Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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TEMPERATURE CONTROL SYSTEM AND METHODS FOR OPERATING
SAME
TECHNICAL FIELD
[0001] This disclosure relates to temperature control of buildings and
other
structures, and more particularly to predictive systems and methods for
heating,
cooling and/or ventilating buildings and other structures.
BACKGROUND
[0002] The statements in this section merely provide background
information
related to the present disclosure and may not constitute prior art.
[0003] Temperature control systems such as heating, ventilation, and air
conditioning (HVAC) systems of structures, are operable to condition the
interior
air of the structure, i.e., to selectively heat and cool the interior air of
the structure.
The HVAC system includes mechanical systems for heating and cooling air that
is
delivered into the interior of the structure via ductwork, to selectively heat
or cool
the interior air.
[0004] Many HVAC systems have electronically controlled exterior air
dampers, which are capable (when used in conjunction with the blower of the
HVAC system) of circulating "fresh" exterior air into the structure. In
addition to
HVAC systems having mechanical means (cooling systems, often utilizing
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compressor(s), condenser fans, blower motors, etc.) to condition the space of
the
structure, many HVAC systems have the means to utilize cool exterior air to
condition the space, via an exterior air damper (also referred to as an
"economizer").
[0005] Many structures have electronically controlled exhaust systems,
which
are capable of exhausting air from the structure. Often, a structure's exhaust
system(s) draws air from near the roof of the structure, and exhausts that air
to the
outside of the structure.
[0006] The operation of the mechanical systems, e.g., cooling, heating,
and/or
ventilation systems, consumes energy, adds wear and tear to the equipment, and
increases the failure rate of that equipment, which may be financially costly.
As
such, it is desirable to condition the interior air of the structure to
desired
temperatures by utilizing predictive data.
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SUMMARY
[0007] A method for operating a temperature control system having a
cooling
system and ventilation system to vent outside air within a structure is
disclosed.
The method includes monitoring an interior temperature of the structure,
monitoring an exterior temperature of ambient air outside of the structure,
defining a first time range and a second time range, associating one or more
operating parameters of the temperature control system with the first time
range,
associating one or more operating parameters of the temperature control system
with the second time range, monitoring operational time and operational load
of
the cooling system for the first time range, predicting a space temperature
and an
outdoor air temperature for a subsequent time period, and controlling the
ventilation subsystem during the second time range based upon the monitored
operational time and operational load of the cooling subsystem for the first
time
range, the monitored interior and exterior temperatures, the predicted space
temperature, the predicted outdoor air temperature, and the one or more
operating
parameters of the cooling subsystem associated with the second time range.
[0008] This summary is provided merely to introduce certain concepts and
not
to identify key or essential features of the claimed subject matter.
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BRIEF DESCRIPTION OF THE DRAWINGS
[0009] One or more embodiments will now be described, by way of example,
with reference to the accompanying drawings, in which:
[0010] FIG. 1 schematically shows an exemplary HVAC system, in
accordance with the present disclosure;
[0011] FIG. 2 schematically shows an exemplary HVAC controller, in
accordance with the present disclosure;
[0012] FIG. 3 is a control scheme for operating the exemplary HVAC
system,
in accordance with the present disclosure;
[0013] FIG. 4 is a control scheme for operating the exemplary HVAC
system
using enthalpy values, in accordance with the present disclosure;
[0014] FIGS. 5 and 6 graphically illustrate exemplary occupied
operational
time ranges and load output for a cooling system and a heating system for
calculation of a cooling potential of a building or other structure, in
accordance
with the present disclosure;
[0015] FIG. 7 graphically shows operation of the HVAC system for venting
outside air into a structure with respect to indoor temperature, in accordance
with
the present disclosure;
[0016] FIGS. 8A and 8B are control schemes for operating the temperature
control system, in accordance with the present disclosure;
[0017] FIG. 9 graphically illustrates a heat transfer metric with
respect to
temperature, in accordance with the present disclosure; and
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[0018] FIGS. 10A and 10B graphically illustrates exemplary operating
metrics of the temperature control system, in accordance with the present
disclosure.
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DETAILED DESCRIPTION
[0019] Throughout the specification and claims, the following terms take
at
least the meanings explicitly associated herein, unless the context dictates
otherwise. The meanings identified below do not necessarily limit the terms,
but
merely provide illustrative examples for the terms. The meaning of "a," "an,"
and
"the" includes plural reference, and the meaning of "in" includes "in" and
"on."
The phrase "in one embodiment," as used herein does not necessarily refer to
the
same embodiment, although it may. Similarly, the phrase "in some embodiments,"
as used herein, when used multiple times, does not necessarily refer to the
same
embodiments, although it may. As used herein, the term "or" is an inclusive
"or"
operator, and is equivalent to the term "and/or," unless the context clearly
dictates
otherwise. The term "based upon" is not exclusive and allows for being based
upon additional factors not described, unless the context clearly dictates
otherwise. The word "exemplary" is used herein to mean "serving as an example,
instance, or illustration." Any embodiment described herein as "exemplary" is
not
necessarily to be construed as preferred or advantageous over other
embodiments.
As used herein the terms building and structure may be used interchangeably.
Upon a careful reading of the teachings herein, one skilled in the art may
readily
apply the teachings to any number of building and structure types falling
within
the spirit of this disclosure.
[0020] Various embodiments of the present invention will be described in
detail with reference to the drawings, where like reference numerals represent
like
parts and assemblies throughout the several views. Reference to various
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embodiments does not limit the scope of the invention, which is limited only
by
the scope of the claims attached hereto. Additionally, any examples set forth
in
this specification are not intended to be limiting and merely set forth some
of the
many possible embodiments for the claimed invention.
[0021] Referring now to the drawings, wherein the depictions are for the
purpose of illustrating certain exemplary embodiments only and not for the
purpose of limiting the same, FIG. 1 schematically shows an exemplary
temperature control system 10 that may help implement the methodologies of the
present disclosure. The system 10 may include various HVAC equipment
components 8 configured to condition the interior air of the structure, i.e.,
to
selectively heat and cool the interior air of the structure. The system 10
includes a
controller 6 for controlling the HVAC equipment components 8. In various
embodiments, the system 10 may include a server 5, a network 4 and/or a mobile
device 2. The methods and devices of the present disclosure may be practiced
with the HVAC system 10 and/or as part of HVAC system 10.
[0022] The server 5 may be directly communicatively connected to the
controller 6 and the mobile device 2 or communicatively connected via the
network 4. The server 5 may be: various embodiments of a computer including
high-speed microcomputers, minicomputers, mainframes, and/or data storage
devices. The server 5 preferably executes database functions including storing
and
maintaining a database and processes requests from the controller 6 and/or
mobile
device 2 to extract data from, or update, a database as described herein
below.
The server 5 may additionally provide processing functions for the mobile
device
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2 and the controller 6 as will become apparent to those skilled in the art
upon a
careful reading of the teachings herein.
[0023] As shown in FIG. 1, the HVAC controller 6 may be directly
communicatively connected to one or more of the HVAC equipment components
8 including one or more sensors 31, 32, 33, and/or 34. In one embodiment, the
controller 6 is wirelessly connected to the one or more HVAC equipment
components 8 via the network 4. In embodiments utilizing a mobile device 2,
the
mobile device 2 may be physically or wirelessly connected to the network 4
and/or the controller 6 during selected periods of operation without departing
from the teachings herein. Components of the system 10 are shown in FIG. 1 as
single elements. Such illustration is for ease of description and it should be
recognized that the system 10 may include multiple additional components in
various embodiments without departing from the teachings herein. For example,
in various embodiments the controller 6 may be incorporated into the server 5.
[0024] The exemplary HVAC system 10 shown in FIG. 1 includes an HVAC
controller 6, which may be or may include a thermostat or a hydronic heat
transfer
system control in some embodiments. The HVAC controller 6 may be configured
to communicatively interact with and control various components of the HVAC
components 8. As shown in FIG. 1, the HVAC controller 6 may be directly
connected to the HVAC components 8 or connected via a network 4 which may
be a locally based network or a wider network such as the Internet. In various
embodiments, the mobile device 2 is communicatively connected to the
controller
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6 so that a user may control the HVAC components 8 using the mobile device 2
via the controller 6.
[0025] The HVAC components 8 may include a heating system 12, a cooling
system 14, a ventilation system 16 including a fan, i.e., a blower, a
humidification
system 18 and/or any other HVAC components or systems, as desired such as an
outside air damper 22 or intake damper 23. In various embodiments, HVAC
components include auxiliary heating and cooling equipment. Exhaust fans 37
and supply air fans 16, removing air from the structure, and moving air into
the
structure, respectively, may also be used in various embodiments. The HVAC
components 8 primarily function as a forced air system although auxiliary HVAC
components may be used in conjunction to supplement conditioning of the
environment within the building. For example, auxiliary heat may be provided
by
electrical resistive heaters, hot water radiant heat, boilers, and/or electric
base
board heaters in various embodiments.
[0026] As illustrated in exemplary FIG. 1, the heating system 12 and the
cooling system 14 are combined in a forced air system; however, it is
contemplated herein that the heating and cooling systems 12 and 14 may be
separated. For example, in residential and/or light commercial applications,
in
various embodiments, a heat pump system may be utilized separate from an air
conditioning cooling system 14.
[0027] In various embodiments the HVAC components 8 include any number
of intake and outtake dampers. In the illustrated embodiment a filter 21, a
first
damper 22, and a second damper 23 are utilized consistent with the teachings
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herein. The damper 22 may be in communication with outside air and the fan 16
is in communication with one or more of the dampers 22 and 23 within a ducting
24, for example. The dampers 22 and 23 may be selectively actuatable as a
group
or individually in various embodiments.
[0028] The HVAC components 8 may include cooling equipment, which may
include more than one unit and/or more than one stage of cooling. The HVAC
components 8 are selectively in gaseous communication with exterior ambient
air
and including operability to intake and/or vent exterior ambient air. In
various
embodiments the ventilation equipment may provide different levels of air
movement as described herein below. The HVAC components 8 may include
other units such as a humidifier unit, a dehumidifier unit, a UV filter unit
and/or
any other suitable HVAC unit and/or equipment as desired.
