U.S. patent application number 15/882932 was filed with the patent office on 2018-08-02 for rotary heat regenerator using parallel plate media.
The applicant listed for this patent is Airxchange, Inc.. Invention is credited to Keith Robinson.
Application Number | 20180216897 15/882932 |
Document ID | / |
Family ID | 62977234 |
Filed Date | 2018-08-02 |
United States Patent
Application |
20180216897 |
Kind Code |
A1 |
Robinson; Keith |
August 2, 2018 |
ROTARY HEAT REGENERATOR USING PARALLEL PLATE MEDIA
Abstract
Rotary wheel regenerator are described that use polymer, paper,
metallic or other substrate having a parallel-plate heat transfer
surface or media configuration. The substrate media can be either
non-desiccant-coated "sensible" substrate, or "enthalpic" desiccant
coated substrate. In exemplary embodiments, the spirally wound
substrate media strips are arranged in a parallel plate manner
using an embossed formation periodically to hold the strips in a
parallel plate configuration. The strip layers are arranged so that
every other layer is embossed and every other layer is without
embossments. The embossed standoffs are not required to be aligned
with one another periodically, and a parallel plate arrangement is
achieved.
Inventors: |
Robinson; Keith;
(Marshfield, MA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Airxchange, Inc. |
Rockland |
MA |
US |
|
|
Family ID: |
62977234 |
Appl. No.: |
15/882932 |
Filed: |
January 29, 2018 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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62451288 |
Jan 27, 2017 |
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F28F 21/084 20130101;
F24F 2203/104 20130101; F28D 19/041 20130101; Y02B 30/56 20130101;
F24F 12/001 20130101; F24F 2203/1068 20130101; Y02B 30/563
20130101; F24F 2203/1048 20130101; F28D 19/042 20130101 |
International
Class: |
F28D 19/04 20060101
F28D019/04; F28F 21/08 20060101 F28F021/08; F24F 12/00 20060101
F24F012/00 |
Claims
1. A parallel-plate rotary wheel regenerator comprising: a
plurality of plates that are parallel, wherein the plurality of
plates includes at least one central plate having a plurality of
embossments that touch and physically separate the central plate
from two other adjacent plates.
2. The regenerator of claim 1, wherein the central plate is made of
aluminum.
3. The regenerator of claim 1, wherein one of the adjacent plates
is made of aluminum.
4. The regenerator of claim 2, wherein the aluminum has a thickness
of about 1 to about 5 mils.
5. The regenerator of claim 2, wherein the aluminum comprises 1100
series aluminum alloy.
6. The regenerator of claim 1, wherein the plurality of embossments
comprise a compressed sine wave shape.
7. The regenerator of claim 6, wherein the compressed sign wave
shape includes features joined at an angle in the range of
approximately 5 degrees to approximately 15 degrees.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application is based upon and claims priority to U.S.
provisional patent application 62/451,288 entitled "Rotary Heat
Regenerator using Parallel Plate Aluminum Media," filed 27 Jan.
2017, attorney docket number 056259-0122; the entire contents of
this noted provisional application are incorporated herein by
reference.
BACKGROUND
[0002] Regenerator heat exchange devices or regenerators are known
for effecting the transfer of heat and moisture between two
counter-flowing air streams. Such heat exchange devices are used,
for example, in heating, ventilation and cooling (HVAC) systems to
conserve energy within buildings. One type of regenerator is the
rotary air-to-air heat exchanger, which is typically in the form of
a rotary heat exchange wheel including a matrix of heat exchange
material. When rotated through counter-flowing air streams, the
rotating wheel matrix is heated by the air stream with the higher
temperature and, in turn, heats the lower temperature air stream.
In addition, the rotating wheel may transfer moisture between the
counter-flowing air streams. To promote moisture transfer, the
wheel heat exchange matrix can be made from, or coated with, a
moisture adsorbent desiccant material. Examples of such prior art
rotary regenerator wheels are shown in FIGS. 1-2.
