U.S. patent application number 12/228667 was filed with the patent office on 2009-03-05 for heat exchanger.
This patent application is currently assigned to Prodigy Energy Recovery Systems Inc.. Invention is credited to Gilbert Demedeiros, Marc Hoffman.
Application Number | 20090056919 12/228667 |
Document ID | / |
Family ID | 40348401 |
Filed Date | 2009-03-05 |
United States Patent
Application |
20090056919 |
Kind Code |
A1 |
Hoffman; Marc ; et
al. |
March 5, 2009 |
Heat exchanger
Abstract
Disclosed herein is a heat exchange apparatus, which comprises a
hollow blade member having a first fluid inlet and a first fluid
outlet and a first fluid passageway for a first fluid that extends
between the inlet and the outlet. The blade member is sized and
shaped to be located in a second fluid passageway for a second
fluid. The blade member is configured to enhance thermal energy
transfer between the fluids as they flow along their respective
passageways.
Inventors: |
Hoffman; Marc;
(Saint-Lambert, CA) ; Demedeiros; Gilbert;
(Beaconsfield, CA) |
Correspondence
Address: |
LERNER, DAVID, LITTENBERG,;KRUMHOLZ & MENTLIK
600 SOUTH AVENUE WEST
WESTFIELD
NJ
07090
US
|
Assignee: |
Prodigy Energy Recovery Systems
Inc.
Montreal
CA
|
Family ID: |
40348401 |
Appl. No.: |
12/228667 |
Filed: |
August 14, 2008 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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60964658 |
Aug 14, 2007 |
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60994039 |
Sep 17, 2007 |
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61008766 |
Dec 21, 2007 |
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61134666 |
Jul 11, 2008 |
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Current U.S.
Class: |
165/109.1 ;
165/164 |
Current CPC
Class: |
F24D 2200/20 20130101;
F28D 7/0008 20130101; F28F 3/048 20130101; F24D 17/0005 20130101;
F28F 13/12 20130101; F28D 21/0012 20130101; F28F 13/08 20130101;
F28F 27/02 20130101; F28D 7/10 20130101; F28D 7/16 20130101; Y02B
30/18 20130101; Y02B 30/566 20130101; Y02B 30/56 20130101; F28F
1/40 20130101 |
Class at
Publication: |
165/109.1 ;
165/164 |
International
Class: |
F28F 13/12 20060101
F28F013/12; F28D 7/00 20060101 F28D007/00 |
Claims
1. A heat exchange apparatus, the apparatus comprising: a hollow
blade member having a first fluid inlet and a first fluid outlet
and a first fluid passageway for a first fluid extending
therebetween, the blade member being sized and shaped for location
in a second fluid passageway for a second fluid, the blade member
being configured to enhance thermal energy transfer between the
fluids as they flow along their respective passageways.
2. The apparatus, according to claim 1, in which the enhancement of
thermal energy transfer is caused by turbulent flow.
3. The apparatus, according to claim 1, in which the enhancement of
thermal transfer is caused by reduction of laminar flow.
4. The apparatus, according to claim 1, in which the enhancement of
thermal transfer is caused by shear within the first and second
fluids.
5. The apparatus, according to claim 1, in which the blade member
has an inner and an outer thermal transfer surface, the inner
thermal transfer surface having a plurality of spaced apart inner
surface projections to induce thermal energy transfer in the first
fluid, the outer thermal transfer surface being located to contact
the second fluid flowing along the second fluid passageway.
6. The apparatus, according to claim 5, in which the inner thermal
transfer surface further includes a plurality of spaced apart inner
surface recesses.
7. The apparatus, according to claim 5, in which the outer thermal
surface has a plurality of spaced apart outer surface projections
located to induce thermal energy transfer in the second fluid as it
flows along the second fluid passageway in contact with the outer
thermal transfer surface.
8. The apparatus, according to claim 5, in which the outer thermal
transfer surface further includes a plurality of spaced apart outer
surface recesses.
9. The apparatus, according to claim 5, in which the inner and
outer thermal transfer surfaces each have a plurality of spaced
apart projections and recesses, the projections and recesses being
disposed substantially parallel to each other.
10. The apparatus, according to claim 1, in which the blade member
has a longitudinal blade axis and two blade walls, each blade wall
having an inner and an outer thermal transfer surface, each thermal
transfer surface having a plurality of ridges and recesses disposed
substantially parallel to each other.
11. The apparatus, according to claim 10, in which the outer
thermal transfer surfaces are located to contact the second fluid
flowing along the second fluid passageway.
12. The apparatus, according to claim 10, in which the ridges and
recesses of the first blade wall being angled in a first direction
relative to the longitudinal axis, the ridges and recesses of the
second blade wall being angled in a second direction relative to
the longitudinal axis, the second direction being different from
the first direction so as to induce cross flow in the first and
second fluids as they travel along their respective
passageways.
13. The apparatus, according to claim 10, in which the ridges
located on opposing inner thermal transfer surfaces contact each
other to induce cross flow in the first fluid as it travels along
the first fluid passageway.
14. The apparatus, according to claim 10, in which the ridges
located on opposing inner thermal transfer surfaces are spaced
apart from each other to induce cross flow in the first fluid as it
travels along the first fluid passageway.
15. The apparatus, according to claim 10, in which the ridges
located on opposing inner thermal transfer surfaces are
interdigitated to induce cross flow in the first fluid as it
travels along the first fluid passageway.
16. The apparatus, according to claim 10, in which the ridges
located on opposing inner thermal transfer surfaces contact each
other to induce turbulence in the first fluid as it travels along
the first fluid passageway.
17. The apparatus, according to claim 10, in which the ridges
located on opposing inner thermal transfer surfaces are spaced
apart from each other to induce turbulence in the first fluid as it
travels along the first fluid passageway.
18. The apparatus, according to claim 10, in which the ridges
located on opposing inner thermal transfer surfaces are
interdigitated to induce turbulence in the first fluid as it
travels along the first fluid passageway.
19. The apparatus, according to claim 1, in which the second fluid
passageway is configured to induce thermal energy-transfer between
the fluids.
20. The apparatus, according to claim 1, in which the first and
second fluids flow in a contraflow direction.
21. The apparatus, according to claim 1, in which the first and
second fluids flow in a parallel flow configuration.
22. The apparatus, according to claim 1, in which the first and
second fluids flow in a cross flow configuration.
23. The apparatus, according to claim 1, in which each blade wall
has a sealable blade edge to allow the blade member to be
pressurized.
24. The apparatus, according to claim 23, in which the blade member
is pressurized to above atmospheric pressure or to below
atmospheric pressure.
25. The apparatus, according to claim 1, in which the blade member
has a longitudinal blade axis, the first fluid inlet and the first
fluid outlet being disposed orthogonal relative to the longitudinal
blade axis.
26. The apparatus, according to claim 1, in which the blade member
has a longitudinal axis, the second fluid passageway has a second
fluid inlet and a second fluid outlet, the second fluid inlet and
the second fluid outlet being disposed coaxial to the longitudinal
axis.
27. The apparatus, according to claim 26, in which the second fluid
inlet and the second fluid outlet are disposed orthogonal to the
longitudinal axis of the blade member.
28. The apparatus, according to claim 1, in which the blade member
is double-walled.
29. The apparatus, according to claim 28, in which the double wall
is a lining located in intimate contact with an inner thermal
transfer surface of the blade member.
30. The apparatus, according to claim 29, in which the lining is
spaced apart from the inner thermal transfer surface, a thermal
transfer filler being located between the lining and the inner
thermal transfer surface.
31. The apparatus, according to claim 29, in which the lining is a
bladder.
32. The apparatus, according to claim 31, in which the bladder is
made from a membraneous heat conductive material.
33. The apparatus, according to claim 1, in which the blade member
is ventable to the atmosphere.
34. The apparatus, according to claim 1, in which the blade member
further comprises a lining located in intimate contact with an
inner thermal transfer surface of the blade member, the lining
defining a double wall, the blade member being configured to allow
the first fluid to drain away from the first passageway or the
second fluid from the second fluid passageway, if either of the
passageways breaks.
35. The apparatus, according to claim 1, in which the first or
second fluids flow by gravity.
36. The apparatus, according to claim 1, in which a turbulator is
located in the first fluid passageway.
37. The apparatus, according to claim 1, in which a turbulator is
located in the second fluid passageway.
38. The apparatus, according to claim 1, in which the second fluid
passageway is pressurized to above atmospheric pressure or below
atmospheric pressure.
39. The apparatus, according to claim 1, in which the first fluid
is cold water and the second fluid is grey water.
40. A blade heat exchange apparatus, the apparatus comprising: at
least one blade member having a first fluid inlet and a first fluid
outlet, and a first fluid passageway for a first fluid extending
therebetween, the blade member having a longitudinal blade axis; a
second fluid passageway for a second fluid, the second fluid
passageway being sized and shaped to receive therein the blade
member; the blade member has two blade walls, each blade wall
having an inner and outer thermal transfer surface, the thermal
transfer surfaces each having a plurality of spaced apart ridges
and recesses, the ridges and recesses being substantially parallel
to each other, the ridges and recesses of the first blade wall
being angled in a first direction relative to the longitudinal
axis, the ridges and recesses of the second blade wall being angled
in a second direction relative to the longitudinal axis, the second
direction being different from the first direction so as to induce
cross flow in the first and second fluids as they travel along
their respective passageways.
41. The heat exchange apparatus, according to claim 40, the ridges
located on the inner thermal transfer surfaces of the blade walls
contact each other, are spaced apart from each other, or are
interdigitated.
42. The heat exchange apparatus, according to claim 40, in which
the second fluid passageway is a channel located in a tray.
43. The heat exchange apparatus, according to claim 40, in which a
plurality of blade members are mounted substantially parallel to
each other.
44. The heat exchange apparatus, according to claim 40, in which a
plurality of the blade members are stacked on top of each other and
define a plate.