[0029] The HVAC components 8 may include one or more sensors, such as
an exterior ambient air temperature sensor 31, an exterior humidity sensor 32,
a
return temperature sensor 33, and/or a smoke detector 34. The sensors 31, 32,
33,
and 34 may be directly or indirectly communicatively connected to the
controller
6. The exterior ambient temperature sensor 31 is configured to measure a
temperature of the outside air and, for example, may be mounted to an exterior
of
the building, or factory installed as part of the HVAC components 8. The
exterior
humidity sensor 32 may also be mounted external to ducting of the HVAC
components 8 or factory installed as part of the HVAC components 8. An
interior
temperature sensor 35 measures a temperature of the interior air of the
building.
The sensor 35 may be internal to the controller 6 or external. Optionally, an
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interior humidity sensor 36 measures the humidity of the interior air of the
structure. The sensor 36 may be internal to the controller 6 or external. In
one
embodiment, the controller 6 may obtain outside, i.e., exterior air
temperature
and/or humidity conditions through an online weather service or may be in
communication with a building automation system having equivalent measuring
functionality. In one embodiment, predicted weather conditions may be utilized
by the controller 6. In various embodiments, the interior and exterior
humidity
sensors 36 and 32 are optional. In various embodiments, sensors 33 and 34 are
optional.
[0030] The network 4 may be any suitable series of points or nodes
interconnected by communication paths. The network 4 may be interconnected
with other networks and contain sub network(s) such as, for example, a
publicly
accessible distributed network like the Internet or other telecommunications
networks (e.g., intranets, virtual nets, overlay networks and the like). The
network
4 may facilitate the exchange of data between and among the HVAC components
8, the HVAC controller 6, and the sensors 31, 32, 33, 34, 35 and 36; although
in
various embodiments the HVAC controller 6 may be directly connected to the
HVAC components 8 and/or the sensors 31, 32, 33, 34, 35 and 36.
[0031] In various embodiments, the mobile device 2 may include one or
more
applications that the user may operate. Operation may include downloading,
installing, turning on, unlocking, activating, or otherwise using the
application in
conjunction with the controller 6. The application may comprise at least one
of an
algorithm, software, computer code, executable instruction sets and/or the
like, for
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example, mobile application software. In the alternative, the application may
be
utilized remotely through a website accessible through the world wide web.
[0032] FIG. 2 shows the exemplary HVAC controller 6. The controller 6
includes a central processing unit (CPU) 50, random access memory (RAM) 52,
input/output circuitry 54 for connecting peripheral devices such as a storage
medium 56 to a system bus 60, a display adapter 58 for connecting the system
bus
60 to a display device, a user interface adapter 62 for connecting user input
devices such as various dials buttons and/or keypads, to the system bus 60,
and a
communication adapter 64 for connecting the controller 6 to the network 4. The
memory 52 and storage medium 56 may be used to store any appropriate
information such as HVAC control routines or code, historical performance
data,
HVAC system and/or HVAC controller parameters, one or more programmable
schedules for changing HVAC system parameters over time, etc.
[0033] The central processing unit 50 is preferably one or more general-
purpose microprocessor or central processing unit(s) and has a set of control
algorithms, comprising resident program instructions and calibrations stored
in
the memory 52 and executed to provide the desired functions. In one
embodiment,
an application program interface (API) is preferably executed by the operating
system for computer applications to make requests of the operating system or
other computer applications. The description of the central processing unit 50
is
meant to be illustrative, and not restrictive to the disclosure, and those
skilled in
the art will appreciate that the disclosure may also be implemented on
platforms
and operating systems other than those mentioned.
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[0034] The HVAC controller 6 may include any number of suitable
components related to effecting control of the HVAC system 10. For example,
HVAC controller 6 may include a user interface 68 which may be graphical. The
user interface 68 may include one or more displays, switches, and/or buttons
that
a user may actuate or otherwise control. In one embodiment, a touchscreen
display may be provided to display the user interface 68 and provide
interaction
therewith.
[0035] In one embodiment, one or more of a cooling device, heating
equipment and/or ventilation equipment may be distinct systems controlled,
either
directly or indirectly, by the HVAC controller 6. In some embodiments, it is
contemplated that the HVAC controller 6 may separately control each component
8. HVAC system parameters may include set points for heating, cooling,
humidity, etc., modes for ventilation equipment, fan settings, and the like
and as
further described below.
[0036] The HVAC controller 6 may include one or more internal sensors
65,
such as a temperature sensor and/or a humidity sensor. The internal sensors 65
may be in addition to the sensors 35 and 36 and may be used for supplemental
or
redundancy purposes, as exemplary. The HVAC controller 6 may include one or
more outputs configured to issue operation commands to the HVAC components
8. It is contemplated herein that the HVAC controller 6 may be configured to
execute any method of the present disclosure. The HVAC controller 6 may be
communicatively connected to one or more sensors connected external to a
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building structure and external to a housing of the controller 6. The
connection
may be via wire or via a wireless embodiment of the network 4.
[0037] In various embodiments, the HVAC controller 6 may maintain in its
memory an operating schedule that may be used to control the HVAC system
based upon time and/or day. The schedule may, for example, be a daily
programmable schedule or any other schedule. In some cases, the schedule may
have a number of days and one or more time periods for each of at least some
of
the days. In some instances, the nominal schedule may include an "occupied",
an
"unoccupied", and a "stand-by" time period for each of the days of a week. The
schedule may have at least one set point associated with each of the one or
more
time periods. The schedule may be maintained in the memory 52, and may be
modified by an end user in various embodiments.
[0038] FIG. 3 shows a control scheme 100 for operating the controller 6
and
the HVAC components 8. Although the control scheme 100 is shown as discrete
elements, such an illustration is for ease of description and it should be
recognized
that the functions performed by the control scheme 100 may be combined in one
or more devices, e.g., implemented in software, hardware, and/or application-
specific integrated circuitry (ASIC) and executed, in some cases, concurrently
or
in parallel. For example, monitoring of the various sensors may be executed
concurrent with any number of execution steps.
[0039] The control scheme 100 is directed at operating efficiencies that
can be
gained from utilizing exterior ambient conditions to ventilate outside air
into the
structure and/or condition the interior environment. For example, during warm
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summer months, the coldest part of the day is typically in the early morning,
such
as between 4:00am and 6:00am. As set forth further below, during this early
morning time, the controller 6 instructs one or more of the HVAC components 8
to operate to effect the intake of cool exterior air (and either passively or
actively
exhaust warm interior air) based upon exterior air conditions, interior air
conditions, the usage of the HVAC components 8 during the previous day, and
current settings of the HVAC components 8. In other words, based upon these
variables, the controller 6 may instruct the HVAC components 8 to intake cool
exterior air, and optionally to exhaust warm interior air to decrease the
temperature of the interior air of the structure to a temperature between the
occupied heating set point and the occupied cooling set point of the HVAC
components 8, as shown in FIG. 7.
[0040] To capitalize on preferential exterior ambient conditions and
achieve
greater operating efficiencies, the control scheme 100 is configured, in one
exemplary implementation, to operate one or more of the HVAC components 8
using the controller 6 to condition the interior environment. As FIG. 3 shows,
the
control scheme 100 is initiated at step 102 whereby the controller 6 operates
the
HVAC components 8 based upon a user's predefined or default operating
parameters, and the results of a prior iteration of the control scheme 100. In
the
exemplary case of cooling the interior air of a building, the control scheme
100
operates during cool mornings to proactively ventilate the building with cool
exterior air based upon the operation of the HVAC components 8 during a
previous period, e.g., during the previous day.
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[0041] In one embodiment, the HVAC components 8 may transition between
an occupied state and an unoccupied state. In one embodiment, the control
scheme 100 is operated only at a predetermined time range. While operating in
an
occupied state, the controller 6 typically operates to maintain interior air
conditions at desired levels, for example, levels directed at maintaining
comfortable conditions for occupants, e.g., a user-supplied set point. In one
embodiment, while in the predetermined time range, the controller 6 executes
the
control scheme 100 to maintain interior air conditions at a second set of
preferential conditions, which may be directed at a different set of
objectives, e.g.,
energy conservation, equipment wear reduction, and/or improvement of indoor
air
quality.
[0042] In one embodiment, operation of one or more of the HVAC
components 8 may be based upon operation that occurred during the previous
period. The previous period may be, for example the previous day, i.e., the
previous 24 hours. Alternatively, the previous period may be, for example, the
previous day less any time duration during which the process 100 operated. For
example, if the process 100 operated for two hours during the previous day
(for
example, from 4:00am to 6:00am), the previous period may be 22 hours (i.e., 24
hours minus 2 hours).
[0043] At step 104, the controller 6 may execute the control scheme 100
during a predefined operating time range. The controller 6 may then deactivate
the control scheme 100 after or outside of the predefined operating time
range.
The operating time may be between 4:00am and 6:00am, for example. In one
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embodiment, the operating time range may be user-defined. Alternatively, the
operating time range may initiate at any suitable predefined time and may last
for
any suitable predefined duration. In one embodiment, operating time may be
defined based upon occurrence of an event. In one embodiment, operating time
may begin at any suitable predefined time, and not terminate until block 116
or
block 120 of figure 3 is "no". In one embodiment, operating time may be
defined
based upon historical trending of the coolest part of the day. As exemplary, a
photocell could be utilized to estimate a time of dawn, and then, in turn,
apply that
time to the next day's predetermined start and stop times of the operating
range.
In one embodiment, a start and stop time of the control scheme 100 may be
determined based upon monitored exterior air temperature. For example, a time
associated with a lowest temperature reading may be set as the start time or a
predetermined time period before the monitored lowest temperature may be set
as
the start time and a predefined duration after the start time may be
calculated for
the stop time.
[0044] At step 106, the control scheme 100 determines a cooling
potential of
the interior air based upon the previous period, e.g., the previous day.
Determining the cooling potential includes determining the cooling usage of
the
HVAC components 8 from the previous period, e.g., the previous day. More
specifically, determining the cooling potential includes adding the sum of the
products of cooling load output and run time of the HVAC components 8 from the
previous period, which may be calculated using the following equation:
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cocrt . = (col * crti) + (coz * crtz) + (co. * crte)
wherein
co = cooling load output (as a factor of the total possible cooling load
output);
crt = the cooling run time of the co (over the run time period of the co);
n = the total number of cooling states in the (user defined) previous period;
and
cocrt . = the sum of the products of the cooling load outputs (over the time
period) and the corresponding cooling run times (over the time period).
