy exchange fresh air
channel 25 (see FIG. 3) within the passive, cross flow air-to-air
heat exchanger 13. After the heat has been removed the stale air,
it will then travel through the stale air exhaust duct 24 to be
exhausted outside of the space. If the outside air temperature is
at or below -5 C or 23 F, the defrost mode will come into affect
and one of two things will happen or a combination of both
depending on the conditions that exist indoors and outdoors. If the
outdoor temperature is below a prescribed limit and if the heating
system is off, the defrost sensor 19 will sense the low
temperature, and close the incoming fresh air damper 33. If the
unit is on in the heating mode the defrost sensor 19 will sense the
low temperature, and open the hot air intake variable defrost
device 46. Allowing heated air to circulate into the fresh air,
mixing with and increasing the temperature of the fresh air prior
to traveling through the passive cross flow, air-to-air heat
exchanger 13. Thereby allowing the unit to operate at much lower
temperatures than prior art without allowing freeze up at the
passive cross flow, air-to-air heat exchanger 13.
[0102] If the compression based heating/cooling system (heating
cooling system) 22 is on in the cooling mode: a different set of
conditions will apply. In the cooling mode the air enters the heat
(energy) exchange chamber 16 and the since heating/cooling system
22 is on in the cooling mode, the stale air will travel through the
liquid to air evaporator/condenser primary heat exchanger 10 which
will be in the condenser mode. Since the heating/cooling system 22
is on in the cooling mode, the Freon in the condenser will be much
warmer then the stale air. Heat will travel from the warm Freon to
the stale air, the cooled Freon will travel to the evaporator in
the heating/cooling system 22 and will be applied to the occupied
space air thereby increasing the efficiency of the heating/cooling
system 22. After the stale air has traveled through the liquid to
air evaporator/condenser primary heat exchanger 10, and has been
heated. It will then travel through the energy exchange stale air
channel 26 (see FIG. 3), and any remaining pre-cooled stale air
temperature will be transferred to the fresh air via the energy
exchange fresh air channel 25 (see FIG. 3) within the passive cross
flow air-to-air heat exchanger 13.
[0103] However, if the heating/cooling system 22 is not operating,
the stale air will travel through the PCAAHE 13, recovering
heat/cool energy which is then transferred to the incoming fresh
air. Using a cross flow heat exchanger (PCAAHE) 13 virtually
eliminating the opportunity for cross flow contamination. The stale
air is then ducted through the stale air exhaust duct 24 then
directly outside the conditioned space. The direct stale air
exhaust eliminates any possibility of transferring any smells from
the bathroom, kitchen and laundry room to other occupied areas.
[0104] In summary, if the liquid to air or geothermal 22 (see FIGS.
7 and 8) or air-to-air 22 (see FIG. 9) compression based heating or
cooling system 22 (see FIGS. 7-9) is operating, the stale air will
pass through the liquid to air evaporator/condenser secondary heat
exchanger 10 arrangement causing a change to the outflow
temperature after traveling through the passive cross flow,
air-to-air heat exchanger (PCAAHE) 13. Greatly increasing the
efficiency of both the heat recovery ventilation system and the
compression based heating/cooling system 22 (see FIGS. 7-9).
[0105] After the fresh air travels through the heat exchange
process, it then travels through the modulating pressure
differential air balancing flow device 27 and is mixed with the
occupied space return air. The indoor return air is drawn from the
return air registers 29 through the indoor return air duct, past
the return air filter 3, and then through the indoor
evaporator/condenser (liquid to air--heating/cooling) 5, then into
the indoor return and fresh air mixing chamber 14, via negative
pressure, created by the same indoor air distribution fan 12. As
both the occupied space, indoor return air, and the fresh air have
been drawn into the same indoor fresh and return air mixing
chamber, 14 and aggressively mixed, the Indoor air distribution fan
12 then distributes the mixed air to the indoor supply air duct 2.
Which in turn sends the mixed air to the individual room supply air
registers 28. Offering evenly distributed mixed air to each area
within the occupied space. The modulating pressure differential air
balancing device 27 is used to maintain balanced pressure/flow
between the incoming and outgoing air, to dictate a slight positive
pressure in the occupied space.