[0003] FIG. 1 represents a cross sectional view of a rotary wheel
heat exchanger assembly within an enclosure having two flow
chambers separated by a divider. The first airflow being directed
through the top chamber and through the top half of the rotary
wheel, the second airflow being directed though the bottom chamber
and through the bottom half of the wheel in a counter direction to
the first airflow. FIG. 2 represents a face on view of the rotary
heat exchange assembly showing 100 the top rotary wheel media
exposed to the first airflow, and the bottom rotary wheel media
exposed to the second airflow in a counter direction to the first
airflow. The wheel is shown sealed circumferentially around it's
perimeter to the wheel casing, and horizontally to the divider
across the diameter of the wheel.
[0004] As the supply airflow and exhaust airflow (fluids) pass
through a typical heat exchange substrate media, two types of fluid
flow can be created, turbulent flow or laminar flow. If the
velocity of the fluid is fast enough, and the passage geometry
large enough, turbulent flow could be created. If the fluid
velocity is low enough, and the passage geometry is small enough,
laminar flow could be created. Turbulence or turbulent flow is a
flow regime in fluid dynamics characterized by chaotic changes in
pressure and flow velocity. It is in contrast to a laminar flow
regime, which occurs when a fluid flows in parallel layers, with no
disruption between those layers.
[0005] Laminar flow means that along the boundary layer or wall of
each layer of heat transfer material, the fluid velocity is
non-turbulent. Therefore, this boundary layer fluid does not mix
with the fluid flowing away from the boundary layer, and heat
transfer from the heat transfer media surface through the fluid is
decreased. Turbulent flow means that the velocity of the fluid
along boundary layer is high enough for the specific passageway
geometry that the boundary layer fluid is mixed with the fluid away
from the boundary layer, and heat transfer from the heat transfer
media surface through the fluid is increased. Most air-to-air
sensible, or enthalpic, rotary wheel regenerators operate in region
of laminar flow as described by the parameter (dimensionless
number) the Reynolds Number (Re), which is typically expressed as
.rho.VD/.mu., where .rho. (rho) is the density, .mu. (mu) is the
absolute viscosity, V is the characteristic velocity of the flow,
and D is the characteristic length for the flow. Typically these
heat exchangers operate at Re numbers of between 200-1000,
indicating laminar flow characteristics. Since laminar flow is not
as effective as transferring heat as turbulent flow, other
parameters of the heat exchanger design become more important, such
as heat transfer media passageway geometry.
[0006] A matrix of a rotary heat exchange wheel can include strips
of thin film material wound about an axis of the wheel so as to
provide a plurality of layers. In such a design, the layers must
have spacing means to create gas passageways extending through the
wheel parallel with the axis. The layers are uniformly spaced apart
so that the gas passageways are of uniform height throughout their
length for greatest efficiency. Transverse elongated embossments
have been provided in a plastic strip to form the gas passageways
between the layers of the regenerator matrix. Numerous closely
spaced transverse embossments are needed to maintain parallelism
between layers if used alone to form the passageways. While such
elongated embossments may maintain parallelism and prevent
circumferential gas leakage, they replace parallel matrix surface
area thereby reducing the heat exchange effectiveness of the
regenerator.
[0007] Typical rotary wheel regenerators--whether made from
plastic, metallic or paper media--are produced using heat transfer
media substrate surfaces formed using a corrugated arrangement
where every other layer is flat, and every other layer is
corrugated. FIG. 3-6 depicts examples of prior art configurations
of heat exchange media used for regenerators. An example of a prior
parallel layer media arrangement having continually corrugated
layers positioned between flat layers creating essentially
triangular shaped passageways (fluted) is shown in FIG. 7.
[0008] For optimum heat and moisture transfer and from a
manufacturing standpoint, it may be easiest to merely provide
dimples in the strip to form the gas passageways between the layers
of the regenerator matrix. While dimples can provide a desirable
high aspect ratio between layers, they unfortunately allow
appreciable circumferential gas leakage in those situations where
there is a high pressure differential between the counter-flowing
air streams, thereby reducing the heat exchange effectiveness of
the regenerator. Additionally, such dimples are not practically
applicable to certain materials such as thin-gauge aluminum or
other metallic materials due to, for example, stress concentrations
and other structural problems.
SUMMARY
[0009] An aspect of the present disclosure includes a
parallel-plate rotary wheel regenerator including: a plurality of
plates that are parallel, wherein the plurality of plates includes
at least one central plate having a plurality of embossments that
touch and physically separate the central plate from two other
adjacent plates.