[0045] To illustrate using example values, if in the previous period the
cooling system 14 operated in cooling mode at 50% load output for a period of
30 minutes, and at 100% load output for a period of 180 minutes, then
cocrt . = (col * crti) + (coz * crtz)
cocrt . = (.5 * 30 minutes) +(1 * 180 minutes), which reduces to: cocrt .=
(15 minutes) + (180 minutes), which is reduced to: cocrt .= 195 minutes.
[0046] Determining the cooling potential includes determining the
heating
usage of the heating system 12 from the previous period, e.g., the previous
day.
More specifically determining the cooling potential includes adding the sum of
the products of heating load output and operating time of the heating system
12
from the previous period, which may be calculated using the following
equation:
hohrt . = (hoi * hrti) + (hoz * hrtz) + (hoe * hrte)
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where
ho = heating load output (as a factor of the total
possible heating load output);
hrt = heating run time of the ho (over the run time
period of the ho, while ho is in a stable state);
n = the total number of heating states in the user
defined time period being measured; and
hohrt sum = the sum of the products of the heating load outputs (over the time
period) and the corresponding heating run times (over the time period).
[0047] To illustrate using example values, if in the previous period the
heating system 12 operated in heating mode at 50% load output for a period of
30 minutes, and at 100% load output for 180 minutes, then
hohrt sum = (hoi * hrti) + (hoz * hrtz);
hohrt sum = (.5 * 30 minutes) + (1 * 180 minutes);
hohrt sum = (15 minutes) + (180 minutes); and hohrt sum = 195 minutes.
[0048] The cooling potential is calculated by subtracting the sum of the
product of the heating load output and the run time (hohrt_) from the sum of
the cooling load output and run time (cocrt sum). Specifically, the controller
6
subtracts the hohrt sum from the cocrt sum to obtain the cooling potential
(cp). For
example, using the example values above:
If cp (cooling potential) = cocrt sum - hohrt sum; If the hohrt sum = 100
minutes;
and
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If the cocrt sum = 150 minutes; then cp = cocrt sum ¨ hohrt sum
cp = 150 minutes-100 minutes; and cp = 50 minutes
[0049] FIGS. 5 and 6 graphically illustrate exemplary time ranges of
exemplary operation of a cooling system and a heating system. FIG. 5
graphically
shows a first sum of products of operational time and operational load of the
cooling system and a second sum of products calculation for operational time
and
operational load of the heating system. The controller may difference the
second
sum of products from the first sum of products. A positive result indicates
cooling
potential, while a zero or negative result indicates no cooling potential.
[0050] FIG. 6 shows an alternative to a sum of products calculation. For
exemplary embodiments of cooling and heating equipment wherein cooling load
output and heating load output are obtained as a function of operating load
may be
represented with respect to operating time. To determine a cooling potential
the
controller may execute a first integral calculation for an operational load of
the
cooling system as a function of operational time over the first time range,
execute
a second integral calculation for an operational load of the heating system as
a
function of operational time over the first time range and then difference the
second integral from the first integral. Similar to above, a positive result
indicates
cooling potential, while a negative result indicates no cooling potential.
[0051] At step 108, the control scheme 100 subtracts a time bias quanta
from
the cooling potential (cp). The time bias may be defined or set by the user.
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time bias is subtracted from the cooling potential value to inhibit use of the
control scheme 100 when only slightly more cooling than heating was observed
in the previous period. In such a situation, it is likely that having the
equipment
cool the structure in the early morning may actually cause the heating
function to
be energized prior to the "heat of the day," which may be around 3:00pm. A
user defined time bias may be adjusted or may be a default value, but as a
default, that value may be set to 60 minutes.
[0052] For example, based upon the example values above:
entc = cp - time bias
wherein
time bias = time bias; and
entc = enable control scheme 100 if positive value.
[0053] For example, if cp = 50 minutes; and if time bias is set to 60
minutes
(which can be the default value); then entc = 50 minutes - 60 minutes; and
entc =
-10 minutes.
[0054] At step 110, the control scheme 100 determines whether the entc
value is positive or negative. If the entc value is zero or negative, the
control
scheme 100 stops the process 100 until the next time period 130. In other
words,
if the entc value is zero or negative (after being biased by the user defined
time
bias), then conditions may, undesirably, cause the controller 6 to effectuate
the
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heating system 12 during the upcoming period, before the heat of the day, if
the
control scheme 100 were to ventilate the air in the building. Accordingly,
when
the entc 110 value is negative, to avoid utilizing the heating system 12 after
having cooled the structure, the control scheme 100 is not operated to utilize
the
exterior air damper 22, and/or fan 16 to intake outdoor air and/or the exhaust
fan(s) 37 to exhaust interior air thereby avoiding cooling the structure
undesirably and avoiding inefficient use of the heating system 12 during the
upcoming time period.
[0055] At step 112, the control scheme 100 measures indoor and outdoor
air
conditions. At step 114, the control scheme 100 adjusts an exterior air
temperature measurement using a user-defined or default temperature bias.
Factoring in a temperature bias will cause the controller 6 to be less likely
to
determine that the exterior air is suitable to use for cooling the structure.
The
greater the temperature bias, the less likely the controller 6 will find the
exterior
air suitable. The temperature bias is added to compensate for electrical
consumption of the equipment which operates during the control scheme 100 to
cool the structure. For example, while running the fan(s) 16 alone consumes
less electricity than running a number of the other HVAC components 8, e.g.,
compressors, condenser fans, etc., there is still energy consumption used by
simply running the fan 16. The "break even" point for venting the exterior air
is
not when the exterior air temperature or enthalpy is slightly less than that
of the
interior air temperature or enthalpy, respectively, but is when the interior
air
temperature or enthalpy is significantly greater than the exterior air
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temperature or enthalpy, respectively, so that the cost to utilize the intake
of
exterior air and the exhausting of indoor air (either passively or actively)
for
cooling is profitable, in terms of the cost per BTU of heat transfer (or
electricity
consumption per BTU of heat transfer). Based on factors including, but not
limited to, indoor air humidity set points, fresh air intake considerations,
specific
equipment characteristics, and the local cost of electricity, the optimal
temperature or enthalpy difference may change. Enthalpy of the exterior air
may
be determined or estimated using exterior temperature and humidity
measurements from the exterior temperature sensor 31 and the exterior humidity
sensor 32 using known calculation techniques and/or modeling processes.
[0056] At step 116, subsequent to determining that the entc value is
positive
the control scheme 100 analyzes the exterior ambient air to determine whether
the exterior air is suitable. The determination of whether the exterior air is
suitable may be based upon the use of industry standard enthalpy calculations,
or
temperature calculations, or some combination of the two. Specifically, the
interior air condition and exterior air condition is measured. The suitability
may
be based upon interior and exterior air temperature and, optionally, humidity
values, provided by the sensors, such as interior temperature sensor 35,
exterior
temperature sensor 31, interior humidity sensor 36, and exterior humidity
sensor
32, network values, etc., or may simply utilize interior and exterior air
temperature sensors 35 and 31, respectively, network values, etc. If the
controller
6 determines that the exterior air is not suitable for intake, then the
control
scheme is stopped at 130 and the controller 6 does not operate the damper(s)
22
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and 23 and the fan 16 to intake exterior air, and optionally the exhaust
fan(s) 37
to exhaust interior air.
[0057] At step 118, subsequent to determining that the exterior air is
suitable
for cooling (or economization), the controller 6 determines a night time
cooling
set point. The night time cooling set point is determined by subtracting the
occupied heating set point, e.g., a "heating" set point on a conventional
thermostat, from the occupied cooling set point, e.g., a "cooling" set point
on a
conventional thermostat, multiplying that value by a bias value (between 0 and
1,
with a default of 0.67, for example), and then subtracting that product from
the
occupied cooling set point. The bias value may be used, for example, to affect
the
degree of pre-cooling within the building, with a larger biasing value
resulting in
more pre-cooling and a smaller biasing value resulting in less pre-cooling.
For
example, the following equation applies:
ntcsp = ocsp - (ocsp - ohsp) * udbv
wherein
ntcsp = night time cooling set point; ocsp = occupied cooling set point;
ohsp = occupied heating set point; and udbv = user defined bias value.
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[0058] Example values are applied to this equation: If ocsp = 70F; If
ohsp =
65 F; and udbv = 0.67; then ntcsp = ocsp - (ocsp - ohsp) * udbv; ntcsp = 70 F -
(70 F - 65 F) * 0.67; ntcsp = 70 F - 5 F * 0.67; ntcsp = 70 F - 3.35 F; and
ntcsp =
66.65 F.
[0059] As explained below, with respect to FIG. 4 and control scheme
200,
alternatively to utilizing only temperature values to determine the ntcsp,
when
humidity values are available, enthalpy values could be entered in place of
temperature values to determine the ntcsp. In such a case, the value of the
ntcsp
could be expressed in terms of enthalpy rather than simple temperature.
Likewise, alternatively to utilizing only temperature values to determine the
result of step 120, when humidity values are available, indoor air enthalpy
and
outdoor air enthalpy could be used rather than simple temperatures.
[0060] At step 120 the control scheme 100 has determined the ntcsp, it
compares the ntcsp with the interior air temperature. If the interior air
temperature is less than or equal to the ntcsp, then the control scheme 100
terminates all sequences 130.
[0061] At step 122, if the interior air temperature is greater than the
ntcsp,
then the control scheme 100 energizes, for example, a relay, triac output,
network
signal, etc., which will, at least, energize equipment which causes cool
outdoor
air to enter the building, e.g., the fan 16, and open the exterior air damper
22
(also known as the fresh air damper 22). The control scheme 100 may energize
any connected exhaust equipment such as the exhaust fan(s) 37, which may
remove air from the building, to help facilitate economization of the primary
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heating, cooling, and ventilation equipment. The relay, triac output, network
signal, etc. will remain active until conditions change in blocks 110, 116, or
120.