45. The heat exchange apparatus, according to claim 40, in which a
plurality of the plates are mounted in a housing, the housing
having a first fluid inlet and a first fluid outlet.
46. The heat exchange apparatus, according to claim 40, in which
the blade member is double walled.
47. The heat exchange apparatus, according to claim 40, in which
the blade member is ventable to the atmosphere.
48. The heat exchange apparatus, according to claim 40, is located
downstream of a drain trap.
49. The heat exchange apparatus, according to claim 40, in which
the first fluid passageway includes a turbulator.
50. The heat exchange apparatus, according to claim 40, in which
the second fluid passageway includes a turbulator.
51. A heat exchange apparatus, comprising: a central conduit having
a conduit wall; an outer jacket substantially encasing the central
conduit, the jacket being spaced apart from the conduit wall to
define an enclosure and having a fluid inlet and a fluid outlet; a
turbulator located in the enclosure, the turbulator having a first
helical wire disposed in a clockwise orientation and a second
helical wire disposed counterclockwise to the first helical wire so
as to induce turbulent flow in a fluid as it contacts the
turbulator.
52. The heat exchange apparatus, according to claim 51, in which
the first and second helical wires cross each other and induce
cross flow in the fluid as it contacts the helical wires.
53. The heat exchange apparatus, according to claim 51, in which
grey water flows along the central conduit.
54. The heat exchange apparatus, according to claim 51, in which
cold water contacts the turbulator.
55. The heat exchange apparatus, according to claim 54, in which
the cold water flows by gravity.
56. A heat exchange apparatus, the apparatus comprising: a central
conduit having a conduit wall; an outer jacket substantially
encasing the central conduit, the jacket being spaced apart from
the conduit wall to define an enclosure and having a fluid inlet
and a fluid outlet; a mesh turbulator located in the enclosure, the
mesh turbulator being configured to induce turbulent flow in a
fluid as it contacts the turbulator.
57. The apparatus, according to claim 56, in which the mesh
turbulator includes a first plurality of helical wires disposed in
a clockwise orientation and a second plurality of helical wire
disposed counterclockwise to the first plurality of helical
wire.
58. The apparatus, according to claim 56, in which the mesh
turbulator includes a plurality of orthogonally disposed wires.
59. The apparatus, according to claim 56, in which the central
conduit and the enclosure further include turbulators.
60. A heat exchange apparatus, the apparatus comprising: at least
one hollow fin member having first and second thermal transfer
surfaces, the first thermal transfer surface defining a first fluid
passageway for a first fluid, which first fluid being flowable
along the first passageway in contact with the first thermal
transfer surface; and a second fluid passageway for a second fluid,
the second fluid passageway being located in intimate contact with
the second thermal transfer-surface, such that the first fluid when
flowing along the first fluid passageway exchanges thermal energy
with the second fluid flowing along the second fluid
passageway.
61. The apparatus, according to claim 60, in which the fin members
are disposed substantially parallel to each other.
62. The apparatus, according to claim 60, further including a
turbulator disposed on the first thermal surface to induce
turbulent flow in the first fluid
63. The apparatus, according to claim 60, further including a
turbulator disposed on the second thermal surface to induce
turbulanet flow in the second fluid.
64. The apparatus, according to claim 60, in which the fin members
are configured as an H-shaped channel member having first and
second end portions, the first end portion being connectable to a
source of a first fluid, the first fluid entering the first end
portion at a first temperature and flowable along the first thermal
transfer surface, the first fluid exiting the second end portion at
a second temperature and a second fluid passageway having an inlet
and an outlet, the second fluid passageway being located in
intimate contact with the second thermal transfer surface, the
inlet being connectable to a source of a second fluid, the second
fluid entering the inlet at a third temperature and flowable along
the second fluid passageway, such that the first fluid when flowing
along the first fluid passageway exchanges thermal energy with the
second fluid flowing along the second fluid passageway, the second
fluid exiting the outlet at a fourth temperature.
65. The heat exchange apparatus, according to claim 60, in which
the fin members are circumferentially disposed about a conduit.
66. A heat exchange apparatus, the apparatus comprising: a conduit
having an arcuate conduit member having first and second ends, and
an arcuate heat exchanger having first and second connecting
portions sealingly connectable to the respective first and second
ends, the heat exchange having first and second thermal transfer
surfaces, an amount of a first fluid entering the conduit at a
first temperature and being in contact with the first thermal
transfer surface and exiting the conduit at a second temperature;
and a fluid passageway having a fluid passageway sidewall of a
membraneous material, the material having at least one heat
conductive surface locatable in intimate contact with the second
thermal transfer surface, the fluid passageway sidewall being
spreadable over an area of the second thermal transfer surface, the
fluid passageway having a fluid passageway inlet and a fluid
passageway outlet, a second fluid entering the fluid passageway
inlet at a third temperature and exiting the fluid passageway
outlet at a fourth temperature.
67. The apparatus, according to claim 1, in which the blade member
is self-supporting.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of the filing dates of
U.S. provisional patent application Ser. No. 60/964,658, filed Aug.
14, 2007; U.S. provisional patent application Ser. No. 60/994,039,
filed Sep. 17, 2007; U.S. provisional patent application Ser. No.
61/008,766, filed Dec. 21, 2007; and U.S. provisional patent
application Ser. No. 61/134,666, filed Jul. 11, 2008, the
disclosures of which are hereby incorporated herein by
reference.
FIELD OF THE INVENTION
[0002] The present invention concerns heat exchangers, and more
particularly to blade-type heat exchangers for recovering heat from
fluids.
BACKGROUND OF THE INVENTION
[0003] Heat exchangers are well-known and widely used in a number
of environments to recover thermal energy from fluids. The thermal
energy, if not recovered, would be lost to the environment.
Generally speaking, heat exchangers work by transferring heat from
one fluid to another via a solid wall, which separates the two
fluids. This straightforward principle has been used to recover
heat from waste water (so called "grey water") in, for example,
household shower and bath systems. A number of designs of heat
exchangers that have been used with household shower/bath systems
are described as follows.
[0004] U.S. Pat. No. 5,143,149 issued to Kronberg on Sep. 1, 1992
concerns a heat recovery system that includes a heat exchanger and
a mixing valve. The heat exchanger appears to include a drain trap
with an inner coiled tube, a baffle plate and a waste water outlet.
The inner coiled tube includes a cold water inlet and a pre-heated
water outlet in fluid communication with each other and is coiled
around the inside wall of a cylindrical member. A waste water inlet
is located in the drain trap such that waste water enters the
cylinder through the inlet, contacts the baffle plate and is
deflected away from a solid central portion towards a perforated
outer region such that the waste water gradually moves downwardly
through the cylinder until it reaches the bottom. Cold water
located in the coiled tube moves in a generally upward direction
opposite to the waste water as it flows downwardly over the coiled
tube to heat the cold water. Heat exchange appears to take place
through the walls of the coiled tube. The heated water then exits
the heat exchanger via the outlet. The design is simple and relies
on the counter-flow principal of heat exchange across a thermally
conductive wall of the coiled pipe. While this apparatus uses the
heat from waste drain water to heat cold water via a heat
exchanger, it does so by direct contact of the waste water with the
coiled cold water tube.
[0005] U.S. Pat. No. 4,821,793 issued to Sheffield on Apr. 18, 1989
discloses a tub and shower floor heat exchanger in which a heat
exchanger cover is supported on the tub floor by a number of
supports, each having an opening therein. The heat exchanger cover
is disposed away from the tub floor and includes a gap between the
cover and the tub floor. A heat exchange tube is connected to a
cold water supply line, the heat exchange tube being arranged
directly beneath the heat exchanger cover. Water flowing from a
shower head strikes the tub bottom and, as waste water flows
towards a drain hole, it is forced back and forth over an extended
path by means of the supports which serve as a baffle system. As
the waste water moves through the baffle system it moves through
the openings and is maintained in a heat exchange relationship with
the heat exchange tube over an extended period of time, thereby
heating the cold water in the heat exchange tube, which is then fed
back to a water line. Disadvantageously, a user of the tub may trip
over the raised heat exchanger cover. The tub may also be difficult
to clean and maintain.
[0006] U.S. Pat. No. 4,619,311 issued to Vasile et al. on Oct. 28,
1986 discloses a counter-flow heat exchanger system in which waste
water exits a shower tub via an essentially vertical waste pipe. A
lower portion of the waste pipe is surrounded by a jacket into
which is fed cold water in a coaxial counter-flow orientation such
that waste water travelling down the waste water pipe exchanges its
heat with the cold water travelling up the jacket thereby heating
the cold water by heat transfer across the waste water pipe wall.
The heated water exits directly to the shower system or moves to a
hot water heater tank.
[0007] U.S. Pat. No. 4,472,372 issued to Hunter on Feb. 8, 1983
discloses a heat exchanger that is located in a drain pipe of a
shower bath. A cylindrical member is in communication with the
drain hole and includes, on the interior, a coiled heat conducting
conduit. The coiled conduit includes a coiled copper tube which
extends the full length of the cylindrical housing and a second
heat conducting coil that is disposed within the annulus of the
first heat conducting coil. The coils are each fed by a common
inlet conduit which feeds cold water through the coiled conduits
such that waste water flowing into the cylindrical member heats the
cold water flowing through the coils which then exits via a common
outlet towards the mixing valve of the shower unit. A baffle in the
form of a central core member is disposed within the annulus of the
central coil and appears to cause the water flowing from the drain
pipe to be maintained in contact with both coils so as to maximize
heat transfer. The heat exchange in this design takes place by
direct contact of the waste water with the cold water conduit.
[0008] U.S. Pat. No. 4,304,292 issued to Cardone et al. on Dec. 8,
1981 discloses a shower unit in which a U-shaped conduit as part of
a heat exchange apparatus. A heat exchange conduit is coiled around
the exterior of the U-shaped conduit. Cold water flows through the
coiled conduit and is heated by the waste water flowing through the
U-shaped conduit, although there is no indication as to the nature
of the contact between the coils and the U-shaped conduit. It is
possible that the heat exchange is occurring across the walls of
the two conduits. The coiled cold water conduit may also be located
internally of the U-shaped conduit. Heat exchange appears to take
place by direct contact of the waste water with the coiled cold
water conduit.