[0106] The preferred embodiment of the invention includes:
[0107] a reversible geothermal heating, cooling heat pump complete
with on-board humidification and with mid or high efficiency energy
recovery system
[0108] a reversible air-to-air heating, cooling heat pump complete
with on-board humidification and with mid or high efficiency energy
recovery system
[0109] a liquid cooled air conditioner complete with on-board
humidification and with mid or high efficiency energy recovery
system
[0110] a hydronic air handler and liquid cooled air conditioner
complete with on-board humidification and with mid or high
efficiency energy recovery system
[0111] an electric forced air heat and air-to-air, air conditioner
complete with on-board humidification and with mid or high
efficiency energy recovery system
[0112] a propane fired forced air heat and air-to-air, air
conditioner complete with on-board humidification and with mid or
high efficiency energy recovery system
[0113] an oil fired forced air heat and air-to-air, air conditioner
complete with on-board humidification and with mid or high
efficiency energy recovery system
[0114] a natural gas fired forced air heat and air-to-air, air
conditioner complete with on-board humidification and with mid or
high efficiency energy recovery system
[0115] The key to the efficiency increases is based on the fact
that the invention uses a compression based system which allows for
increased efficiency, based on the fact that the invention can use
primary and secondary exchange. The primary and secondary exchange
allows for increased efficiency because the invention couples the
compression system with the passive heat exchanger, thereby
increasing the ability to exchange energy by the two exchange
methods. The existing technology uses only passive exchange.
Passive exchange is limited. Evaporative and condensing exchange
methods are much more aggressive and capable of energy exchange. By
marrying the two methods we are essentially increasing the
efficiency on both systems. The HRV increase would be an increase
of about 10 to 15% over traditional passive methods, and the
compression based (heating/cooling) side would increase by
approximately 5 to 7%.
[0116] The remote compression system, as shown in FIG. 5, offers
the benefit of remote installation. The integrated split system
would offer all the benefits and operational parameters of all
other unitary designs, as best shown in FIGS. 1 and 2.
[0117] For greater clarity, Table 1 below lists the various parts
and components shown in the drawings:
1TABLE I Description of Parts and Components Ref. no. Description 1
flexible non-insulated indoor stale air duct - from moist air areas
2 main indoor supply air duct from system 2-1 main indoor supply
air duct canvass noise reduction connection 2-2 main indoor supply
air noise reduction insulation 3 main indoor return air duct to
system 3-1 main indoor return air duct canvass noise reduction
connection 4 outdoor stale air exhaust weather hood 4-1 outdoor
stale air exhaust weather hood bird screen 4-2 outdoor stale air
exhaust weather hood collar wall connection 5 indoor reversible
evaporator/condenser (Freon to air) - air coil 5-1 refrigeration
line in or out - to or from indoor reversible evaporator/condenser
(Freon to air) air coil 5-2 refrigeration line in or out - to or
from indoor reversible evaporator/condenser (Freon to air - direct
exchange) - air coil 6 absorption/rejection evaporator/condenser
Freon to liquid - indoor water coil 6-1 refrigeration line in or
out - to or from absorption/rejection evaporator/condenser Freon to
liquid - indoor water coil 6-2 refrigeration line in or out - to or
from absorption/rejection evaporator/condenser Freon to liquid -
indoor water coil 7 outdoor fresh air intake weather hood 7-1
outdoor fresh air intake weather hood bird screen 7-2 outdoor fresh
air intake weather hood collar wall connection 8
absorption/rejection evaporator/condenser air to Freon outdoor air
coil - air to air system 9 electronic controls system c/w on-board
diagnostics 10 secondary, high efficiency, active reversible, vapor
compression, evaporator/condenser heat exchanger 10-1 refrigeration
line in or out - to or from secondary, high efficiency, active
reversible evaporator/condenser heat exchanger 10-2 refrigeration
line in or out - to or from secondary, high efficiency, active
reversible evaporator/condenser heat exchanger 11 internally
trapped coupled condensate drain line 11ah Externally trapped
coupled condensate drain line for a split system 12 indoor air
distribution blower 13 primary, passive, cross flow air to air heat
exchanger core (PCAAHEC) 14 indoor return & fresh air mixing
chamber 15 room thermostat 16 heat recovery ventilation (energy)
exchange chamber 16-1 heat recovery ventilation (energy) exchange
chamber insulated door 17 dedicated stale air exhaust fan 18 indoor
grease catcher kitchen stale air filter 19 defrost sensor 20 stale
air heat recovery core particulate filter 21 fresh air heat
recovery core particulate filter 22 compression based heating &
cooling system or a reversible, mechanical vapor compression system
or a heat pump, FIG 6, 7, 8, 9. liquid to air - air to liquid - air
to air - heating/cooling unitary system 22cs compression based
heating & cooling system or a reversible, mechanical vapor
compression system or a heat pump, FIG 5. liquid to air - air to