In one embodiment, the controller will terminate step 122 if the controller 6
is
transitioned to an occupied state. In one embodiment, the controller 6 will
terminate step 122 if a current time is outside of the predefined time range.
[0062] At various points in the control scheme 100, the controller 6 may
transition the one or more of the HVAC components 8 to a stopped operating
state 130. The control scheme 100 may be configured to transition out of step
130
after a predefined duration of time or upon occurrence of an event.
[0063] FIG. 4 shows a control scheme 200 for operating the controller 6
and
the HVAC components 8 illustrating operation of the system 10 using enthalpy
values determined from temperature and humidity measurements. Although the
control scheme 200 is shown as discrete elements, such an illustration is for
ease
of description and it should be recognized that the functions performed by the
control scheme 200 may be combined in one or more devices, e.g., implemented
in software, hardware, and/or application-specific integrated circuitry (ASIC)
and
executed, in some cases, concurrently or in parallel. For example, monitoring
of
the various sensors may be executed concurrent with any number of execution
steps.
[0064] The control scheme 200 is directed at operating efficiencies that
can be
gained from utilizing exterior ambient conditions to ventilate outside air
into the
structure and/or condition the interior environment. For example, during warm
summer months, the coldest part of the day is typically in the early morning,
such
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as between 4:00am and 6:00am. As set forth further below, during this early
morning time, the controller 6 instructs one or more of the HVAC components 8
to operate to effect the intake of cool exterior air (and either passively or
actively
exhaust warm interior air) based upon exterior air conditions, interior air
conditions, the usage of the HVAC components 8 during the previous day, and
current settings of the HVAC components 8. In other words, based upon these
variables, the controller 6 may instruct the HVAC components 8 to intake cool
exterior air, and optionally to exhaust warm interior air to decrease the
temperature of the interior air of the structure to a temperature between the
occupied heating set point and the occupied cooling set point of the HVAC
components 8, as shown in FIG. 7.
[0065] To capitalize on preferential exterior ambient conditions and
achieve
greater operating efficiencies, the control scheme 200 is configured, in one
exemplary implementation, to operate one or more of the HVAC components 8
using the controller 6 to condition the interior environment. As FIG. 4 shows,
the
control scheme 200 is initiated at step 202 whereby the controller 6 operates
the
HVAC components 8 based upon a user's predefined operating parameters, e.g.,
set points, and the results of a prior iteration of the control scheme 200. In
the
exemplary case of venting exterior air into an interior of the structure, the
control
scheme 200 operates during cool mornings at predefined or determined times to
proactively ventilate the building with cool exterior air based upon the
operation
of the HVAC components 8 during a previous period, e.g., during the previous
day.
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[0066] At step 204, the controller 6 may execute the control scheme 200
during a predefined operating time range, a predefined time duration having a
determined start time based upon prior measured exterior air conditions and/or
photocell measurements.
[0067] At step 206, the control scheme 200 determines a cooling
potential of
the interior air based upon the previous period, e.g., the previous day,
similar to
step 106 described herein above with respect to control scheme 100.
[0068] At step 208, the control scheme 200 subtracts a time bias or
buffer
value from the determined cooling potential (cp). This time bias is subtracted
from the cooling potential value to prohibit use of the control scheme 200
when
only slightly more cooling than heating was observed in the previous period.
[0069] At step 210, the control scheme 200 determines whether the entc
value is positive or negative or zero. The entc value is the difference
between the
cooling potential value and the time bias or buffer value. If the entc value
is zero
or negative, the control scheme 200 stops the process 200 until the next time
period by transitioning the control scheme 200 to a stop state 230.
[0070] At step 212, the control scheme 200 measures interior and
exterior air
conditions including an exterior temperature and exterior humidity. At step
214,
the control scheme 200 determines the exterior enthalpy using the monitored
exterior air conditions including temperature and humidity. Enthalpy of the
exterior air may be determined or estimated using exterior temperature and
humidity measurements from the exterior temperature sensor 31 and the exterior
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humidity sensor 32 using known calculation techniques and/or modeling
processes.
[0071] At step 215, the control scheme 200 adjusts the determined
enthalpy
value using a buffer value. Factoring in a buffer will cause the controller 6
to be
less likely to determine that the exterior air is suitable to use for cooling
the
structure. The greater the buffer value, the less likely the controller 6 will
find the
exterior air suitable. The buffer value is added to compensate for electrical
consumption of the equipment which operates during the control scheme 200 to
cool the structure. For example, while running the fan(s) 16 alone consumes
less electricity than running a number of the other HVAC components 8, e.g.,
compressors, condenser fans, etc. in combination with each other, there is
still
energy consumption used by simply running the fan 16. The "break even" point
for venting the exterior air is not when the exterior air temperature or
enthalpy is
slightly less than that of the interior air temperature or enthalpy,
respectively,
but is when the interior air temperature or enthalpy is significantly greater
than
the exterior air temperature or enthalpy, respectively, so that the cost to
utilize
the intake of exterior air and the exhausting of indoor air (either passively
or
actively) for cooling is profitable, in terms of the cost per BTU of heat
transfer
(or electricity consumption per BTU of heat transfer). Based on factors
including,
but not limited to, indoor air humidity set points, fresh air intake
considerations,
specific equipment characteristics, and the local cost of electricity, the
optimal
temperature or enthalpy difference may change.
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[0072] At step 216, subsequent to determining that the entc value is
positive
the control scheme 200 analyzes the exterior ambient air to determine whether
the exterior air is suitable. The determination of whether the exterior air is
suitable may be based upon the use of industry standard enthalpy calculations,
or
temperature calculations, or some combination of the two. In one embodiment,
the interior humidity value and exterior humidity values are compared. If the
controller 6 determines that the exterior air is not suitable for intake,
e.g., interior
conditions are preferable to exterior conditions, then the control scheme 200
is
stopped at 230 and the controller 6 does not operate the damper(s) 22 and 23
and
the fan 16 to intake exterior air, and optionally the exhaust fan(s) 37 to
exhaust
interior air.
[0073] At step 218, subsequent to determining that the exterior air is
suitable
for venting exterior air to the interior of the structure, the controller 6
determines
a night time enthalpy cooling set point similarly to the process described
herein
above with respect to control scheme 100 only using enthalpy values and not
exclusively temperature values. The night time cooling set point 218 is
determined by subtracting the occupied enthalpy heating set point, from the
occupied enthalpy cooling set point, and then multiplying that value by a bias
value (between 0 and 1, with a default of 0.67, for example), and then
subtracting
that product from the occupied enthalpy cooling set point. For example, the
following equation applies:
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ntcsp = ocsp - (ocsp - ohsp) * udbv
wherein
ntcsp = night time cooling set point; ocsp = occupied enthalpy cooling set
point;
ohsp = occupied enthalpy heating set point; and udbv = user defined bias
value.
[0074] At step 220 the control scheme 200 has determined the ntcsp, it
compares the ntcsp with the interior enthalpy. If the interior air enthalpy is
less
than the ntcsp, then the control scheme 200 terminates all sequences by
transitioning to block 230.
[0075] At step 222, if the interior air enthalpy is greater than the
ntcsp, then
the control scheme 200 energizes, for example, a relay, triac output, network
signal, etc., which will, at least, energize equipment which causes cool
outdoor
air to enter the building, e.g., the fan 16, and open the exterior air damper
22. The
process may energize any connected exhaust equipment, which may remove air
from the building, to help facilitate economization of the primary heating,
cooling, and ventilation equipment. The relay, triac output, network signal,
etc.
will remain active until conditions change in blocks 210, 216, or 220. In one
embodiment, the controller will terminate step 222 if the controller 6 is
transitioned to an occupied state. In one embodiment, the controller 6 will
terminate step 222 if a current time is outside of the predefined time range.
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[0076] At various points in the control scheme 200, the controller 6 may
transition the one or more of the HVAC components 8 to a stopped operating
state 230. The control scheme 200 may be configured to transition out of step
230
after a predefined duration of time or upon occurrence of an event.
[0077] FIG. 7 graphically shows operation of the HVAC system for venting
exterior air into a structure with respect to indoor temperature, while
outdoor air
is suitable for cooling 116. As FIG. 7 shows, specific condition ranges
related to
the structure's interior and monitored exterior temperature result in venting
exterior air to the interior of the structure. In one embodiment, venting of
the
exterior air to the inside will occur when: (1) the time biased cooling
potential is
positive; and (2) the indoor temperature is greater than a cooling set point
associated with an unoccupied status of the structure, i.e., (second time
range).
As illustrated in FIG. 7, the criteria for venting of the exterior air to the
inside is
satisfied in zone 300.
[0078] As set forth above, in one embodiment the controller 6 may
utilize a
thermostat of the HVAC components 8. For example, when the controller 6
utilizes a conventional thermostat of the HVAC components 8, the following is
typical with most conventional thermostats: G terminal = fan 16 on; Y1
terminal
= cooling first stage; Y2 terminal = cooling second stage; W1 terminal =
heating
first stage; W2 terminal = heating second stage.
[0079] A capacitor may be set to charge when the Y1 terminal is
activated,
with a resistor inline with the capacitor, which acts as a regulator for the
current.
The same capacitor could also be charged when the Y2 terminal is activated,
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which would also have an inline "regulator" resistor. Likewise, the heating
terminals could also have a capacitor which is charged via the W1 and W2
terminals, with "regulating" resistors in-line. The charges of the two
capacitors
would be discharged via a short, which is regulated by a (high value)
resistor. At
the initiation time of the control scheme 100, e.g., 4:00 am, the total
charges of
each of the two capacitors could be compared via an integrated circuit (IC) to
determine the cooling potential (as set forth above) for the upcoming time
period.
The time bias could be incorporated by adding a potentiometer to the circuit.
When used in this configuration, some level of circuit integration could be
added.
For example, a time clock of the thermostat may be incorporated into the
process.
Similarly, the occupied set points (or at least the lowest cooling set point)
may be
incorporated into the process.
[0080] In one embodiment, interior humidity and exterior humidity
sensors
are optional, and a provision may be made to utilize both or only one type of
humidity sensor. In one exemplary application using only an exterior humidity
sensor, the system 10 utilizes a default, predefined humidity reading as a
reference marker to compare measurements from the exterior humidity sensor.