[0009] U.S. Pat. No. 4,300,247 issued to Berg on Nov. 17, 1981
discloses a heat exchanger integral with the base of a shower unit
in which a drain hole is in communication with the heat exchanger.
The heat exchanger has a pair of so-called drain water flow through
compartments, which are separated by a heat conducting material
from a pair of cold water flow through compartments. Cold water is
fed into the compartments and, after absorbing heat from the drain
water, exits via an output. The heat exchange appears to occur by
direct contact of water with the surface of a supply of cold water;
in this case, however, instead of being a conduit, the cold water
is located in compartments. Waste water fills one side of a number
of serpentine compartments up to a line and exchanges heat across
the folded layers of heat conductive material into complementary
cold water containing compartments. Presumably, this folded
arrangement of the heat conductive material allows for a great
surface area over which the heat exchange can take place. The heat
exchange takes place by direct contact of waste water on the
container of cold water.
[0010] U.S. Pat. No. 6,722,421 issued to MacKelvie on Apr. 20, 2004
discloses a rather complex arrangement of either vertical or
horizontal heat exchangers which have built-in heat storage for
continuous heat recovery from waste drain water. A vertical heat
exchanger includes a drain conduit connected to a drain water
source, a water reservoir surrounding the drain conduit and a cold
water conduit coiled around the water reservoir. A number of nested
convection chambers are located on the external wall of the drain
conduit and hold a volume of water adjacent to the wall of the
drain conduit. In operation, drain water in the drain conduit heats
the volume of water in the chambers, which through convention flows
into the reservoir thereby heating same and the cold water flowing
through the coiled conduit. The horizontal version of the heat
exchanger has a convention chambers that appears to "cup" the
central drain conduit and operate on the same convection principle
as described for the vertical design. Interestingly, simultaneous
flow of cold water in the coiled conduit and waste water in the
drain conduit is not necessary. There is no contact between the
drain conduit and the cold water conduit.
[0011] U.S. Pat. No. 5,791,401 issued to Nobile on Aug. 11, 1998
discloses a portion of a waste water conduit which is U-shaped. The
drain conduit includes a number of axially disposed consecutive
solid wall ridges and depressions, which are located around the
entire inner surface of the drain conduit. A cold water conduit is
coiled around the waste water conduit and includes a smooth,
arcuate thermal transfer surface complementary to the curvature of
the cold water conduit sidewall. This design appears to operate
when the void in the U-shaped portion of the waste water drain
conduit is entirely filled with waste water.
[0012] U.S. Pat. No. 5,740,857 issued to Thompson et al., Apr. 21,
1998 discloses a heat recovery and storage device useful to recover
heat from warm waste water in which a generally horizontal waste
water conduit is surrounded by a cold water reservoir. The waste
water conduit includes a number of projections made of a high
thermally conductive material located on a lower external surface
of the conduit and which project into the cold water reservoir so
as to transfer heat to same. The upper portion of the conduit is
made of a material which limits heat re-conduction. The cold water
is in direct contact with the outer wall of the drain water
conduit.
[0013] U.S. Pat. No. 4,256,170 issued to Crump on Mar. 17, 1981
discloses a liquid-to-liquid heat exchanger which includes a number
of fins located at a lower portion of the waste water conduit. The
fins are arranged to define a generally serpentine fluid pathway
within a jacket of cold water, which surrounds the waste water
conduit. The fins are also used to transfer heat to the cold water
and induce turbulence in the cold water flow.
[0014] Thus, there is a need for an improved heat exchange
apparatus, in which the fluids do not contact each other and which
provides efficient thermal energy transfer across the heat
exchanger walls over a short pathway, and in which debris and
maintenance tooling can pass through the heat exchange
apparatus.
SUMMARY OF THE INVENTION
[0015] We have designed a novel, blade-type, passive fluid-to-fluid
heat exchange apparatus, which uses turbulators to induce and
maintain turbulent flow to provide unexpectedly high efficiency
heat recapture from waste water (also known as "grey water")
commonly found in household shower and bath systems. Moreover, the
blade members are self-supporting and do not require additional
frames for support as is typically required in existing heat
exchange designs.
[0016] Accordingly, in one aspect there is provided a heat exchange
apparatus, the apparatus comprising: a hollow blade member having a
first fluid inlet and a first fluid outlet and a first fluid
passageway for a first fluid extending therebetween, the blade
member being sized and shaped for location in a second fluid
passageway for a second fluid, the blade member being configured to
enhance thermal energy transfer between the fluids as they flow
along their respective passageways.
[0017] Accordingly in another aspect, there is provided a blade
heat exchange apparatus, the apparatus comprising: at least one
blade member having a first fluid inlet and a first fluid outlet,
and a first fluid passageway for a first fluid extending
therebetween, the blade member having a longitudinal blade axis; a
second fluid passageway for a second fluid, the second fluid
passageway being sized and shaped to receive therein the blade
member; the blade member has two blade walls, each blade wall
having an inner and outer thermal transfer surface, the thermal
transfer surfaces each having a plurality of spaced apart ridges
and recesses, the ridges and recesses being substantially parallel
to each other, the ridges and recesses of the first blade wall
being angled in a first direction relative to the longitudinal
axis, the ridges and recesses of the second blade wall being angled
in a second direction relative to the longitudinal axis, the second
direction being different from the first direction so as to induce
cross flow in the first and second fluids as they travel along
their respective passageways.
[0018] Accordingly in another aspect, there is provided a heat
exchange apparatus, comprising: a central conduit having a conduit
wall; an outer jacket substantially encasing the central conduit,
the jacket being spaced apart from the conduit wall to define an
enclosure and having a fluid inlet and a fluid outlet; a turbulator
located in the enclosure, the turbulator having a first helical
wire disposed in a clockwise orientation and a second helical wire
disposed counterclockwise to the first helical wire so as to induce
shear turbulent flow in a fluid as it flows through the enclosure
and contacts the turbulator.
[0019] Accordingly in another aspect, there is provided a heat
exchange apparatus, the apparatus comprising: a central conduit
having a conduit wall; an outer jacket substantially encasing the
central conduit, the jacket being spaced apart from the conduit
wall to define an enclosure and having a fluid inlet and a fluid
outlet; a mesh turbulator located in the enclosure, the mesh
turbulator being configured to induce shear and turbulent flow in a
fluid as it flows through the enclosure and contacts the
turbulator.
[0020] Accordingly in one embodiment of the present invention there
is provided a heat exchange apparatus, the apparatus
comprising:
[0021] a) at least one hollow fin member having first and second
thermal transfer surfaces, the first thermal transfer surface
defining a first fluid passageway for a first fluid, which first
fluid being flowable along the first passageway in contact with the
first thermal transfer surface; and
[0022] b) a second fluid passageway for a second fluid, the second
fluid passageway being located in intimate contact with the second
thermal transfer surface, such that the first fluid when flowing
along the first fluid passageway exchanges thermal energy with the
second fluid flowing along the second fluid passageway.
[0023] Accordingly in another embodiment of the present invention
there is provided a heat exchange apparatus, the apparatus
comprising:
[0024] a) a channel member having first and second end portions,
the channel member having a plurality of hollow fin members
extending between the first and second end portions, the fin
members having first and second thermal transfer surfaces, the
first thermal transfer surface defining a first fluid passageway,
the first end portion being connectable to a source of a first
fluid, the first fluid entering the first end portion at a first
temperature and flowable along the first thermal transfer surface,
the first fluid exiting the second end portion at a second
temperature; and
[0025] b) a second fluid passageway having an inlet and an outlet,
the second fluid passageway being located in intimate contact with
the second thermal transfer surface, the inlet being connectable to
a source of a second fluid, the second fluid entering the inlet at
a third temperature and flowable along the second fluid passageway,
such that the first fluid when flowing along the first fluid
passageway exchanges thermal energy with the second fluid flowing
along the second fluid passageway, the second fluid exiting the
outlet at a fourth temperature.
[0026] Accordingly in one embodiment of the present invention there
is provided a heat exchange apparatus, the apparatus
comprising:
[0027] a) a channel member having first and second thermal transfer
surfaces, at least one thermal transfer surface being uneven and
defining a first fluid passageway for a first fluid; and
[0028] b) a second fluid passageway for a second fluid, the second
fluid passageway being located in intimate contact with the second
thermal transfer surface, the flow of at least one of the fluids
being disrupted such that the first fluid when flowing along the
first fluid passageway exchanges thermal energy with the second
fluid flowing along the second fluid passageway.
[0029] Accordingly in another embodiment of the present invention,
there is provided a heat exchange apparatus, the apparatus
comprising:
[0030] a) a fluid passageway having a fluid passageway sidewall of
a membraneous material, the material having at least one heat
conductive surface locatable in intimate contact with a portion of
a conduit sidewall, the conduit having an inlet and an outlet, a
first fluid entering the inlet at a first temperature and exiting
the outlet at a second temperature, the fluid passageway sidewall
being spreadable over an area of the conduit sidewall, the fluid
passageway having a fluid passageway inlet and a fluid passageway
outlet, a second fluid entering the fluid passageway inlet at a
third temperature and exiting the fluid passageway outlet at a
fourth temperature.
[0031] Accordingly, in another embodiment, there is provided a heat
exchange apparatus, the apparatus comprising:
[0032] a) a conduit having an arcuate conduit member having first
and second ends, and an arcuate heat exchanger having first and
second connecting portions sealingly connectable to the respective
first and second ends, the heat exchanger having first and second
thermal transfer surfaces, an amount of a first fluid entering the
conduit at a first temperature and being in contact with the first
thermal transfer surface and exiting the conduit at a second
temperature; and
[0033] b) a fluid passageway having a fluid passageway sidewall of
a membraneous material, the material having at least one heat
conductive surface locatable in intimate contact with the second
thermal transfer surface, the fluid passageway sidewall being
spreadable over an area of the second thermal transfer surface, the
fluid passageway having a fluid passageway inlet and a fluid
passageway outlet, a second fluid entering the fluid passageway
inlet at a third temperature and exiting the fluid passageway
outlet at a fourth temperature.