liquid - air to air heating/cooling system - Compressor section for
a split system 22ah compression based heating & cooling system
or a reversible, mechanical vapor compression system or a heat
pump, fig 5. liquid to air - air to liquid - air to air
heating/cooling system -Air Handling Section For a Split System
22rp mechanical vapor compression system piping for a split system
fig 5. 23 insulated fresh air intake duct 24 insulated stale air
exhaust duct 25 non-insulated indoor stale air duct 26 defrost port
- from "fresh intake to exhaust chamber" or from "fresh air intake
to space 27 adjustable, weighted modulating pressure differential
air balancing device 28 indoor supply air registers 29 indoor
return air registers 30 indoor return air filter 31 system cabinet
31ah Remote direct expansion, "DX" system cabinet for split system
31cs Remote Compression section system cabinet for split system 32
domestic hot water tank 33 incoming fresh air balancing damper 34
brass cross for link from desuperheater within system to domestic
hot water tank 35 indoor stale air registers from moist air areas,
not including kitchen 36 loop pump(s) for closed loop operation 37
3 way loop purging valve(s) for purging closed loop system 38a
underground energy source inflow piping 38b underground energy
source discharge piping 39 hot water piping from desuperheater
within system to domestic hot water tank 40a main bi-flow tx valve
40a-1 refrigeration piping outgoing or incoming to or from main
bi-flow tx valve 40a-2 refrigeration piping outgoing or incoming to
or from main bi-flow tx valve 40b main bi-flow tx valve temperature
sensing bulb 41 4 way reversing valve 41-1 refrigeration piping
outgoing or incoming to or from 4 way reversing valve 41-2
refrigeration piping outgoing to common suction line from 4 way
reversing valve 41-3 refrigeration piping outgoing or incoming to
or from 4 way reversing valve 41-4 refrigeration piping incoming
hot gas line to 4 way valve 42 filter/drier 43 sight glass &
moisture indicator 44 Compressor 44-1 high pressure gas
refrigeration line out of compressor 44-2 low pressure gas suction
line in to compressor 45 unit mounted humidistat 46 hot air intake
variable defrost device 47 hot air bypass defrost tube 48 hydronic
or electric back-up/emergency heat cavity 49 humidifier atomizing
tube(s) 50 humidifier solenoid (24v) - opens on humidistat call 51
HRV drain pan 52 incoming stale air damper 53 HRV condensate drain
assembly 54 main blower motor 55 internal air coil drain pan 56a
standard 70 f warm or 100 f pre-heated air 24 v motorized defrost
damper 56b optional 70 f air, space air port 24 v motorized defrost
damper 56c optional 70 f air, exhaust air port 24 v motorized
defrost damper 57 external connection for humidifier 58 external
connection for condensate drain 59 external connection for water
out loop or well 59-1 water line out of water coil to loop or well
60 external connection for water in loop or well 60-1 water line in
to water coil from loop or well 61 desuperheater water coil 61-1
water line from domestic hot water tank to desuperheater water coil
61-2 water line to desuperheater water coil from domestic hot water
tank 61-3 refrigeration high pressure, hot gas line from
desuperheater water coil 61-4 refrigeration high pressure, hot gas
line in to desuperheater water coil 62 kitchen exhaust register 63
refrigeration chamber for a unitary system 63cs refrigeration
chamber for a split system 63ah refrigeration chamber for a split
system 64 drain pan over flow sensor 65 secondary bi-flow
accumulator 65-1 refrigeration piping outgoing or incoming to or
from secondary bi-flow accumulator 65-2 refrigeration piping
outgoing or incoming to or from secondary bi-flow accumulator 66
main accumulator 66-1 refrigeration low pressure line out of main
accumulator 66-2 refrigeration low pressure line into main
accumulator 67a secondary bi-flow tx or cap line air coil 67a-1
refrigeration piping outgoing or incoming to or from secondary
bi-flow tx or cap line air coil 67a-2 refrigeration piping outgoing
or incoming to or from secondary bi-flow tx or cap line air coil
67b secondary bi-flow tx line suction line temperature sensor 68
fresh air induction port 70 indoor air coil positive pressure
chamber 71 desuperheater water pump 72 external connect for
desuperheater incoming water flow 73 external connect from
desuperheater - outgoing water flow 74 water coil side t to connect
optional high efficiency secondary active recovery system 75 air
coil side t to connect optional high efficiency secondary active
recovery system 76 central thermostat, 2 stage heat, one stage cool
77 desuperheater high limit switch thermodisc 78 incoming
desuperheater water line 79 outgoing desuperheater water line 80
24v motorized zone valve for well geothermal system 81 a/c head
pressure control to regulate well system a/c water flow rate 82
pressure regulating valve for to modulate flow with well system 83
pressure gauge 84 flow meter 85 outdoor air to air blower 85-1
outdoor air to air blower motor 86 outdoor air to air defrost
sensor 87 incoming fresh air channel to PCAAHE 13 88 incoming stale
air channel to PCAAHE 13 89 incoming fresh air channel after PCAAHE
13 90 incoming fresh air channel after PCAAHE 13 91 optional
exhaust defrost bypass port 92 stale air chamber 93 optional 70 f
space air defrost port 94 optional positive pressure defrost
port
* * * * *