[0010] The central plate can be made of aluminum;
[0011] One or both of the adjacent plates can be made of
aluminum.
[0012] The aluminum can have a thickness of, e.g., about 1 to about
5 mils.
[0013] The aluminum can include 1100 series aluminum alloy.
[0014] The plurality of embossments can include a compressed sine
wave shape.
[0015] The compressed sign wave shape includes features joined at
an angle in the range of approximately 5 degrees to approximately
15 degrees.
[0016] These, as well as other components, steps, features,
objects, benefits, and advantages, will now become clear from a
review of the following detailed description of illustrative
embodiments, the accompanying drawings, and the claims.
BRIEF DESCRIPTION OF DRAWINGS
[0017] The drawings are of illustrative embodiments. They do not
illustrate all embodiments. Other embodiments may be used in
addition or instead. Details that may be apparent or unnecessary
may be omitted to save space or for more effective illustration.
Some embodiments may be practiced with additional components or
steps and/or without all of the components or steps that are
illustrated. When the same numeral appears in different drawings,
it refers to the same or like components or steps.
[0018] FIG. 1 depicts a side view of an example of a prior art
air-to-air heat exchanger including a rotary heat exchange wheel
having a regenerator matrix.
[0019] FIG. 2 depicts an end elevation view of the prior art heat
exchanger of FIG. 1 as viewed from cutting plane 2-2.
[0020] FIG. 3 depicts a perspective view of an embossed strip and
an un-embossed strip being wound to form the regenerator matrix of
FIG. 1.
[0021] FIG. 4 depicts an enlarged view of a portion of the embossed
strip of the prior art regenerator matrix of FIG. 1.
[0022] FIG. 5 depicts an enlarged plan view of a portion of the
embossed strip of the prior art regenerator matrix of FIG. 1.
[0023] FIG. 6 depicts a sectional view of the embossed strip of
FIG. 5 taken along cutting plane 6-6.
[0024] FIG. 7 depicts an example of a prior art layered media
arrangement having continually corrugated layers positioned between
flat layers creating essentially triangular-shaped fluted
passageways.
[0025] FIG. 8 depicts an example of a parallel-plate arrangement
according to the present disclosure.
[0026] FIGS. 9A-9D depict further example of a parallel-plate
arrangements according to the present disclosure.
DETAILED DESCRIPTION OF ILLUSTRATIVE EMBODIMENTS
[0027] Illustrative embodiments are now described. Other
embodiments may be used in addition or instead. Details that may be
apparent or unnecessary may be omitted to save space or for a more
effective presentation. Some embodiments may be practiced with
additional components or steps and/or without all of the components
or steps that are described.
[0028] The present disclosure provides improvements to and
advantages for parallel-plate heat transfer media geometry utilized
for rotary wheel regenerators, within the fluid velocity ranges
where rotary wheel regenerators are typically applied (laminar
flow), and can provide optimal performance tradeoff between heat
transfer performance and friction loss. Although parallel-plate
heat transfer media regenerators have been designed and produced
using plastic heat transfer media, an aspect of the present
disclosure provides parallel-plate regenerators of aluminum or
other metallic or non-metallic media using periodic embossed
standoffs. This parallel-plate geometry can also provide for media
less prone to clogging due to contaminants in the air, and more
easily cleaned if clogging does occur. Embodiments of the present
disclosure can also provide for manufacturing less media length per
wheel to produce a lighter and more cost effective media
[0029] An aspect of the present disclosure provides a rotary wheel
regenerator using polymer, paper, metallic (e.g., aluminum, etc.)
or other substrate having a parallel-plate heat transfer surface
configuration. The substrate media can be either
non-desiccant-coated "sensible" substrate, or "enthalpic" desiccant
coated substrate. In exemplary embodiments, spirally wound
substrate media strips are arranged in a parallel-plate manner
using an embossed formation periodically to hold the strips in a
parallel-plate configuration. The strip layers may be arranged so
that every other layer has embossments and each alternating layer
may be flat without embossments. The embossed standoffs--or
embossments--are not intended to be aligned with one another
periodically, and a parallel-plate arrangement is achieved, rather
than a typical triangular shaped arrangement. The benefits of a
parallel-plate geometry media over other typically used geometries
include higher thermal performance resulting in increased energy
savings, lower pressure drop to reduce fan power energy required
and reduce structural load on the wheel frame, less clogging due to
contaminates resulting in better long term savings, longer life,
and less frequent cleaning, less material required to manufacture
for lower cost and weight.