[0034] Accordingly in another embodiment of the present invention,
there is provided a heat exchange apparatus for use with a P-Trap
having an inlet and an outlet, the P-Trap having a first drain
portion disposed orthogonal to the ground and connectable to a
drain, a second drain portion being disposed away from the ground
in a downward gradient, and a U-shaped drain portion
interconnecting the first and second drain portions, the apparatus
comprising:
[0035] a) a fluid passageway having a fluid passageway sidewall of
a membraneous material, the material having at least one heat
conductive surface locatable in intimate contact with a sidewall of
first drain portion, the second drain portion and the U-shaped
portion, a first fluid entering the inlet at a first temperature
and exiting the outlet at a second temperature, the fluid
passageway sidewall being spreadable over an area of the first
drain portion, the second drain portion and the U-shaped portion
sidewall, the fluid passageway having a fluid passageway inlet and
a fluid passageway outlet, a second fluid entering the fluid
passageway inlet at a third temperature and exiting the fluid
passageway outlet at a fourth temperature.
[0036] Accordingly in another embodiment of the present invention,
there is provided a drainage apparatus for use with a drain trap,
the apparatus comprising:
[0037] a) a P-Trap having an inlet and an outlet, the P-Trap having
a first drain portion being disposed orthogonal to the ground and
connectable to the drain trap, a second drain portion being
disposed away from the ground in a downward gradient and a U-shaped
drain portion interconnecting the first and second drain
portions;
[0038] b) the second drain portion comprising: [0039] i) an arcuate
conduit member having first and second ends, and an arcuate heat
exchanger having first and second connecting portions sealingly
connectable to the respective first and second ends, the heat
exchanger having first and second thermal transfer surfaces, an
amount of a first fluid entering the second drain portion at a
first temperature and being in contact with the first thermal
transfer surface and exiting the second drain portion at a second
temperature; and [0040] ii) a fluid passageway having a fluid
passageway sidewall of a membraneous material, the material having
at least one heat conductive surface locatable in intimate contact
with the second thermal transfer surface, the fluid passageway
sidewall being spreadable over an area of the second thermal
transfer surface, the fluid passageway having a fluid passageway
inlet and a fluid passageway outlet, a second fluid entering the
fluid passageway inlet at a third temperature and exiting the fluid
passageway outlet at a fourth temperature.
[0041] Accordingly in another embodiment of the present invention,
there is provided a drainage apparatus for use with a drain trap,
the apparatus comprising:
[0042] a) a P-Trap having a drain portion disposed orthogonal to
the ground and connectable to the drain trap and a U-shaped drain
portion;
[0043] b) a heat exchanger in fluid communication with the U-shaped
portion, the heat exchanger having a channel member having first
and second end portions, the channel member having a plurality of
hollow fin members extending between the first and second end
portions, the fin members having first and second thermal transfer
surfaces, the first thermal transfer surface defining a first fluid
passageway, a first fluid entering the first end portion from the
U-shaped portion at a first temperature and flowable along the
first thermal transfer surface, the first fluid exiting the second
end portion at a second temperature; and
[0044] c) a second fluid passageway having an inlet and an outlet,
the second fluid passageway being located in intimate contact with
the second thermal transfer surface, the inlet being connectable to
a source of a second fluid, the second fluid entering the inlet at
a third temperature and flowable along the second fluid passageway,
such that the first fluid when flowing along the first fluid
passageway exchanges thermal energy with the second fluid flowing
along the second fluid passageway, the second fluid exiting the
outlet at a fourth temperature.
[0045] Accordingly in one embodiment of the present invention there
is provided a drainage apparatus for use with a drain trap, the
apparatus comprising:
[0046] a) a P-Trap having a drain portion being disposed orthogonal
to the ground and connectable to the drain trap and a U-shaped
drain portion;
[0047] b) a heat exchange apparatus in fluid communication with the
U-shaped portion, the apparatus having a channel member having
first and second thermal transfer surfaces, at least one thermal
transfer surface being uneven and defining a first fluid passageway
for a first fluid received from the U-shaped portion; and
[0048] c) a second fluid passageway for a second fluid, the second
fluid passageway being located in intimate contact with the second
thermal transfer surface, the flow of at least one of the fluids
being disrupted such that the first fluid when flowing along the
first fluid passageway exchanges thermal energy with the second
fluid flowing along the second fluid passageway.
[0049] Accordingly, in another embodiment there is provided a heat
exchange apparatus, as described in the embodiments above, for use
with a drain trap of a bath tub or a shower tub in a household
drainage system.
[0050] Accordingly, in another embodiment there is provided a
turbulator for inducing turbulent flow in a fluid, the turbulator
comprising: a hollow blade member having a fluid inlet and a fluid
outlet, and a fluid passageway for the fluid extending
therebetween, the fluid passageway being configured to induce
turbulent flow in the fluid as it flows therealong.
[0051] Accordingly, in yet another embodiment, there is provided a
heat exchange apparatus, the apparatus comprising: a plurality of
turbulators for inducing turbulent flow in a first fluid, each
turbulator having a hollow blade member having a fluid inlet and a
fluid outlet, and a first fluid passageway for the first fluid
extending therebetween, the first fluid passageway being configured
to induce turbulent flow in the first fluid as it flows therealong;
and a second fluid passageway for a second fluid, the second fluid
passageway being sized and shaped to receive the turbulators
therein and configured to induce turbulent flow in the second fluid
as it flows along the second fluid passageway.
BRIEF DESCRIPTION OF THE DRAWINGS
[0052] These and other features of the invention will become more
apparent from the following description in which reference is made
to the appended drawings wherein:
[0053] FIGS. 1A and 1B illustrate a household shower/bath system
showing the location of an embodiment of a heat exchange
apparatus;
[0054] FIG. 2 is an exploded perspective view of an embodiment of a
heat exchange apparatus;
[0055] FIG. 3A is a perspective view of a channel member of FIG.
2;
[0056] FIG. 3B is a partial cross-sectional view taken along line
3b-3b' of FIG. 3 showing two uneven thermal transfer surfaces;
[0057] FIG. 4A is an end view of the channel member showing a
single uneven thermal transfer surface;
[0058] FIG. 4B is a detailed view of a number of peaks and troughs
of the channel member of FIG. 4A;
[0059] FIG. 5A is a longitudinal cross section view of the heat
exchange apparatus showing the location of end caps;
[0060] FIGS. 5B and 5C are end views showing respectively the first
end cap and the second end cap located relative to the channel
member;
[0061] FIG. 5D is a cross sectional end view of the heat exchange
apparatus with the end cap removed;
[0062] FIG. 6 is a perspective view of another embodiment of a
capillary heat exchange apparatus with end caps removed to show a
channel member;
[0063] FIGS. 7A-7D are a number of cross section views of the
channel member of FIG. 6 showing different locations of capillaries
and double walls;
[0064] FIG. 8 is an alternative cross section view of the channel
member of FIG. 6 showing the location of grey water;
[0065] FIGS. 9A and 9B are diagrammatic representations showing an
end view comparison of a standard conduit with a heat exchange
apparatus;
[0066] FIG. 10 is a detailed partially exploded perspective view of
an alternative capillary embodiment of a heat exchange
apparatus;
[0067] FIG. 11 is a partial cutaway view showing detail of the
apparatus of FIG. 10;
[0068] FIGS. 12A and 12B are respectively an end view and a
perspective view of an insert showing circumferentially disposed
hollow (capillary) fin members;
[0069] FIG. 13 is a longitudinal cross sectional view of an
embodiment of a partial clam shell and partial blister pack heat
exchange apparatus located around a grey water pipe;
[0070] FIG. 14 is a cross sectional end view of a blister pack-type
heat exchange apparatus located adjacent a grey water pipe;
[0071] FIGS. 15A and 15B are cross sectional views showing a double
wall bladder-type heat exchange apparatus and a blister pack heat
exchange apparatus located around a grey water pipe;
[0072] FIG. 16 is a cross sectional end view of an embodiment of a
heat exchange apparatus showing an arcuate insert and atmospheric
vent;
[0073] FIGS. 17A and 17B illustrate a household shower/bath system
showing the location of a heat exchange apparatus relative to a
P-Trap;
[0074] FIGS. 18A and 18B illustrate a household shower/bath system
showing the location of a check valve relative to the heat exchange
apparatus;
[0075] FIGS. 19A and 19B is an end view and a perspective partial
exploded view of an alternative embodiment of a heat exchange
apparatus showing a one piece insert having a multiple fluid
circuit;
[0076] FIG. 20A is a perspective partial exploded view of a heat
exchange apparatus showing multiple one piece inserts;
[0077] FIG. 20B is an end view of the heat exchange apparatus of
FIG. 20A;
[0078] FIG. 21A is a perspective exploded view of an embodiment of
an alternative capillary heat exchange apparatus;
[0079] FIG. 21B is a side view of the heat exchange apparatus of
FIG. 21A
[0080] FIG. 21C is a cross sectional view of the channel member of
FIG. 21A showing square top hollow fin members;
[0081] FIG. 22A is an end view of round top capillary heat exchange
walls;
[0082] FIG. 22B is diagrammatic representation of a heat exchange
apparatus showing difference planes of flow for grey water;
[0083] FIG. 23 is a perspective view of an embodiment of a blade
type heat exchange apparatus with blade members removed;
[0084] FIG. 24A is a perspective view of an alternative embodiment
of a blade type heat exchange apparatus showing blades having
surface patterns;
[0085] FIG. 24B is a partial cross-sectional view of blade members
of FIG. 24A showing interdigitating surface projections;
[0086] FIG. 25A is a diagrammatic representation of a hollow blade
member showing combined performance enhancement surface features in
which GW is grey water and CW is cold water;