For example, the system 10 may be configured to assume that the interior
humidity is at a first predefined level under a first set of criteria, e.g., a
reading
from the exterior humidity sensor after running the control scheme 100 for at
least a first time period. Another example, may assume that the interior
humidity
is simply at a predefined level. During operation, the system 10 could compare
the assumed humidity value and the measured value until the exterior humidity
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levels exceed 50% relative humidity, at which point the assumed interior
humidity level would stay at 50%, while the actual relative humidity value for
the
exterior humidity levels would be reflected in the system's 10 calculations.
In
one embodiment, the control scheme 100 may stop if the exterior humidity is
above and/or below a predetermined threshold.
[0081] On thermostat embodiments having a switch to select "cool" (only)
or
"heat" (only), there could be a calculated or user-defined ntcsp (see above).
The
calculated ntcsp could use a user defined temperature offset value which may
be
set via programming the thermostat, or may simply use a default value of a
certain
number of degrees less than the lowest cooling set point on the thermostat.
[0082] FIG. 8A shows a block diagram illustrating an exemplary process
400
for controlling the system 10 based upon a calculated anticipated heat energy
transfer metric. Although FIG. 8A may show a specific order of method steps,
the
order of the steps may differ from what is depicted. Unless specifically
stated, the
methods or steps shown in the flowcharts and described in the accompanying
text
are not constrained to a particular order or sequence. In various embodiments,
some of the steps thereof can occur or be performed concurrently or with
partial
concurrence and not all the steps have to be performed in a given
implementation
depending on the requirements of such implementation. Further, the order or
sequence of any process or method steps may be varied or re-sequenced
according
to alternative embodiments. Other substitutions, modifications, changes, and
omissions may be made in the design, operating conditions and arrangement of
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the exemplary embodiments without departing from the scope of the present
disclosure. All such variations are within the scope of the disclosure.
[0083] At step 412 of the process 400, operating of the system 10 may
include
determining a fixed or minimum outdoor air damper position (FMOADP) using
any one of the following equations:
FMOADP= (RAT - MAT) / (RAT - ODAT)
FMOADP= (MAT - RAT) / (ODAT - RAT)
FMOADP = 1 ¨ ((ODAT - MAT) / (ODAT - RAT))
FMOADP = 1¨ ((MAT ¨ ODAT) / (RAT ¨ ODAT))
where
ODAT represents an outdoor air temperature which can be measured using sensor
31, and
RAT represents a return air temperature, which may be measured from sensor 33,
and
MAT represents a mixed air temperature measured from sensor 39.
[0084] For example, if MAT = 55 F, ODAT = 50 F, and RAT = 70 F, then
FMOADP = (70 F ¨55 F) / (70 F ¨ 50 F), which equals a value of 0.75,
meaning that the outdoor air damper 22 is open 75%, where a '1' value is
defined
as completely open and a '0' value is defined as closed.
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[0085] In various embodiments, a discharge air temperature may be
utilized to
determine FMOADP instead of the MAT variable as one skilled in the art will
recognize upon a careful reading of the teachings herein.
[0086] In various embodiments, the FMOADP could be calculated and
trended (based on time or time in different states/values) for use later. For
example, specific calculations of FMOADP at noon and at 2pm, may be trended
to determine position at 1pm or 3pm. In one embodiment, the FMOADP may be
used in calculating the energy (or heat) added to, or removed from the
structure
via the "fresh air intake", or intake of outdoor air.
[0087] Additionally, heat transfer due to FMOADP and ventilation status
(VS) may be calculated when considering temperatures. In various embodiments,
depending on operating parameters of the system 10, historical heat transfer
rates
due to the intake of outdoor air may be used to predict the heat transfer
going
forward. For example, the heat transferred during the last same day of the
previous week could be used to determine another day's anticipated value, or
may
begin as the average heat transferred the last same day of the week and month
for
the first year, and/or then in later years, the average heat transferred on
the same
day of the week and month in preceding years. In one exemplary application, a
church might have nominal load demand on every day of the week except
Sunday. Basing the next day's predicted cooling potential based on the last
Sunday's actual load demand, or on the same Sunday from the previous year's
load demand may be beneficial instead of using the prior day's load demand.
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[0088] In one embodiment, if multiple systems with different maximum
volumetric flow rates are used, then a "VS constant" can be multiplied by each
individual climate control equipment's value for VS, such that the value of VS
for
each individual climate control equipment shall be in proportion to its
volumetric
flow rate in relation to all other climate control equipment. For example: If
two
pieces of climate control equipment are used, one capable of moving 4,000 CFM
(unit #1), and another capable of moving 8,000 CFM (unit #2), then the VS
constant for unit #1 would be 0.5, and the VS constant for unit #2 would be 1.
[0089] At step 414 of the process 400, a numeric value for the variable
representing the heat transfer due to bringing outdoor air into and expelling
indoor
air out of a structure may be determined, iteratively at predetermined
sampling
intervals, e.g., at a time interval t, as follows, while understandably
similar
calculations could be made by replacing the temperature variables for enthalpy
variables and modifying the equations slightly:
FMOADP heat = VS * (ODAT - RAT) * FMOADP
where
FMOADP heat = the heat transfer metric due to bringing outdoor air into and
expelling indoor air out of a structure,
ODAT represents an outdoor air temperature,
FMOADP represents a fixed or minimum outdoor air damper position,
RAT represents a return air temperature or exhaust air temperature, and
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VS represents an operating status of the ventilation system 16 (e.g., 0 = off,
1 =
on 100%, 0.5= 50% output, etc.).
[0090] For example: If ODAT = 60 F, FMOADP = 0.1 (i.e., 10%), RAT = 70
F, VS = 1 (on), then FMOADP heat = 1 * (60 F - 70 F) * 0.1, which reduces to
¨ 1 F.
[0091] At step 416, the system 10 may determine FMOADP Heat sum.
FMOADP Heat sum represents a heat transferred (based on the FMOADP heat
metric), resulting from venting outdoor air into, and indoor air out of, the
building
structure for the entire period being measured (e.g., a whole day, 22 hours,
one
week, etc.). In exemplary applications having multiple climate control
equipment
(i.e. air conditioners, exhaust fans, etc.) within a building structure or
zone, the
FMOADP Heat sum can be summed with the FMOADP Heat sum of the other
networked and/or controlled systems, however, the FMOADP heat calculation of
each individual unit would likely need to have a "VS constant" (as described
above) applied to the FMOADP heat value for each individual unit.
FMOADP Heat sum could be calculated as follows:
FMOADP_Heat_sum Ezj=i Xi ti
where
x represents FMOADP heat,
ti represents a predetermined time interval,
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FMOADP heat represents the heat transfer metric (as defined above) due to
bringing outdoor air into and expelling indoor air out of a structure,
i represents an interval,
z represents a number of preset timed intervals during the period (the period
usually being 22 or 24 hours, but could be 6 hours, etc.) wherein each measure
of
FMOADP heat is taken.
[0092] Similarly, FMOADP Heat sum may be calculated using an integral
calculation:
FMOADP Heat sum ¨ fa FMOADP_heat(t) dt
where
a = the beginning of the time period,
b = the end of the time period, and
t = time.
[0093] At step 418 of the process 400, the system 10 may calculate a
heat
transfer metric (HeatTransferred) due to a HVAC unit's operation of mechanical
heating or cooling (e.g. using gas burners, refrigerant based systems, etc.),
iteratively at predetermined sampling intervals, e.g., at a time interval t,
as
follows, while understandably similar calculations could be made by replacing
the
temperature variables for enthalpy variables and modifying the equations
slightly.
The operation of the mechanical cooling or mechanical heating is preferably
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considered to ascertain the heat transfer into or out of a structure during a
period
of time. In a situation where the volumetric air flow (in cubic feet per
minute
(CFM)) is known, the energy transferred may be fairly easily calculated,
however,
in a situation where the CFM is unknown, and for the purposes of the
disclosure,
the total heat transfer, as a result of a HVAC unit's mechanical operation,
(e.g.,
use of gas burners for heating, refrigeration based cooling systems,
compressors,
etc.) may require the formation of a new metric.
[0094] The
variable `HeatTransferred' represents a heat transfer metric, due to
a HVAC units operation of mechanical heating and/or cooling, but not including
the heat energy transferred due to bringing outdoor air into, and expelling
indoor
air out of a structure, and may be determined by:
HeatTransferred = VS * (SAT - RAT) - FMOADP heat
where
SAT represents a temperature of the supply air from sensor 38,
RAT represents a temperature of the return air which may be obtained from
sensor 33, and
FMOADP heat = the heat transfer metric (as defined above) due to bringing
outdoor air into, and expelling indoor air out of a structure.
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[0095] For example, if SAT = 100 F, RAT = 70 F, VS = 1 (on), and
FMOADP heat = - 1 F, then: HeatTransferred = 1 * (100 F - 70 F) ¨ (-1 F)
which reduces to HeatTransferred = 31 F.
[0096] FIG. 8B shows an alternative process 400' for implementation in
the
system 10 without sensors 31, 33, 38, and 39 being used for calculating
HeadTransferred at step 418'. In one embodiment, HeatTransferred may be
calculated as follows: HeatTransferred = VS * (Ho ¨ Co), wherein
FMODAP heat is equal to zero (step 414'); and Ho represents heating load
output
and Co represents cooling load output as described hereinabove with reference
to
FIG. 3. FMOADP Heat sum is then calculated at step 416' based upon a
FMOADP heat having a 0 value. As one skilled in the art may understand after
considering the teachings disclosed herein that the units of measurement will
change from degree-minutes to minutes. Such embodiments using this alternative
calculation for HeatTransferred shall also affect the processes, equations,
and
conclusions given in some parts this disclosure, however, it should be noted
that
alternative calculations for HeatTransferred and/or Total heat tansferred
(described below) to operate the system 10 at step 460', when used in
conjunction
with the teachings herein disclosed, could effectively be used as understood
by
those skilled in the art upon a careful reading of the teachings herein.