[0030] FIG. 8 depicts an example of a parallel-plate substrate
media configuration 800 according to the present disclosure. As
shown, a rotary wheel, shown as 801, can include rotary wheel media
802, which can include a number of layers of a parallel-plate
configuration. Four such plates 804(1)-804(4) are shown, but any
practical number may be used. The parallel plates 804(1)-804(4) are
spaced apart creating parallel flow passageways 805(1)-805(3) to
allow airflow through the rotary wheel in the direction of wheel
depth. Of most importance is that the resultant parallel plates
(shown as curved in this application) are uniformly spaced apart,
and that the resultant parallel-plate passageways are not divided
into small triangular, square, or round finite small passageways.
While curved (circular) parallel plates are shown, other geometries
can of course be realized within the scope of the present
disclosure, e.g., "spiral" polygon shapes, concentric polygon
shapes, straight parallel plates, etc. Moreover, while some
embodiments may be wound, e.g., like tape on a spool, other
embodiments may have concentric shapes, sized appropriately to next
together such as shown in FIG. 9A-9B.
[0031] FIGS. 9A-9D depict further examples of a parallel-plate
plate substrate media configurations 900A-900D according to the
present disclosure. FIG. 9A depicts a section 900A of a concentric
circular rotary wheel media having parallel and concentric plates
that are not wound per se but assembled adjacent to one another in
a nested circular fashion as shown. FIG. 9B depicts a section 900B
of a concentric square rotary wheel media (fitting within the shape
of a rotary wheel) having parallel and concentric plates that are
not wound per se but assembled adjacent to one another in a nested
arrangement of squares (or rhomboids or rectangles) as shown. FIG.
9C depicts a section 900C of a wheel media having parallel plates
that are in a stacked flat and parallel arrangement as shown. FIG.
9D represents a section 900D of a spirally wound rotary wheel media
showing three layers or plates of a parallel-plate configuration
with embossments. The section 900D includes a central layer 902 and
two adjacent layers 904(1)-904(2). The adjacent layers or plates
904(1)-904(2) are shown to be flat layers, while the middle or
central layer or plate 902 is show to have periodically spaced
standoffs, or embossments, 910(1)-910(3) to create the
parallel-plate configuration. The embossments 910(1)-910(3) touch
and physically separate the central plate 902 from two other
adjacent plates 904(1)-904(2). The periodic spacing of the standoff
embossments (such a 910A-910C) is not critical to the increased
performance of parallel-plate designs described herein, as long as
it is frequent enough to keep the layers from deforming or sagging
thereby losing parallel configuration, and not too frequent to
essentially create a square finite flute configuration rather than
a parallel-plate configuration. The spacing between the
embossments, thus, may be dependent upon the material(s) used for
the layers or plates and the thickness of the layers or plates,
and/or the desired height of the embossments. The embossments are
preferably the full width of the matrix for leakage mitigation
purposes, whatever the width is (e.g., 1'' to 12''). The
embossments can be uniform across their length, e.g., with the
profile as shown in FIG. 9D.
[0032] As shown, the crimped embossment can have a compressed
sign-wave-like shape, in exemplary embodiments. Such a shape offers
the advantages of centering the middle formed layer between flat
layers uniformly and creating a structural support between the
surface of one flat layer though the middle formed layer to the
surface of the next flat layer. This sign wave shaped embossment
helps to keep the wheel media from collapsing as it is spirally
wound from a small diameter to large diameter while maintaining a
uniform parallel-plate media configuration. Such an embossment can
be made by any suitable method or technique. In exemplary
embodiments, such embossments may be made by crimping or stamping
or forming the media as required. One method of creating the sine
wave formation would be to create a stamping die of the profile
desired (e.g., a machined die set), and stamp that formation into a
media layer at the desired frequency or spacing by drawing the
layer strip through the die, and actuating the die at a rate
coincidental to the rate of the strip to create the formations at
the desired periodic spacing. Such embossments may, in exemplary
embodiments, have features joined at an angle in the range of
approximately 5 degrees to approximately 15 degrees. In exemplary
embodiments, the layers or plates are made of 1100 series alumni
having a uniform thickness in the range of between about 1 mil
(0.001 inch) and about 5 mil (0.005 inch), e.g., 1 mil, 2 mil, 3
mil, 4 mil, or 5 mil. Of course, other types of aluminum alloy can
be used. By employing embossments with such a configuration, a
number of advantages are afforded. These advantages include, but
are not limited to, the ability to use thin gauge metal for the
matrix media, e.g., aluminum, aluminum alloys, stainless steel
alloys (e.g., 300 series including 304 and 310), titanium, titanium
alloys, and the like. These advantages also include the doing away
of any need to use secondary embossments, such as single-sided
embossments as used in the prior art, which reduces friction loss
(lowering the pressure drop), which in turn reduces power
requirements for one or more fans pushing air through the system.