[0087] FIG. 25B is a diagrammatic representation of the hollow
blade member taken along lines 25B showing fluid flow patterns;
[0088] FIG. 26 is a perspective, exploded view of an alternative
embodiment of a blade type heat exchange showing blades having
angled surface ridges;
[0089] FIG. 27 illustrates a number of club grip type corrugated
heat exchanger piping;
[0090] FIG. 28A is a side view of a blade member showing in solid
lines a plurality of angled ridges on one surface and in phantom
lines a plurality of angled ridges on another surface and
illustrating criss cross patterns and contact points;
[0091] FIG. 28B is a cross sectional view of the blade member taken
along line 28B showing the location of ridges and recesses of two
blade surfaces;
[0092] FIG. 29 is a diagrammatic representation of a section of a
blade member showing a centre spot weld, ridges, and crimped
ends;
[0093] FIG. 30A is a longitudinal cross section view of a double
wall blade member showing atmospheric vents;
[0094] FIG. 30B is a cross section view of the blade member taken
along 30B showing the double wall and surface textures;
[0095] FIG. 31A is a diagrammatic representation of a hollow blade
member showing macroscopic and microscopic textures and fluid flow
patterns;
[0096] FIGS. 32A and B is a representation of a golf ball showing
alternative icosahedron dimple structure;
[0097] FIG. 33 is a perspective partial cutaway view of a
blade-type heat exchanger;
[0098] FIG. 34 is a detailed view of an end portion of the
blade-type heat exchanger of FIG. 33 showing the manifold and heat
exchange wall details;
[0099] FIG. 35 is a detailed side view of one end of the heat
exchange apparatus of FIG. 33 showing ridges and recesses of blade
member surfaces;
[0100] FIG. 36 is a partially exploded view of a blade type heat
exchanger showing an alternative orientation of the cold water
manifolds;
[0101] FIG. 37 is a perspective view of a large scale blade-type
heat exchange apparatus housing;
[0102] FIG. 38 is a perspective view of the heat exchange apparatus
of FIG. 3 with the top removed to show the blade members;
[0103] FIG. 39 is a side view of a large dimensioned blade
member;
[0104] FIG. 40 is a perspective view of an alternative design of a
large dimension heat exchanger apparatus housing;
[0105] FIG. 41 is a side view of an alternative embodiment of a
vertical heat exchange apparatus;
[0106] FIG. 42 is a longitudinal cross sectional view of the heat
exchange apparatus of FIG. 41 showing the location of a double
slinky turbulator;
[0107] FIG. 43 is a detailed view of a section of the double slinky
wire turbulator;
[0108] FIGS. 44A and 44B are respectively a partial cutaway view
and a detailed view of a double slinky wire turbulator;
[0109] FIGS. 45A, 45B and 45C are respectively a partial cutaway
view and a detailed views of a mesh turbulator;
[0110] FIGS. 46A-46H illustrate a number of designs of compact heat
exchanger apparatus comprising internally located wire turbulators
or surface defined ribbed turbulators;
[0111] FIGS. 47A and 47B are perspective view of respectively a
smooth turbulator and a double sided ribbed turbulator;
[0112] FIG. 48 is a diagrammatic representation of a system for
controlling and for monitoring heat exchange apparatuses.
DETAILED DESCRIPTION
Definitions
[0113] Unless otherwise specified, the following definitions
apply:
[0114] The singular forms "a", "an" and "the" include corresponding
plural references unless the context clearly dictates
otherwise.
[0115] As used herein, the term "comprising" is intended to mean
that the list of elements following the word "comprising" are
required or mandatory but that other elements are optional and may
or may not be present.
[0116] As used herein, the term "consisting of" is intended to mean
including and limited to whatever follows the phrase "consisting
of". Thus the phrase "consisting of" indicates that the listed
elements are required or mandatory and that no other elements may
be present.
[0117] As used herein, the term "turbulator" when referring to
either a surface or to an insert having a surface that acts as a
turbulator, is intended to mean that the surface has a plurality of
projections extending away therefrom. Surface turbulators and
inserted turbulators are used to increase convenction rates and
heat transfer coefficients at heat exchange surfaces in fluid
passageways in order to provide high performance in compact heat
exchange assemblies, and to orientate fluids into a pre-defined
direction often resulting in chaotic paths. Examples of types of
turbulators include, but are not limited to, corrugations, peaks
and troughs, nubbins, raised chevrons having a gap between, fish
scales, raised zigzag moldings, meshes, criss cross oriented wires,
porous materials, and the like. Turbulators may comprise uniform or
non-uniform surface profiles, textures, open cell structures, and
shapes. Porosity and fluid passageway geometry allow control of
fluid flow via solid or semi-solid mechanical structures and may be
constructed from laminate composites, molded parts, and even mesh
of plastics, ceramics, metals or other materials.
[0118] As used herein the term "fluid" is intended to mean gas or
liquid. Examples of liquids suitable for use with the heat
exchangers described herein include, but are not limited to, water,
hydraulic fluid, petroleum, glycol, oil and the like. Examples of
gases include, for example, combustion engine exhaust gases and
steam.
[0119] The invention features a novel heat exchange apparatus in
which hollow fin members or hollow blade members with or without
surface patterns can be used to promote efficient thermal energy
transfer between fluids across thermal energy transfer surfaces.
The flow of fluids can be passive, i.e. by gravity or can flow
under the influence of pressure, either above or below atmospheric
pressure. The heat exchange apparatuses described herein are also
self-draining. Moreover due to their design, the blade members can
be located directly in a grey water pathway with or without the use
of pre-filtration to remove particulate debris. In one example, the
efficiency of heat recapture is 40-60% when compared to 25% heat
recapture efficiency of conventional systems. To achieve this, in
one example, we use a channel with plurality of hollow blades to
move, by gravity, grey water along a pathway such that it exchanges
its heat (typically about 40.degree. C.) to a source of cold water
flowing through another passageway located in intimate contact with
the channel. In other examples, higher fluid temperatures
(>100.degree. C.) can also exchange their thermal energy to cold
water so as to generate steam. The heat exchange takes place across
a thin (typically from about 1/1000 inch to about 1/5 inch
thickness) double wall arrangement. Furthermore, thermal energy
transfer occurs along a significantly shorter pathway between
thermal transfer surfaces when compared to thermal transfer across
solid fins. The cold water is heated to produce warmed water, which
may then be stored in a storage tank or communicated to a mixing
valve in a shower or bath system. Advantageously, the heat
exchanger apparatus is constructed from inexpensive materials and
when installed is essentially maintenance-free. The grey water
conduits (pipes) used are standard 1.5 to 4 inch and are
universally retrofittable into existing plumbing systems with the
minimum of disruption to the household. The apparatus may also be
connectable to active heat exchange apparatus such as, for example,
a Peltier Module. The various designs of heat exchange apparatus
will now be described in detail.
[0120] Referring now to FIGS. 1A and 1B, an embodiment of a modular
heat exchange apparatus is shown generally at 10 in use with a
household shower and bath system 12. The household shower and bath
system 12 includes a water heater 14, a hot water line 16, a cold
water line 18, a warm water line 20, a mixing valve 22, a shower
head 24 and a drain trap 26. The hot and warm water lines 16, 20
are each connected to the mixing valve 22, the temperature of the
water exiting the shower head 24 being controlled by the user
operating the mixing valve 22. The cold water line 18 is connected
to the heat exchange apparatus 10 and feeds cold water 25 (a second
fluid) into the apparatus 10. The warm water line 20 is connected
to the heat exchange apparatus 10 and the mixing valve 22. The
drain trap 26 receives drain water 28 (so called "grey water") (a
first fluid) from the shower/bath tub and communicates the drain
water to the heat exchange apparatus 10. After flowing through the
heat exchange apparatus 10, the grey water 28 exits the household
shower system 12 to a main drain (not shown). It should be noted
that although an example of a household shower/bath system is
illustrated, the heat exchange apparatus described may also be used
for other applications that require heat exchange between two
fluids. Furthermore, it is to be noted that any of the heat
exchangers described hereinbelow can also be connected to the
system 12.
[0121] Referring now to FIG. 2, the heat exchange apparatus 10 is
described in more detail. Broadly speaking, the heat exchange
apparatus 10 comprises a channel member 30 which has a first end
portion 32 and a second end portion 34, and which defines a first
fluid passageway 36 for the first fluid 28. The channel member 30
includes a first thermal transfer surface 38 and a second thermal
transfer surface 40. At least one of the thermal transfer surfaces
is uneven. In the example illustrated, both the thermal transfer
surfaces 38, 40 are uneven. In the example shown, the first thermal
transfer surface 38 is corrugated and defines a plurality of
fin-like peaks (or blades) 42 and troughs 44 that extend
longitudinally along the channel member 30 between the first and
second end portions 32, 34. Although the peaks 42 and troughs 44
are disposed substantially parallel to each other, it is to be
understood that the peaks 42 and troughs 44 can be arranged in any
manner. The first end portion 32 is connectable to a source of the
grey water 28, which enters the first end portion 32 at a first
temperature T1 and flows along the surface 38, exiting the second
end portion 34 at a second temperature T2. A second fluid
passageway 46, typically a cold water conduit, has a second fluid
inlet 48 and a second fluid in outlet 50, and is located in
intimate contact with the second thermal transfer surface 40 of the
channel member 30. The second fluid inlet 48 is connectable to a
source of the second fluid (not shown), which enters the inlet 48
at a third temperature T3 and flows along the second fluid
passageway 46. The grey water 28 exchanges thermal energy with the
cold water such that it exits the outlet 50 at a fourth temperature
T4 as warmed water. The temperature of the warmed water T4 is
greater than the temperature T3 of the cold water entering the
inlet 48. The warmed water feeds into the warm water line 20 and
may be mixed with hot water in the mixing valve 22.