[0097] Step 420 of the process 400 may include determining the heat
transferred due to the mechanical operations, e.g., gas burners, refrigeration
circuits, etc., but excluding the heat energy transferred due to introducing
outdoor
air into, and expelling indoor air out of the structure. This value may be
calculated
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for a predefined period (i.e. a whole day, 22 hours, a week, etc.), wherein
the
calculation is computed once per interval, and then summed, which may then be
represented by the variable: HeatTransferred sum, which may then be calculated
by:
HeatTransfered_sum Ef=1X1 ti
where
i represents an interval or iteration,
ti represents a predetermined time interval
x represents HeatTransferred, and
z represents a number of preset timed intervals during the period (the period
usually being 22 or 24 hours, but could be 6 hours, etc.) wherein each measure
of
HeatTransferred is taken.
[0098] Alternatively, the HeatTransferred sum could be calculated by:
HeatTransferred sum ¨ b HeatTransferred(t) dt
where
a = the beginning of the time period,
b = the end of the time period, and
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t = time
[0099] In one embodiment, of a structure having a plurality of networked
systems, a separate HeatTransferred sum may be determined for each system and
then may be added together.
[0100] Subsequent to calculating the HeatTransferred sum, the process
400
calculates a Total heat transferred (at step 422) by adding HeatTransferred
sum
with FMOADP Heat sum. Total heat transfered then represents a total F-
minutes of heat transferred into the structure by the HVAC unit during the
time
period (i.e. 22 hours, 24 hours, one week, etc.). For example: if
HeatTransfered sum = 500 F-minutes, FMOADP Heat sum = -400 F-minutes,
then Total heat transfered = 500 F-minutes + (-400 F-minutes) = 100 F-
minutes.
[0101] In the above example, the heat energy was transferred into the
structure (the heating system 12 was operated to introduce heat into the
structure).
If the value would have been negative, then heat energy would have been
transferred out of the structure by the system 10 via one or more of the
components, e.g., the ventilation system 16.
[0102] Once the total heat transferred has been determined, it can be
used to
determine the slope M 440, which in turn can be used to predict the next
period's
heat transfer (NTotal heat transferred 450). To determine M, the
total heat transferred for at least two historic time periods can be
calculated (i.e.
two days, two 6 hour periods, two weeks, or whatever period is determined to
be
most effective in predicting the next period's heat transfer desired). The
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total heat transferred for the first historic time period could be
total heat transferred I, and for the second historic time period could be
called
total heat transferred 2, and so on, as determined in step 424.
[0103] If the volumetric flow rate of the air, based on VS is known,
then one
skilled in the art may calculate the heat transfer in British Thermal Units
(BTU) of
HeatTransferred, FMOADP Heat sum, and Total heat transferred. Integrating
the calculations into the system to provide for automated calculations of
HeatTransferred sum versus FMOADP Heat sum would prove beneficial in
terms of analyzing deficiencies in equipment configurations/damper settings
(i.e.
if a structure was drawing in excessive amounts of outdoor air, etc.).
[0104] The process 400 further includes determining an average outdoor
air
temperature for a period (AODAT) at steps 430 and 432.
[0105] AODAT could be calculated by:
v,z
AODAT t =1 Xi) Z
where
AODAT represents an average outdoor air temperature for a period,
z represents a number of preset timed intervals during the period (the period
is
usually 22 or 24 hours, but could be 6 hours, etc.),
x represents an outdoor air temperature, and
i represents a predetermined time interval
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[0106] Alternatively, AODAT may be calculated by:
b
AODAT = (fa f(x) dx) / (b-a)
where
f(x) represents a function of AODAT measurements over the time period a to b,
a represents a beginning of the time period, and
b represents an end of the time period.
[0107] At steps 434 and 436 of the process 400, iterations of the
average
space temperature inside the structure, e.g., ASTI, AST2, etc., may be
calculated
by:
tv,z
AST ""s" (>1x) /z
where
AST represents the average space temperature for a period,
z represents a number of preset timed intervals during the period (the period
usually being 22 or 24 hours, but could be 6 hours, etc.) wherein each measure
of
the space temperature set point is taken,
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x represents ST, which is a space temperature measurement made by sensor 35,
and
i represents a predetermined time interval.
[0108] Alternatively, the AST could be calculated by:
b
AST = (fa f(x) dx) I (b-a)
where
AST represents an average space temperature for a period,
f(x) represents a function of AST measurements over the time period a to b,
a represents a beginning of the time period,
b represents an end of the time period, and
x represents ST, which is a space temperature measurement made by sensor 35.
[0109] Considering that it's reasonable to assume that a structure or
zone with
no internal heat sources, e.g., lights, people, computers, etc., that has zero
influence from radiant heat, e.g., from the sun, that is not affected by the
differential temperatures of materials inside or of the building structure,
e.g. the
concrete floor, etc., that there is no differential temperature between the
inside of
the structure and the earth, and assuming (for purposes of the process 400),
that
the HVAC equipment, e.g., the exhaust fans 37 and the supply air fans 16, do
not
add heat energy to the structure, it's reasonable to assume that the
structure's
Total heat transferred 0, if the ASTSP = AODAT = AST, where
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ASTSP represents the average space temperature set point for a period,
AODAT represents the average outdoor air temperature for a period, and
AST represents the average space temperature for a period.
[0110] Because outdoor air temperatures vary during the course of a
period it
is beneficial to sample certain variables and values throughout the day. As
indicated herein above, Total heat transferred = HeatTransferred sum +
FMOADP Heat sum. As expressed herein above, a 22 hour, 24 hour, period may
be used to define a "day" or "period", however it should be understood that
when
determining a slope of a graph, it may be beneficial to use different time
periods.
For example: While it is understood that HeatTransferred sum and
FMOADP Heat sum can use identical time periods for determining
Total heat transfered, and any equations that combine HeatTransferred sum,
FMOADP Heat sum, Total heat transferred, AODAT, and AST will likely
require that identical time periods be used, it should also be understood that
in the
application of determining the slope ((AODAT2 ¨ AST2) ¨ (AODAT1 ¨ ASTI)) /
(Total heat transferred2 ¨ Total heat transferred') that smaller time periods
may
be more suitable, e.g., a 6 hour time period., although the disclosure herein
contemplates that various time periods may be utilized consistent with the
teachings herein.
[0111] Subsequent to determining AODAT and AST, the process 400
calculates a slope 'M' based upon two or more iterations of AODAT, AST, and
the Total heat transferred calculations at step 440.
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[0112] The slope `IVI' is the slope of the graph relating Total heat
transferred
to (AODAT ¨ AST), and may be calculated by:
M = ((AODAT2 ¨ AST2) ¨ (AODAT1 ¨ ASTI)) / (Total heat transferred2 ¨
Total heat transferred')
where
AST' represents an average space temperature for the 1st period,
AST2 represents an average space temperature for the 2nd period,
AODAT1 represents an average outdoor air temperature for the 1st period,
AODAT2 represents an average outdoor air temperature for the 2nd period, and
Total heat transferred' and Total heat transferred2 being defined hereinabove
and having been calculated in step 424.
[0113] At step 442 of the process 400, the system 10 may apply various
statistical conditioning or averaging of the slope M to maintain consistency.
Because the slope of the graph relates Total heat transferred to (AODAT ¨ AST)
it should remain fairly constant, since the slope is directly related to the R-
value
of the structure's envelope (as well as other minor factors- in some cases).
In one
embodiment, a time period of one week may be used to maintain
consistency/accuracy by averaging M over that time period. M could be averaged
by:
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rvIz
AM ""s" i=i Xi) Z
where
AM represents an average of M over time,
x represents M, as defined above,
z represents a number of preset periods during the time span in which M is
averaged (the time span in which M is averaged could be one week, two weeks,
etc.), and
i represents a predetermined interval where each M is calculated.
[0114] Under this summation equation, the difference between the
beginning
of the time span and the end of the time span may be defined as a week (i.e.,
7
days), while M, could be recalculated every six hours, or once a day, for
example.
As noted above, if slope M is to be calculated every six hours, then the
subsequent periods within the calculations for AODAT, AST, and
Total heat transferred would preferentially use six-hour time periods, where
appropriate. AM may be calculated using the following equation:
AM = (fa f (x) dx) I (b-a)
where
Where f(x) represents a function of m slope calculations over the time span a
to b,
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a represents a beginning of the time span, and
b represents an end of the time span.
[0115] With reference to FIG. 9, B is a y-intercept used on FIG. 9 that
illustrates a relationship of Total heat transferred to (AODAT ¨ AST). At step
444 of process 400, B may be calculated for a time period, i, by the equation:
B = (AODATi-ASTi) ¨ (Total heat transferredi * Mi)
where
AODAT represents average outdoor air temperature, as defined previously,
AST represents average space temperature, as defined previously,
i represents a predetermined interval where each B is calculated, and
M represents a slope of the graph comparing Total heat transferred to (AODAT-
AST).
[0116] Similar to calculating AM, an average B could be calculated over
a
time span. Average B, represented as AB, may be calculated in step 446 of the
process 400 using:
tv,z
AB '"'" (4i=1 Xi) Z
where
AB represents an average of B over time,
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x represents B, as defined above,
z represents a number of preset periods during the time span in which B is
averaged (the time span in which B is averaged could be one week, two weeks,
etc.), and
i represents a predetermined interval where each B is calculated.
[0117] In one embodiment, AB could be calculated by one or more
variations
of:
b J-
AB = (fa f(x) dx) / (b-a)
where
f(x) represents a function of y-intercept (B) calculations over a time span a
to b,
a represents a beginning of the time span, and
b represents an end of the time span.
[0118] Subsequent to determining the AM slope and AB (the average y-
intercept of figure 9), the process continues to step 450 wherein a
NTotal heat transferred value is determined. In various embodiments, weather
predictions may be utilized in conjunction with the AM slope to determine the
next period's (e.g., day), anticipated/projected Total heat transferred, i.e.,
NTotal heat transferred. In some embodiments, the AM slope permits
incorporating set point data into the equation for determining the next day's
anticipated/projected Total heat transferred. For example: a church may not
have
need for cooling any day except Sunday. Such as this is the case, it's likely
that
the parishioners would set the thermostat to a very high temperature set point
for
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all days except for Sunday. Assuming that the space temperature will need to
reach the space temperature set point, we can use the slope to determine the
NTotal heat transferred.