By doing away with a need to use secondary embossments, embodiments
of the present disclosure can provide a much lower recovery
efficiency ratio (RER) compared with prior art design. The RER, a
well-known parameter in the HVAC energy recovery field, is defined
as energy recovered over the energy expended in the recovery.
Embodiments of the present disclosure can improve either or both of
the numerator and denominator of the RER. Moreover, doing away with
the need for using secondary embossments also removes the
requirement of aligning the heights of the two different types of
embossments, which task is normally labor, time, and energy
intensive.
[0033] The challenge in designing heat transfer media passageway
geometry is the tradeoff between having more heat transfer media
surface area for better thermal performance and less heat transfer
media surface area for lower friction, i.e. pressure drop through
the regenerator. The laminar flow ratio (f/j) is a parameter that
describes the friction to heat transfer media geometry for various
passageway configurations. The letter f stands for the friction
coefficient, and the letter j for the Coburn heat transfer factor.
It has been shown that as the f/j ratio becomes smaller, the
tradeoff between friction loss and heat transfer capability is
optimized. Within typical heat transfer media spacing ranges used,
f/j ratios have been calculated to support the idea that
parallel-plate heat transfer media geometry has a higher performing
configuration than round ducts, square ducts, triangular ducts, or
random packed ducts. In the laminar flow region typically applied
to energy recovery regenerators, the f/j factors can be calculated
for various media geometries using the following formula:
f j = Pr 1 3 * f * Re Nu . [ EQ . 1 ] ##EQU00001##
[0034] In Equation 1, Pr designates the Prandtl number for gas (0.7
for most gasses). (f*Re) is the resultant of multiplying the
friction factor (f) of the geometry and the Reynolds number (Re).
Nu is the Nusselt number resulting from the given geometry. Using
Nu and f*Re values (e.g., from Kays and London Compact Heat
Exchangers--third edition 1984, p. 120), f/j factors can be
calculated for specific media geometries, giving f/j factors of
4.79 for triangular passageways, 4.23 for square ducts, 3.88 for
round ducts, and 2.8 for parallel-plate ducts. This reveals that
the parallel-plate geometry under laminar flow conditions exhibits
superior performance (tradeoff between pressure loss and thermal
transfer) per unit of media face area.
[0035] Having a regenerator media geometry that provides lower
friction and higher thermal transfer per unit face area results in
several performance advantages. Higher thermal transfer results in
higher energy savings over time. Lower friction loss translates
into lower pressure drop through the regenerator resulting in less
fan power (energy) required to pass airflow through the device,
which translates into better overall energy savings over time.
Lower pressure drop also translates into less load on the wheel
frame structure resulting in longer life of the device.
[0036] In some applications, VOCs or `sticky` contaminants (such as
cigarette smoke or airborne cooking oils) that may be present in
the ventilated space will be passed through the wheel and can
potentially stick to the media surface and eventually restrict the
passageways. In addition, any dust or dirt particles in the space
caught in the HVAC system will pass through the wheel, further
dirtying and restricting the passageways. Once the wheel media
passageways become restricted due to clogging, thermal performance
is degraded and pressure drop through the wheel is increased
resulting in lower energy savings, increased operational costs,
higher structural loads to the wheel frame, and potentially
decreased supply of ventilation air through the wheel.