[0122] The first and second fluids flow in a contra-flow manner
through the heat exchange apparatus 10. It is also possible to have
the fluids flow in a parallel flow manner. The first temperature T1
of the first fluid 28 entering the first fluid passageway 36 can be
greater than or less than the second temperature T2 of the first
fluid 28 as it exits the first fluid passageway 36. Similarly, the
third temperature T3 of the second fluid 25 can be greater than or
less than the fourth temperature T4 of the second fluid 25 as it
exits the second passageway 46. In the examples illustrated herein,
the first temperature T1 of the first fluid 28 entering the first
fluid passageway 36 is greater than the second temperature T2 of
the first fluid 28 as it exits the first fluid passageway 36. The
third temperature T3 of the second fluid 25 is less than the fourth
temperature T4 of the second fluid 25 as it exits the second fluid
passageway 46. By way of example, T1 is typically 40.degree. C. for
grey water (the first fluid), T2 is typically 30.degree. C. for
grey water exiting the heat exchanger 10, T3 is typically
10.degree. C. for cold water (the second fluid), and T4 is
typically 24.degree. C. for warmed water entering the warm water
line 22 from the heat exchanger 10. To measure the efficiency of
the heat exchange apparatus, the following equation is used:
Effectiveness = T cold out - T cold i n T grey i n - T cold i n
##EQU00001##
[0123] where T denotes temperature in .degree. C.
[0124] At least one of the fluids flows through its respective
passageway under pressure, the other fluid flowing through its
respective passageway at atmospheric pressure. Typically, the
second fluid (the cold water) flows under pressure at approximately
50 psi along the second fluid passageway 46.
[0125] Still referring to FIG. 2, the heat exchange apparatus 10
further comprises an arcuate piece 52, a first end cap 54 and a
second end cap 56. A support member 58 interconnects the arcuate
piece 52, the end caps 54, 56, and provides a housing for the
channel member 30 and the second fluid passageway 46. The channel
member 30 may optionally include a mesh filter 60 which lies snug
against the channel member 30. The mesh filter 60 significantly
reduces the amount of debris, such as hair, soap scum and other
particulates, which would otherwise clog the channel member 30.
[0126] Referring now to FIGS. 3A and 3B, the channel member 30 is
generally elongate and, when viewed in cross-section, is H-shaped.
The channel member 30 includes two sidewalls 62, 64 which form a
boundary on either side of the channel member 30. It is to be
understood that although the channel member 30 in this example
illustrated is H-shaped, any cross sectional shape is possible.
When connected to the drain trap 26, the channel member 30 is
disposed away from a horizontal plane towards the ground at an
angle of about 1.degree. such that when the grey water from the
shower drain enters the channel member 30 at the first end portion
32 it flows passively and by gravity along the first fluid
passageway towards the second end portion 34. Two adjacent peaks
42a and 42b define one trough 44a located therebetween. A fluid
convection promoter 68 (or turbulator) is located at a trough base
70 and projects into the trough 44a. The convection promoter 68 is
located on the first thermal transfer surface 38 and increases
thermal exchange, across the surface 38. Located between an end
peak 42c and each side wall 62, 64 is another convection promoter
68. The convection promoters 68 can be in the form of a microscopic
peak, although other promoters known to those skilled in the art
can be used. The second thermal transfer surface 40 may optionally
include a plurality of fin-like projections (or blades) 66, which
extend away from the surface 40, as best illustrated in FIG. 3B. In
one example, the projections 66 may be also be corrugations similar
in shape to the corrugations on the first thermal transfer surface
38. The cold water conduit (the second fluid passageway) lies
snugly and in intimate contact with the projections 66 so as to
provide highly efficient heat transfer from the first fluid
passageway 36 to the second fluid passageway 46.
[0127] Referring now to FIGS. 4A and 4B, the second thermal
transfer surface 40 is smooth. In this case, the second fluid
passageway 46 is located adjacent the second thermal transfer
surface 40 and includes a plurality of turbulators 72 located in
the second fluid passageway 46. The turbulators 72 in due
turbulence and establish shear forces in the second fluid as it
flows through the second fluid passageway 46. A number of
turbulators designed for round pipe insertion are known to those
skilled in the art.
[0128] As best illustrated in FIG. 4B, as the grey water flows
along the first fluid passageway 36 a rotational flow pattern is
established, as indicated by the arrows, between adjacent peaks.
This convective rotational flow pattern provides enhanced transfer
of thermal energy from the grey water to the heat conductive peaks
42 and troughs 44 of the first thermal transfer surface 38 to the
second fluid passageway 46 located adjacent thereto. Delaminators
(turbulators) can also be used to induce fluid rotation, or laminar
flow disrupters (turbulators) may be used to enhance thermal energy
transfers and also to manage fluid flow. Advantageously,
turbulators also manage debris and reduce its accumulation in the
first and second fluid passageways.
[0129] As best illustrated in FIGS. 2 and 5A through 5D, the first
end cap 54 is connected to the first end portion 32 of the channel
member 30, whereas the second end cap 56 is connected to the second
end portion 34. In order to aid flow of the grey water along the
first fluid passageway 36 by gravity and to reduce "pooling" of
water in the apparatus, the second end cap 56 is disposed at an
angle away from a longitudinal axis 74 of the channel member 30.
The location of the second end cap 56 with respect to the first end
cap 54 creates a deviation away from the axis 74. While this may be
acceptable to some local plumbing regulations, it may be prohibited
in others. In order to circumvent this problem, the first end cap
54 can be connected to the lower first end portion of the channel
member 30 with the same deviation from the longitudinal axis of the
channel member 30 such that the grey water would flow along the
channel member at a typical angle of 1.degree. away from the
horizontal.
[0130] Referring now to FIG. 6, an alternative example of a heat
exchange apparatus 76 is illustrated which comprises a non-H shaped
channel member 78, the first and second end caps 54, 56, the cold
water inlet 48 and the warmed water outlet 50. The channel member
78 includes a plurality of capillary hollow fin members 79 which
define wave-like peaks 80 and troughs 82 extending along the
channel member 78 between the first and second end portions 32,
34.
[0131] As best illustrated in FIGS. 7A through 7D, the hollow fin
members 79 include a first thermal transfer surface 84 located on
an upper portion of a first wall 86 (adjacent the grey water), the
first thermal transfer surface 84 defining the first fluid
passageway 28 for the first fluid, and a second wall 88 located in
intimate contact with the first wall 86. A second thermal transfer
surface 90 is located on a lower portion of the second wall 88. The
grey water flows along the first fluid passageway 28 in contact
with the first thermal transfer surface 84. A second fluid
passageway 92 is in intimate contact with the second thermal
transfer surface 90. The second fluid passageway 92 is a capillary
which carries the second fluid. The walls 86, 88 are generally
constructed from thin sheet thermally conductive material such as,
for example, aluminium, gold, copper or alloys thereof.
Additionally, the second wall 88 is sandwiched between the
capillary fluid passageway 92 and can allow venting to the
atmosphere via an interstitial gap between the first and second
walls 86, 88 in the event that the integrity of the walls 86, 88
are compromised. It should be noted that although a double wall
arrangement is illustrated, a single wall arrangement is also
contemplated, such that the capillary lies in intimate contact with
the second thermal transfer surface of the single wall. The channel
member 78 is mounted on a support 94 that includes a number of
complementary posts 96 which extend into the space between adjacent
peaks. As described above for the heat exchange apparatus 10, the
grey water flows along the first fluid passageway it exchanges
thermal energy with the cold water flowing along the second fluid
passageway. However, in this case the hollow design of the fin
members 79 allows heat exchange across a thin (typically from about
1/1000 inch to about 1/5 inch thickness) wall arrangement, such
that thermal energy transfer occurs along a significantly shorter
pathway between the thermal transfer surfaces when compared to
thermal transfer across solid fins as described above. The thin
walls of the heat exchanger 76 improve performance. Various
stiffeners such as, for example, surface adhesion, interlocking
geometries, external supports, fasteners, internal ribs and
chambers, as well as turbulators or combinations thereof, are used
to allow the use of thin walls. Water hammer protection (not shown)
can be built into the soft zones of the support 94 or the posts 96.
Additionally, turbulators (surface or insertable) may be used with
either of the first and second fluid passageways.
[0132] As best illustrated in FIG. 8, instead of having a capillary
fluid passageway 92 for the second fluid, the second fluid may flow
against the lower portion of the second wall 88 with the addition
of turbulators 98 to provide forced convection by shearing of the
second fluid at it travels in intimate contact with the second
thermal transfer surface. It is also possible to have similar
turbulators 98 on the first thermal transfer surface, but this may
compromise the flow of the grey water. An additional advantage of
having turbulators 98 replacing posts 96 is increased strengthening
of the channel member. Owing to the thinness of the walls of the
hollow fin members, strengthening members such as the turbulators
98 may be necessary to maintain the structural integrity of the
channel member. Grey water flowing along the channel member 78
fills the troughs 82 to near the top of the peaks 80. Thermal
energy is transferred across the first thermal transfer surface 84
to the second thermal transfer surface 90 via the first and second
walls 86, 88 and to the cold water flowing in the second fluid
passageway 92.
[0133] Referring now to FIGS. 9A and 9B, typically, grey water
exiting the drain trap 26 of the shower or bath tub enters a
cylindrical 2-inch drain pipe 70 and defines a surface areas of
approximately 0.85 in.sup.2 at a flow rate of approximately 10
L/minute. A volume of the grey water in the pipe 70 normally never
contacts the sidewall of the pipe 70 and if thermal energy is to be
recaptured by heat exchange across the sidewall, its transfer will
be largely inefficient. Advantageously, using the channel members
30 and 78 described above, the grey water 8 flows along the first
fluid passageway 36 at the same flow rate as with the pipe 70, but
does so over the length of the channels by contacting the heat
conductive peaks 42 and troughs 44. Thus, the distribution of the
0.85 in.sup.2 area into multiple smaller area sections maximizes
the heat transfer from the grey water by maximizing heat exchange
contact area surfaces.