[0119] A predicted space temperature may be determined by taking all
relevant data regarding scheduled set point information (which correlates
space
temperature set points with times), default space temperature set points,
historical
user set point data, etc. Although the usual day/night temperature swing which
occurs will lead to many embodiments simply having a daily time period, one
skilled in the art may envision an embodiment configured, such that energy may
be stored, in a region of the world like Antarctica, wherein the period may be
generally extended for the entire warm season, which would be the summer. Such
as thee normal one- day embodiment will be the case, the calculation of ASTSP,
is provided as an exemplary embodiment for an exemplary application, normally
being about one day, however it should be understood by those skilled in the
art
that the one day examples given herein are not intended to limit the scope of
the
disclosure. ASTSP, generally, may include the average space temperature set
points for the next period and may be calculated by:
tv,z
ASTSP ""s" u4=ixi) Z
where
ASTSP represents an average space temperature set point for a period,
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z represents a number of preset timed intervals during the period (usually 22
or 24
hours, but could be 6 hours, etc.) wherein each measure of the space
temperature
set point is taken,
x represents the space temperature set point, and
i represents a predetermined time interval.
[0120] Alternatively, the ASTSP could be calculated by:
b
ASTSP = (fa f(x) dx) I (b-a)
where
f(x) is a function of space temperature set points from a to b,
a represents a beginning of the time period,
b represents an end of the time period.
[0121] PAODAT is the predicted average outdoor air temperature. In one
embodiment, this value may be determined from an average of the predicted
outdoor air temperatures (PODAT) over a future time period. In one embodiment,
PAODAT may be based upon forecasted predictions from subscription or
governmental sources, e.g., weather forecasting information. In one
embodiment,
PAODAT may simply be based upon a rolling average temperature period over a
predefined number of time periods, e.g., days. As there are many ways to
determine PAODAT, which one skilled in the art will recognize upon a careful
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reading of the disclosure herein may understand there are many ways to
determine
PAODAT.
[0122] PAST is the predicted average space temperature for the following
time period (i.e. the next day or next 12 hours, etc.). There are many ways to
calculate PAST. In one embodiment of the invention, PAST may be equal to the
AST of a chosen historical time period, such as the day before, or the same
day of
the previous week. The limitation of setting PAST equal to a previous time
period's AST is that this method does not take into account the future set
point
temperature schedule.
[0123] In one embodiment, PAST is a function of predicted outdoor air
temperature (PODAT) and the future set point temperature. Using historical
data,
the space temperature could be plotted versus the outdoor air temperature
under
different set point temperature conditions. From this data, functions to
represent
ST versus ODAT, under different set point conditions, could be determined. Any
data that derives a non-functional result would be negated or accounted for
differently. Next, the PODAT could be substituted for the ODAT in the
functions.
In one embodiment, PAST can be calculated as follows:
hi hi
ai (x))1dx
PAST ¨ ( 1 J )(T1* + T2* jai (f(x))2dx
T1+T2+===+Tn b1-a1 b2-a2
Tn* rbn
jan (f(x))ndx)
bn- an
where
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x represents a predicted outdoor air temperature (POADT),
(f(x))1, (f(x))2...(f(x))n represent a function of space temperature based on
POADT, wherein the function may be different for every set point temperature,
Ti, T2... Tn represent time intervals in which the set point temperature
remains a
constant (i.e. for the first 4 hours (T1=4) of the day the set point is at 70
F, for the
next 6 hours (T2=6) the set point is 72 F, etc.),
n represents a total number of set point intervals for the time period (i.e.
day, 12
hours, etc.),
bl, b2, bn represent an ending POADT of the interval, and
al, a2, an represent a beginning POADT of the interval.
[0124] In one embodiment, PAST may be calculated based upon Newton's
"Law of Cooling (Warming)." Newton's "Law of Cooling" states that the rate at
which the temperature changes of one body is proportional to the difference in
the
temperatures of the body and the environment. In this application, the
environment includes the outside as well as the effects of internal heat
sources,
such as computers, lights, etc.. The differential equation for Newton's "Law
of
Cooling" is as follows:
d(ST)
= k(ODAT1¨ ST)
dt
Accounting for internal heat sources:
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d(ST)
= k(YODAT1¨ ST)
dt
where
d(ST)
dt _______ represents a rate of change of temperature with respect to time,
k represents a proportionality constant,
t represents time,
YODAT1 represents the outdoor air temperature minus the value of the above B
or AB at the start of the time interval, and
ST represents a space temperature at any time t.
[0125] We will begin by assuming that the building is warming up and
YODAT1 > ST1 . This differential equation is solved by separating the
variables:
d(ST)
= kdt
(YODAT1 ¨ ST)
and then integrating
f d(ST) = fkdt
(YODAT1 ¨ ST)
ln IYODAT1 ¨ STI= kt + c
where
c represents a constant obtained in any antiderivative.
[0126] Solve for ST via exponentials on both sides of the equation:
YODAT1 ¨ ST =
YODAT1 ¨ ST = (e'd )(ec )
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[0127] Since c is a constant, ec is also a constant, hereinafter
referred to as: C
and the equation becomes:
YODAT1 ¨ ST = Cekt .
[0128] By solving for ST, the equation may be represented as:
ST = YODAT1 ¨ .
[0129] In predicting how the structure responds to temperature changes,
both
k and C can be determined. Two data points are used to determine how the
structure naturally warms. Using historical data (t1, ST1) and (t2, 5T2) where
the
numbers 1 and 2 indicate first and second data points while YODAT1 remains
constant.
[0130] These data points are inserted into the solved differential
equation to
obtain two equations with the same two unknowns, k and C.
ST1= YODAT1¨ Cek(t1)
ST2 = YODAT1¨ Cek(r2)
[0131] To simply solve for k and C, we can assume that tl = 0.
ST1= YODAT1¨ Ce" )
ST1= YODAT1¨ C
C =YODAT1¨ ST1
and C is simply the difference in the initial indoor and outdoor temperatures
minus the value of B or AB.
[0132] Substituting this value of C into the same equation with the
second
data point, we can solve for k.
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ST2 = YODAT1¨ (YODAT1¨ ST1)ek(t2)
ST2 ¨ YODAT1
= ek(t2)
¨(YODAT1¨ ST1)
( ST2 ¨ YODAT1 in = k(t2)
¨(YODAT1¨ ST1))
(
ST2 ¨ YODAT1
in
¨(YODAT1¨ STO
k ¨ ______________________
(t2)
[0133] If ti # 0, then we can transform the equations removing the
exponentials to solve for k and C. First, substitute the two data points to
obtain
two equations.
YODAT1¨ ST1= Cek(t1)
YODAT1¨ ST2 = Cek(t2)
[0134] We now take the natural logarithm of both sides.
ln(YODAT1¨ STO =ln(Cek")
in(YODAT1¨ ST1) = ln(C)+1n(ek")
in(YODAT1¨ ST1)= in(C)+k(ti)
[0135] We use the same process with the second equation to obtain:
ln(YODAT1¨ ST2) = in(C) + k(t2) .
[0136] Using the method of elimination, we first solve for k. One
equation is
subtracted from the other and the common term in(C) is eliminated yielding:
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ln(YODAT1¨ ST2)-1n(YODAT1¨ ST1) = k(t2)¨ k(t1)
ln(YODAT1¨ ST2)-1n(YODAT1¨ ST1) = k(t2¨ ti)
k =ln(YODAT1¨ ST2)-1n(YODAT1¨ ST1)
(t2¨ti)
in (YODAT1¨ ST2
k
YODAT1¨ ST1
¨
(t2¨ti)
[0137] Knowing the value of k, we can substitute this value and solve
for C:
ln(YODAT1¨ ST1) = ln(C)+ kti
ln(YODAT1¨ ST1) in(C)
ln(YODAT1¨ ST2)-1n(YODAT1¨ ST1) (t1)
=
(t2 ¨ tl)
in(C) ln(YODAT1¨ ST1)
ln(YODAT1¨ ST2)¨ ln(YODAT1¨ ST1) (t1)
=
(t2¨ti)
ln(YODAT 1 ST1) ln(YOR4TI-ST 2)-1n(YODAT 1- ST 1) (t1)
C e (t 2 -t1)
In( YOR4T1- ST 2)
YO(Dt 2,4T tli-)ST 1 (ti)
ln(YOR4 T1 ST1)
C e
[0138] The value of k is a value dependent on the thermal
characteristics of
the structure. The value C would be calculated with different values of YODAT1
and ST1.
[0139] When the outside temperature minus the above B or AB is less than
the inside temperature (YODAT2 < ST1, where YODAT2 is the outdoor air
temperature minus either B or AB, the structure will naturally cool. Again, we
start with Newton's "Law of Cooling":
d(ST)
= k(ST ¨YODAT2) .
dt
where
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YODAT2 represents the outdoor air temperature minus the value of above B or
AB at the start of the time interval.
[0140] Separate the variables and integrate as before:
d(ST)
= fkdt
ST ¨YODAT2
ln IST ¨ YODA T2I = kt +c
ST ¨YODAT2=ekt c
ST ¨YODAT2=Ce
ST =Ce +YODAT2
[0141] Two data points are used to determine how the structure naturally
cools. Using historical data (t1, ST1) and (t2, ST2) where the numbers 1 and 2
are
the labels for the first and second data points while YODAT2 remains constant.
These data points are inserted into the above solved differential equation to
obtain
two equations with the same two unknowns, k and C.
ST1=Cek(t1) +YODAT2
ST2=Cek" +YODAT2
[0142] To simply solve for k and C, we can assume that tl = 0.
ST1= Ce" ) +YODAT2
ST1= C +YODAT2
C = ST1¨YODAT2
Where C is the difference in the initial indoor and outdoor temperatures minus
the
y-intercept (B or AB - as defined herein above) of FIG. 9 for the start of the
period of structural cooling.
[0143] Substituting this value of C into the same equation with the
second
data point, we can solve for k.
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ST2 = (ST1¨YODAT2)ek(t2) +YODAT2
ST2 ¨YODAT2 = ek(t2)
ST1¨YODAT2
ln (ST2 ¨YODAT2 = k(t2)
ST1¨YODAT2
in ( ST2 ¨YODAT2
k
ST1¨YODAT2
=
(t2)
[0144] If tl # 0, then we can transform the equations removing the
exponentials to solve for k and C as before.