[0037] Long, thin "flute" or straw-like triangular passageways
resultant of a typical prior-art corrugated matrix geometry 700,
such as shown in FIG. 7, can become restricted as the non-air
particles build up, and block the passageway. Because the
corrugated matrix design results in finite triangular shaped
straw-like `fluted` passageways, the velocity profile is not
constant across the cross section of each passageway. The flow has
a lower velocity in the corners of the triangles, as eddies and
roll-ups from the corners' boundary layers block the incoming flow.
These low velocity corners are perfectly suitable for dust and
other contaminants to build up in, as the flow is too slow to force
them out the long passageway. As the passageways in the wheel
become restricted by built up contaminants, the pressure drop
through the wheel will increase drastically as blockages in the
incoming flow develop. As each finite fluted passageways become
more and more clogged over time, less thermal performance and
higher pressure drops are realized, and the passageway can
eventually become completely blocked. These straw-like passageways
are difficult to clean due to their small cross section and long
flow length. In addition, the fluted design inherently results in a
very stiff media assembly. Between the flow length of the
passageway (often between 6 inches up to a foot), the rigidity of
the media, and the triangular shape with tight, difficult to clean
corners, the corrugated design can be difficult to clean of built
up clogging.
[0038] The shape of the parallel plate geometry does not
necessarily have tight corners to collect dust and dirt, and the
length of the passageway is typically shorter, e.g., between 1
inches up to 6 inches depending on the design and size of the
wheel. In addition, the parallel-plate media can flex since it
lacks the high structural rigidity of the corrugated, triangular
shape. This flexing can allow contaminants to more readily pass
through the media rather than collect within a rigid finite
passageway.
[0039] During use, the velocity profile across the wheel and within
each parallel passageway is more uniform than the corrugated
triangular fluted media at each diameter (due to the lack of tight
passageways and increased area for open flow per diameter), helping
prevent lower flow velocities that would allow a build-up of
contaminants and thus flow blockages. The flexible matrix geometry
allows slight motion during operation which will also help in
keeping potentially clogging particles moving through the short
passageway.
[0040] Cleaning of any substances attached to the media is more
effective with the parallel-plate design, as there are no finite
small flutes and fewer tight corners to flush out, and the media
may be flexed to allow any particles to dislodge and exit the short
flow length. The parallel-plate design also helps to prevent
clogging during use, necessitating less frequent cleaning.
[0041] Because the parallel-plate design prevents the amount of
blockage inherent to a corrugated design, the pressure drop is not
expected to rise during use as it would in its corrugated
counterpart. Thus, the parallel plate not only decreases the
potential for clogging of the media and improves the clean-ability
of the wheel, but also reduces the overall pressure drop through
the wheel over time. Due to the potential of contaminants and other
non-air substances flowing through the passageways of the wheel,
the parallel-plate design is better suited than the fluted or
corrugated design to applications with any possibility of
contaminants that may foul the wheel.
Exemplary Embodiments
[0042] A rotary wheel regenerator with parallel plate media
geometry design according to the present disclosure can provide one
or more of the following advantages:
[0043] Having lower friction loss through the media passageways
resulting in lower pressure loss profile through the regenerator
therefore resulting in less energy (blower power) required to pass
air through either side of the device (fresh air side and exhaust
air side), resulting in better energy savings over time.
[0044] Having lower pressure drop due to better geometrical flow
profile resulting in less load and stress on the structure of the
heat wheel resulting in longer life of the wheel.
[0045] Having higher overall transfer of heat and/or moisture as
desired from one side of the regenerator to the other resulting in
higher energy savings.
[0046] Using less spirally wound length of material to manufacture
the geometry than typical corrugated triangular flute media
resulting in lower media cost and lighter weight of the finished
device.
[0047] Having geometrical passageways that are less prone to
collecting dirt and dust due to the passageway shape (parallel
plate--long rectangular shape), and therefore are less apt to
restrict and clog over time.
[0048] Having geometrical passageways that are slightly flexible to
aid in allowing dirt and dust to pass through the media more
readily.
[0049] Having passageways that are more readily cleaned due to
shape and flexibility, resulting in better energy savings over time
and consistent supply of fresh air for IAQ.
[0050] Having resultant transfer media that will maintain higher
energy transfer over time and lower pressure losses over time due
to being less prone to clogging, and due to better flow profiles
through the cross section and more easily cleanable due to cross
section shape and flexibility.
[0051] Having better energy savings over time due to less
degradation due to clogging and ease of cleaning.