[0134] Referring now to FIGS. 10, 11, 12A and 12B, in which an
alternative embodiment of a heat exchange apparatus is illustrated
generally at 100. The apparatus 100 comprises a circumferentially
disposed channel member 102, two end manifolds 104, 106, optional
turbulators 108, and an outer sleeve 109. The channel member 102
includes a plurality of hollow fin members 110 and a capillary cold
water passageway 112, which lies in intimate contact with the
second thermal transfer surface. A cold water inlet 114 feeds cold
water into the capillary 112 and warmed water exits the capillary
at an outlet 116. Grey water flows into the apparatus 100 via the
manifold 104 and flows over the first thermal transfer surface of
the channel member 102. The turbulators 108 not only disrupt the
flow of the grey water and create forced convention, but they also
maintain the structural integrity of the hollow fin members 110.
The turbulators can be surface turbulators or insertable
turbulators. Water hammer protection (not shown) can be built into
the soft zones of the turbulators 108. A one-piece capillary insert
111, as illustrated in FIGS. 12A and 12B, may be inserted into the
outer sleeve 109. The one-piece insert 111 includes the channel
member 102 as described above. The turbulators 108 can also be
inserted into the insert 111 to further enhance thermal transfer as
well as enhance the structural integrity of the apparatus. The
centrally disposed turbulator 108 can be used in a configuration
where the shaft of the element 108 is used to fasten and tighten
the manifolds 104, 106.
[0135] Referring now to FIG. 13, an alternative embodiment of a
heat exchange apparatus of the present invention is shown generally
at 200. Broadly speaking, the heat exchange apparatus 200 comprises
a cold water fluid passageway 202, which has an optional fluid
passageway sidewall 204 in double wall configurations that is made
of a membraneous material, which is pliable, yet resilient. The
material can be made from pliable sheet material, such as, for
example, but not limited to, gold, copper, or aluminium. The
material includes at least one heat conductive surface 206 which is
located in intimate contact with a portion of a sidewall 208 of a
grey water conduit 210. The conduit 210 has an inlet 212 and an
outlet 214. The grey water enters the inlet 212 at a first
temperature T1 and exits the outlet 214 at a second temperature T2.
In this embodiment, the fluid passageway sidewall 204 is spreadable
over an area of the conduit sidewall 208. The membrane may be a
single sheet of pliable material or it may be part of a bladder
that is made of the same pliable material. The fluid passageway 202
may be defined by the use of an inwardly directed force from an
external shell 218 that is located adjacent the sidewall 204. In
the example illustrated, the shell 218 surrounds the conduit 210
and the sidewall 204. It is also contemplated that only a half
shell located adjacent a lower portion of the conduit could be
used. The shell 218 includes a plurality of inwardly directed
projections 220, which when pressed against the membrane or bladder
defines the fluid passageway 202, and act as turbulators. The fluid
passageway includes a fluid passageway inlet 221 and a fluid
passageway outlet 223. The second fluid (cold water) enters the
fluid passageway inlet 221 at a third temperature and exits the
fluid passageway outlet 223 at a fourth temperature. Examples of
shells include, but are not limited to, clamshells or blister
packs. The pre-defined designs of the projections 220 can be used
to imprint a complementary design onto the membrane or bladder
thereby define a fluid passageway having an identical design as the
clamshell or blister pack. In single wall configurations, the
bladder or the blister packs are omitted, and the passageway 202 is
defined directly by the shell 218.
[0136] Referring to FIG. 14, an example of a blister pack type of
shell 222 is shown located adjacent a heat conductive sidewall 224
of a grey water conduit 225. The blister pack 222 includes a
thermal transfer surface 226 which lies in intimate contact with
the conduit 225. Although the example illustrated shows a grey
water conduits it is to be understood that this is an optional
feature and that the grey water may flow in direct contact with the
thermal transfer surface 226. A plurality of spaces 228 between
adjacent blisters 230 serves as the second fluid passageway for
cold water to flow therealong. One or more of the spaces 228 may
also comprise turbulators. The blister pack and clam shells can be
positioned so that metallic surfaces in contact with the grey water
conduit effectively extend with fin-like patterns into the cold
water passageway.
[0137] Referring now to FIGS. 15A and 15B, the heat exchange
apparatus 200 and the blister pack 222 can be located around a grey
water conduit. In the examples illustrated, the conduit includes
inwardly projecting square-shaped fins 232 and an outer shell 234,
which provides support for the components of the heat exchange
apparatus. In one example, the bladder 204 lies snug against the
outer wall of the conduit. In another example, the blister pack 222
lies in intimate contact with the sidewall 224. The blister pack
222 also defines the second fluid passageway. A drain hole 236 is
located in the shell 234 to provide venting of the first and second
fluid passageways away from the apparatus should either of the
blister pack or the bladder rupture.
[0138] Referring now to FIG. 16, an embodiment of a heat exchange
apparatus is shown generally illustrated at 300 in cross sectional
view. This heat exchange apparatus 300 comprises a conduit 302 with
an arcuate conduit member 304 and a fluid passageway 306. The
conduit 302 has first and second ends 308, 310, and an arcuate heat
exchange plate 312. The arcuate heat exchange plate 312 has first
and second connecting portions 313, 314 that are sealingly
connected to the respective first and second ends 308, 310 of the
conduit 302. The heat exchange plate 312 has first and second
thermal transfer surfaces 316, 318. An amount of grey water enters
the conduit 302 at a first temperature and contacts the first
thermal transfer surface 316 and exits the conduit 302 at a second
temperature. Generally speaking, this embodiment is useful for grey
water that covers the arcuate heat exchange plate 312 and reaches a
depth of several millimeters in the conduit 302. A fluid passageway
320 similar to the one described for the heat exchange apparatus
200 above can be used with this embodiment. In this example, the
fluid passageway 320 is in the form of a bladder and is located in
intimate contact with the second thermal transfer surface 318 of
the heat exchange plate 312. A cap 322, which is comparable to the
shell described above, may be located snug against the bladder so
as to form the fluid passageway 320. A drain hole 324 is located in
the cap 322 to drain water away to atmosphere in case the integrity
of the bladder or the conduit 302 is compromised. The ability to
vent cold or grey water is a requirement for certain plumbing
standards to prevent mixing of cold water with waste drain
water.
[0139] Referring now to FIGS. 17A, 17B, 18A and 18B, a household
shower system is shown generally at 400 and includes a P-Trap 402.
P-Traps are know to those skilled in the art. The heat exchange
apparatus 300 as described above, would be ideally suited for use
with any part of the P-Trap such that the heat conductive surface
of the heat exchange apparatus could be located in intimate contact
with a sidewall of the P-trap 402. Furthermore, any part of the
P-trap could be modified to include the heat exchange apparatus
300, as described above. In this case, the grey water exiting the
P-Trap would contact and flow along and against the heat exchanger
plate 312. Similarly, the heat exchange apparatus 10 and 76 could
be used in place of downstream portions of the P-trap. The heat
exchangers as described above and below may optionally include a
check valve 403. The check valve 403 is of the type known to those
skilled in the art. In the event of either a plumbing system
failure or maintenance, simultaneous to a grey water channel wall
failure of the heat exchanger, the check valve 403 will replace or
supplement the double wall membrane of the heat exchanger to
protect the water supply circuit of the building where the
installation is located.
[0140] As best illustrated in FIGS. 19A, 19B, 20A, 20B and 21, an
alternative embodiment of a heat exchange apparatus is illustrated
generally at 500. The heat exchange apparatus 500 comprises a one
piece insert 502 similar to the one piece insert 111 described
above. In this embodiment, however, the insert 502 includes a
multiple circuit 504 with a circumferentially disposed channel
member 506 located inside a shell 508. The shell 508 is larger than
the radius of the insert 502 and defines a void 510. The void 510
may be filled with an insulating media such as air or some other
suitable insulating material. The void 510 may also contain a fluid
to which the insert 502 can exchange thermal energy. The channel
member 506 includes hollow capillary fin members 512, each adjacent
fin member 512 having located therebetween a post 514. The insert
502 may include longitudinally disposed perforations 516, which
expose the fin members 512 to fluid circulating within the shell
508. The shell 508 protects and structurally reinforces the fin
members 512 either by mechanical contact or by additional
components such as turbulator 526 located between the insert 502
and the shell 508. Two end caps 520 are located at either end of
the insert 502 and seal the insert 502, the fin members 512 and the
void 510 in the shell 508. Tubing 522 and 524 carry the grey water
and cold water via manifolds (not shown) into and out of the heat
exchange apparatus 500. It is to be noted that either of the tubes
522 and 524 can be individually connected in series or in parallel
into one of the multiple circuits 504 as well as in contra flow or
parallel directions so as to obtain the desired contra flow or
parallel flow thermal performance characteristics of the heat
exchange apparatus 500. Additional turbulators 526, as described
above, are located between the insert 502 and the shell 508. The
turbulators 526 create turbulence in all fluid passing through the
void 510 and promote heat exchange on the fin members 512 through
the perforations 516. Furthermore, the turbulators 526 also provide
additional stiffening to the heat exchange apparatus 500.
[0141] As best illustrated in FIGS. 20A and 20B, a plurality of
inserts 502 may be grouped together into a larger heat exchange
apparatus 528. This heat exchange apparatus 528 is typically used
when high volume, high flow and high performance is required such
as for example in industrial applications. Typically, for these
applications rapid heating and cooling is necessary for technical
reasons, whether in grey water, pharmaceutical processes, steam
generation applications, food sterilization, or cleaning
applications such as in farming. Using the apparatus 528, rapid and
precise heat transfer from one fluid to another is achieved. The
apparatus 528 can be assembled with bundles of the inserts 502,
which are enclosed in sealed and pressurized vessels 530. The
vessels 530 include the multiple inserts 502 as well as multiple
turbulators 526. Fluid enters the void 510 via inlets 532 and exits
via outlets 534. The combination of series and parallel connections
of the grey water and cold water inlets and outlets of the fluid
circuits provides improved heat exchange performance in a variety
of circuit combinations and connections.