ST1¨YODAT2=Cek(t1)
ST2 ¨YODAT2 = Cek(t2)
[0145] We may now take the natural logarithm of both sides.
in (ST1 ¨ YODAT2)= ln(Cek" )
ln(ST1¨ YODAT2)= ln(C)+ ln(ek")
ln(ST1¨ YODAT2)= ln(C)+ k(t1)
[0146] We use the same process with the second equation to obtain
ln(ST2 ¨ YODAT 2) = in(C) + k(t2).
[0147] Using the method of elimination, we first solve for k. One
equation is
subtracted from the other and the common term in(C) is eliminated yielding
ln(ST2 ¨ YODA T2)¨ ln(ST1¨ YODAT2)=k(t2)¨ k(t1)
ln(ST2 ¨ YODAT2)¨ ln(ST1¨ YODAT2)= k(t2 ¨ ti)
k = ln(ST2 ¨ YODAT2)¨ ln(ST1¨ YODAT2)
(t2¨ tl)
in ( ST2 ¨YODAT2
k
ST1¨YODAT2
=
(t2 ¨ tl)
[0148] Knowing the value of k, we can substitute this value and solve
for C.
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ln(ST1¨ YODAT2) = ln(C)+ ktl
ln(ST1¨ YODAT2) ln(C)+ ln(ST2 ¨ YODAT2)¨ ln(ST1¨ YODAT2) (tl)
=
(t2 ¨ tl)
ln(C) ln(ST1¨ YODAT2)
ln(ST2 ¨ YODAT2)¨ ln(ST1¨ YODAT2) (tl)
=
(t2¨tl)
ln(ST2-YODAT2)-1n(ST1-Y0DilT2)(t1)
ln(ST1-YODAT 2 )
C e-
(t2-t1)
lni ST 2-YORzIT 2)
1n(ST1-YODAT2) ST(1 t 2Y tf;AT 2 (t1)
C e-
V:1149] We will use as an example three intervals to see how PAST can be
calculated: naturally warming, maintaining set point (STSP), and naturally
cooling. Space temperature (ST) is a function of time (t).
YODAT1¨Cekt <t2
ST(t) = STSP t2t <t3
Cekt +YODAT2 t3t t4
where
STSP represents space temperature set point.
[0150] Knowing the value of k for warming and cooling, we can predict
PAST. In one instance as FIGS. 10A and 10B illustrate, there may be a period
of
natural warming, a steady period (temperature at STSP), and a period of
natural
cooling. Finding the average (PAST) may be done the following way:
PAST = 1 ft4
ST (t)dt
t4¨tl ti
1 st2 t3 t 4
(YODAT1¨Cekt)dt + (STSP)dt + (Ce +YODAT2)dt
t4¨ tl _ ti t2 t3
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[0151] Using the value of k from the historical data and the difference
in
indoor and outdoor temperatures (plus the value of B or AB), we can predict
when the ST of the structure will be at STSP as the building warms using:
STSP =YODAT1¨Cekt . Solve for t. This is t2. This defines an interval of
natural
structural warming [ti, t2].
[0152] While the structure is at STSP and the cooling system cycles,
this will
define the next interval [t2, t3] as the value of t3 can be obtained from
predicted
weather (the time at which YODAT2 = STSP) after the heat of the day (YODAT2
being the outdoor air temperature minus the value of above B or AB).) The
interval of time through which the structure naturally cools will define the
third
interval [t3, t4] . t4 would be the time at which the outdoor ambient
conditions are
desirable to condition the structure. Again, t4 can be obtained from predicted
hourly weather (hourly, minutely, etc.) and may be set, in one embodiment, to
a
time at which it is desirable to condition the space. In another embodiment,
t4
may be a time at which YODAT = STSP, etc.
The expansion of each interval in the calculation of PAST is shown below.
t2 t2 t2
(YODAT1¨ Ceict)dt = (YODAT1)dt ¨ (Ceict )dt
ti tl
t2 C
_
= (YODAT1)titl _(ekt)1t2 k ti
C ) )
= (YODAT1)(t2¨t1)--(ek(t2 ¨ ek(t1 )
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t,
(STSP)dt = (ST t2 SP)13
= (STSP)(t3)¨(STSP)(t2)
= STSP(t3¨t2)
J t4 t4
k = (Ceict)dt + (YODAT2)dt
, (Cet +YODAT2)dt t3t4 t3
C t4 it4
+(YODAT2)tit3
t3
C k(t4) k(t3
-k (e ¨e ))+ (YODAT 2)(t4 ¨t3)
When considering the teachings herein above, one skilled in the art could
determine PAST using the conditional processes described herein above for
various scenarios.
[0153] The predicted average space temperature (PAST) for the next
period,
e.g. the next day, could be extracted from a user-supplied temperature
schedule,
default temperature schedule, historical user entry data, a combination of
these,
the equations given herein above, etc. The NTotal heat Transferred value is
that
which the system 10 would try to achieve in order to condition the structure
in
preparation of the next day, however, upper and lower limits may inhibit the
value
being too high or low, and/or upper and lower limits may inhibit the
operations to
achieve NTotal heat Transferred in order to keep the space temperature within
reasonable limits. The appropriate limits on the operations of the systems may
be
understood by one skilled in the art, when considering the teachings herein
disclosed.
[0154] In one embodiment, NTotal heat Transferred may be calculated by:
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NTotal heat Transferred = ((PAODAT ¨ PAST) ¨ AB) / AM
where
AM represents an average M, as previously defined,
AB represents an average B, as previously defined,
PAODAT represents a predicted average outdoor air temperature, and
PAST represents a predicted average space temperature over a period.
[0155] If volumetric flow rates of the system 10 are known in real units
of
measure (i.e. CFM),) then industry standard calculations could be made to
determine the real value, in terms of real units of measure (i.e. BTU), of
heat
transfer. Also an amount of energy produced inside the structure due to
people,
computers, lights, etc., which is referred to as IHEPIS (the value of the x-
intercept
of the graph in FIG. 9 multiplied by -1) could be calculated using real units
of
measure (e.g., BTU's). Also, if the surface area of the structure's envelope
is
known, then the R-value of the structure's envelope could be computed using
the
slope of (AODAT ¨ AST) / Total heat transferrred, although if for instance a
window was left open, the resulting heat transfer would affect the calculated
R-
value.
[0156] Additionally, k could be used to calculate the effective thermal
capacity of the structure.
[0157] Subsequent to determining NTotal heat Transferred, the system 10
may operate various components to effect ventilation, cooling, and/or heating
at
step 460 based upon the calculated NTotal heat Transferred value. In a
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simplified example, the following table shows the AODAT, AST, and
total heat transferred over three days (i.e. three time periods). Please note
that
this example may not be typical, but rather is given for illustrative
purposes.
Day Monday Tuesday Wednesday
AODAT 70 F 90 F 50 F
AST 68 F 68 F 68 F
Total heat transferred -100 F-min -600 F-min 200 F-min
In this example, M1 is the slope for the graph comparing Total heat
transferred
to (AODAT-AST) from Monday to Tuesday, and M2 is the slope from Tuesday
to Wednesday. M1 and M2 may be calculated as:
M1= ((70-68) - (90 - 68))/((-100)-(-600)) = -1/25
M2= ((90 - 68) - (50 - 68))/((-600)-200) = -1/20
[0158] Therefore, the average slope, AM = ((-1/25) + (-1/20))/2 = -
0.045.
Next, the y-intercept (B1) from Monday to Tuesday, and B2 from Tuesday to
Wednesday would be calculated as follows:
B1 = (70 - 68) ¨ (-100)*(-1/25) = -2 F
B2 = (50 - 68) ¨ (200)*(-1/20) = -8 F
[0159] Therefore, the average B, AB = ((-2) + (-8))/2 = -5 F.
If PAODAT for Thursday was calculated as 75 F, and PAST for Thursday was
calculated as 68 F, NTotal heat transferred could be calculated for this
example
as:
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NTotal heat transferred = ((75-68) ¨ (-5)) / (-0.045) = -267 F-min.
[0160] This means that the system would cool the structure on Thursday,
transferring -267 F-min of heat energy to do so. Therefore, during the time
when
conditions were optimal (usually from 4-6am), the system would bring in cool
outdoor air for a certain amount of time until the total heat transferred
reached
the -267 F-min necessary to meet the day's predicted cooling requirements.
Alternatively, the system could also activate mechanical cooling (i.e.
compressors, refrigeration systems, etc.) to cool the structure. If
NTotal heat transferred were a positive value, then the system could heat the
structure instead of cooling it. If opportune, this could be done during the
heat of
the day by bringing in outdoor air and exhausting indoor air, or
alternatively, with
mechanical heating (i.e. heat pumps, etc.) if conditions warranted such
action.
[0161] The internal heat energy produced inside a structure, due to
things like
lighting, computers, etc. is referred to herein as: "IHEPIS".
[0162] In order to model JEEP'S, at least two periods with varying
Total heat transferred and (AODAT - AST) values may be used in order to
determine a slope M, which has a correlation to the R-value of that
structure's
envelope. IHEPIS may be calculated as the value of -1 multiplied by the x-
intercept of the graph, shown as exemplary FIG. 9 comparing
Total heat transferred to (AODAT - AST). Once the average slope (AM) and
average y-intercept (AB) are known over a time span, IHEPIS could be
calculated
as:
IHEPIS = -1 * (-AB/AM)
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where
AB = average y-intercept B, as defined previously, and
AM = average slope M, as defined previously.
[0163] As one skilled in the art will readily understand upon a careful
reading
of the teachings herein, space temperature set point may be used rather than
space
temperature to operate many of the functions, calculations, and equations
disclosed herein.
[0164] The disclosure has described certain preferred embodiments and
modifications thereto. Further modifications and alterations may occur to
others
upon reading and understanding the specification. Therefore, it is intended
that
the disclosure not be limited to the particular embodiment(s) disclosed for
carrying out this disclosure, but that the disclosure will include all
embodiments
falling within the scope of the appended claims.
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