[0052] The components, steps, features, objects, benefits, and
advantages that have been discussed are merely illustrative. None
of them, nor the discussions relating to them, are intended to
limit the scope of protection in any way. Numerous other
embodiments are also contemplated. These include embodiments that
have fewer, additional, and/or different components, steps,
features, objects, benefits, and/or advantages. These also include
embodiments in which the components and/or steps are arranged
and/or ordered differently.
[0053] For example, as shown in FIG. 9, one method of creating
parallel plate rotary wheel media is to create an intermediate
layer, between two flat layers, having embossed formations
sufficiently periodically spaced intended to stand the layers apart
thus creating parallel plates. Variations to this method could
include a variety of other methods of spacing the layers apart
including inserting periodically small pins into a layer or layers,
perpendicular to the face of the layers, to hold the layers
uniformly apart, applying a spot of glue or polymer material of the
appropriate thickness periodically to hold the layers uniformly
apart, fastening thin spacers periodically extending across the
wheel width from wheel face to wheel face to hold the layers
uniformly apart, piercing small formations (e.g., like so-called
"chads" on ballot cards) into the surface of each flat layer to
create standoffs to hold the layers uniformly apart. Another method
of holding the parallel plates apart could be to install a series
of thin rods or wires from the outer diameter of the wheel rim,
through all of the layers, and into the hub of the wheel,
perpendicular to the wheel axis. Each layer (in this case all flat
layers) would be pierced by the rods and held in their appropriate
positions to create uniform spacings and passageways between the
flat layers.
[0054] Unless otherwise stated, all measurements, values, ratings,
positions, magnitudes, sizes, and other specifications that are set
forth in this specification, including in the claims that follow,
are approximate, not exact. They are intended to have a reasonable
range that is consistent with the functions to which they relate
and with what is customary in the art to which they pertain.
[0055] All articles, patents, patent applications, and other
publications that have been cited in this disclosure are
incorporated herein by reference.
[0056] The phrase "means for" when used in a claim is intended to
and should be interpreted to embrace the corresponding structures
and materials that have been described and their equivalents.
Similarly, the phrase "step for" when used in a claim is intended
to and should be interpreted to embrace the corresponding acts that
have been described and their equivalents. The absence of these
phrases from a claim means that the claim is not intended to and
should not be interpreted to be limited to these corresponding
structures, materials, or acts, or to their equivalents.
[0057] The scope of protection is limited solely by the claims that
now follow. That scope is intended and should be interpreted to be
as broad as is consistent with the ordinary meaning of the language
that is used in the claims when interpreted in light of this
specification and the prosecution history that follows, except
where specific meanings have been set forth, and to encompass all
structural and functional equivalents.
[0058] Relational terms such as "first" and "second" and the like
may be used solely to distinguish one entity or action from
another, without necessarily requiring or implying any actual
relationship or order between them. The terms "comprises,"
"comprising," and any other variation thereof when used in
connection with a list of elements in the specification or claims
are intended to indicate that the list is not exclusive and that
other elements may be included. Similarly, an element proceeded by
an "a" or an "an" does not, without further constraints, preclude
the existence of additional elements of the identical type.
[0059] None of the claims are intended to embrace subject matter
that fails to satisfy the requirement of Sections 101, 102, or 103
of the Patent Act, nor should they be interpreted in such a way.
Any unintended coverage of such subject matter is hereby
disclaimed. Except as just stated in this paragraph, nothing that
has been stated or illustrated is intended or should be interpreted
to cause a dedication of any component, step, feature, object,
benefit, advantage, or equivalent to the public, regardless of
whether it is or is not recited in the claims.
[0060] The abstract is provided to help the reader quickly
ascertain the nature of the technical disclosure. It is submitted
with the understanding that it will not be used to interpret or
limit the scope or meaning of the claims. In addition, various
features in the foregoing detailed description are grouped together
in various embodiments to streamline the disclosure. This method of
disclosure should not be interpreted as requiring claimed
embodiments to require more features than are expressly recited in
each claim. Rather, as the following claims reflect, inventive
subject matter lies in less than all features of a single disclosed
embodiment. Thus, the following claims are hereby incorporated into
the detailed description, with each claim standing on its own as
separately claimed subject matter.
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