[0142] Built-in options may be included within any of the heat
exchange apparatuses described herein in order to increase overall
system performance and durability. These options include thin wall
elements; laminar flow disruptor elements; check valve systems; one
or more external level indicators; anti scaling capabilities such
as, for example, mechanical devices and passage configurations to
reduce scaling, anti-scaling coatings, vibration, chemical, and
electrical means; anti corrosion means such as, for example,
electrical, chemical, anodic, cathodic, and coatings; and water
hammer protection such as, for example, shock absorbers, flexible
or relatively soft and elastic cold water circuit components.
Additional features may include use of an insulating shell on the
systems and subsystems. System leaks and malfunctions can be
detected in a variety of ways using, for example, relative flow
measurement and/or pressure transducers and gauges located at
strategic points in the heat exchange apparatus. Extrudable
capillary fin geometry, as well as flow disruptors and other
structural elements can be made of glass or Pyrex. The heat
exchangers may be self draining in both horizontal and vertical
positions. Individual heat exchanger modules or cylinders or heat
exchanger bundles can be positioned at the top or at the bottom of
larger vessels, such as with the vessels 530 described above,
depending on heat exchange requirements in a given application. If
electric power is required for monitoring or control equipment,
power sources such as batteries, thermoelectric, or micro-turbines
can be advantageously used in combination or alone.
[0143] Referring to FIGS. 21A, 21B, 21C and 22A, an alternative
design of a heat exchange apparatus is shown generally at 600. The
apparatus 600 can be used in shower applications and can
advantageously be packaged into an enclosure of modest dimensions,
and easily inserted as a component of existing or new plumbing
systems, with or without a check valve (not shown). The apparatus
600 comprises a tray 602, a grey water area cover 604 and a channel
member 606. Two end plates 608 each include a grey water opening
610 are located at the ends of the channel member 606. The channel
member 606 includes an angled entry portion 612 and an angled exit
portion 614. The angled portions 612 and 614 are angled inwardly
away from the end plates 608. Cold water is communicated into and
out of the apparatus via cold water connectors 616 and flows along
a cold water passageway 618. As it is generally the case with the
other Heat Exchanger embodiments described above, grey water area
cover 604 may optionally include internal auger guiderails (not
shown) to allow the passage of a plumber's drain observation and
cleaning tools inserted into either of the two grey water openings
610, without interfering with the flow of grey water along the
channel member 606. The tray 602 includes cavities 620 and entry
and exit manifolds 622. Cold water turbulators (not shown) may be
located in the cavities 620 and inside the cold water passageways
618 between the cold water entry and exit manifolds 622. The tray
602 and the cover 604 may be combined into a single piece if
desired. The turbulators increase the thermal performance of the
system by creating turbulent flow within the cold water passageways
618. As best illustrated in FIG. 21C, when viewed in cross section,
the channel member 606 comprises a heat exchange wall 624 of
minimal thickness. The heat exchange wall 624 defines a plurality
of troughs 626, along which the grey water travels, and a
corresponding plurality of square topped peaks 628. Located
adjacent the heat exchange wall 624 is the cold water passageway
618. The heat exchange wall 624 corresponds to the distance
traveled by the heat from each of the troughs 626 to each of the
cold water passageways 618. This capillary configuration provides
exceptional heat exchange performance between the troughs 626 and
the cold water passageway 618. The very small thickness of the
capillary heat exchange wall 624, combined with very large heat
exchange surfaces can be achieved using specific geometries and
high strength materials such as, for example, stainless steel,
copper, gold, and the like, to form hollow fin members, leading to
higher thermal performance than those obtained when solid material
are used. It is well known in the art that thermal performance in
relatively low temperature cases, such as with the heat exchange
apparatuses described herein, thermal energy transfer performance
depends on the following factors: heat exchange area, physical
material properties (heat transfer rate), material thickness, flow
turbulence (convection) in each fluid, and thermal gradient present
between the two fluids. The heat exchange apparatus 600
advantageously uses a corrugated foil to form the thin heat
exchange wall surface 624 with a large surface area. A stiffening
surface 630 is attached to the lower end of the troughs 626 at
fastening locations 632 using fastening means such as, for example,
brazing, seam welding or spot welding. This allows the location of
the channel member 606 into a vessel that can be pressurized at
will, while maximizing heat exchange surfaces of the fin
members.
[0144] Referring now to FIG. 22B, the grey water passageway can
enter the heat exchange apparatus at two distinct levels, as
indicated by arrows 1 and 2 with respect to grey water channel
planes 627, 629. Arrow 2 above the higher plane 629 advantageously
promotes debris passage in the grey water channel, albeit at the
expense of drainage system slope disruption when installed in
existing drainage systems such as during renovations. Also, the
exit of the apparatus can be done in two different configurations
with respect to the plane 627, the exit being either coplanar with
the grey water channel or below, as illustrated by arrows 3 and
4.
Blade-Type Heat Exchange Apparatus
[0145] It is to be noted that in the heat exchange apparatuses 10,
76, 100, 200, 300, 500, and 600 described above, the grey water was
described as the "first fluid" and the cold water was described as
the "second fluid". In the following embodiments, for ease of
description of the heat exchangers, the cold water is now referred
to as the "first fluid" and the grey water is now referred to as
the "second fluid"
[0146] As best illustrated in FIG. 23, we have now designed a
so-called blade-type heat exchange apparatus, which comprises one
or more hollow blade members 638, each blade member having a first
fluid (cold water) inlet 639 and a first fluid outlet 641 and a
first fluid passageway 643 for a first fluid extending
therebetween. The hollow blade members 638 are sized and shaped to
be located in a second fluid passageway 645 for a second fluid
(grey water). The blade members 638 are configured to enhance
thermal energy transfer between the fluids as they flow along their
respective passageways. The blade members 638 can be each
manufactured from suitably formed thin sheet material, and spot or
seam welded, or brazed and individually assembled. A plurality of
hollow blade members 638 can be arranged substantially parallel to
each other and assembled as a heat exchange apparatus in which the
blade members 638 are connected together using fasteners 640. Each
blade member 638 can be removed, tested for quality and
re-assembled in the heat exchange apparatus. Also included is a
cold water manifold 622 having a plurality of slots 623. The blade
members 638 can also be assembled using mechanical components such
as O-rings and gaskets, or they can be fastened by more permanent
means, such as welding or brazing. In the latter case, the heat
exchange apparatus can be made exclusively from welded or brazed
thin sheet material, using well known high volume manufacturing
techniques and quality control procedures in order to provide a
high quality heat transfer and a durable system. Vents to the
atmosphere may also be included in the assembly such as via an
opening (not shown) adjacent to the manifolds 622.
[0147] Referring now to FIGS. 24A and 24B, the hollow blade member
638 includes a plurality of projections 649 located either on an
inner wall surface 641a or on an outer wall surface 645 or on both
surfaces of the blade member 638. The projections 649 can be
located on a portion of the aforesaid surfaces or, as illustrated,
can be located along the entire length of the outer surface 645 of
the blade member 638. The projections 649 can be any shape such as
ridges, chevrons, pads, discrete nubbins and the like. Furthermore,
the projections 649 may themselves comprise well defined surface
roughness and additionally include microscopic projections
extending therefrom. The projections 649 can be embossed on the
surfaces 641a or 645, or they may be added to a smooth surface of
the blade member. Surface texture (roughness) increases the
frictional forces acting between the fluid and the surface leading
to higher turbulence. For household and industrial applications,
the cold water passageway 643 of each blade member 638 typically
operates under pressures of approximately 500-100 psi for a
duration of about thirty years, therefore it is desirable to
reinforce the blade members 638 to increase their lifespan. The
projections 649 provide increased burst resistance to the
passageways 643 by reinforcing and stiffening the blade members
638. Furthermore, the reinforcement that the projections 649
provide allows the use of very thin walls, hence providing improved
thermal exchange performance. Moreover, the projections 649 can be
used to align the cold water passageways among themselves within
the assembly, and with an outer shell 647. Advantageously, the
projections 649 control the fluid flow and enhance the thermal
energy transfer between the grey water and the cold water by
promoting and sustaining turbulent flow in the grey water or the
cold water, or both, as they travel along their respective
passageways. Additionally, the projections 649 enhance the thermal
energy transfer between the grey water and the cold water by
disrupting laminar flow and causing shear in the grey water, the
cold water or both. The projections 649 can be incorporated to
increase thermal performance, by modifying and controlling the flow
of either or both fluids by a suitable configuration, while
determining, aligning, and maintaining the geometry of the
individual heat exchange blade members as well as the geometry of
their assembly. Additionally, the projections 649 may be extended
from the blades 638 into the top of the grey water passageway (not
shown) to help guide the passage of plumbing tools traversing the
heat exchanger during maintenance, repair, or inspection activity.
Also, alignment and sealing mechanisms and devices either directly
or indirectly involved with the thermal energy exchange of the heat
exchange apparatus, may be used and are constructed of metallic or
non-metallic materials. Various fastening systems such as welding,
brazing, adhesion, cohesion, mechanical fasteners and seals and the
like can be used to position, assemble and attach turbulator
sub-system components into the heat exchange apparatus. An
additional advantage of the projections 649 is that they provide
cold water anti scaling action and grey water anti clogging action
created through suitable cold water and grey water water speed and
water direction management geometries, which in turn increases the
useful life of the blade members and decrease maintenance
needs.
[0148] As best illustrated in FIGS. 25A and 25B, the location of
the projections 649 along the surfaces of the blade members 638
causes induction of flow patterns as shown by arrows 642. The
projections 649, in this case, ridges, are orientated in such as
manner that when cold water passes through the blade member 638 it
is de-laminated as well as rotated as shown by the arrows 642 so as
to generally induce shear and turbulent flow in the cold water
passageway 643. Similarly, in a contraflow configuration, rotation
is also induced in the grey water channel by the same shaped
projections 649, as illustrated by arrows 644, which enhances
turbulent flow in the grey water. The ridges 649 can be stamped
into or out of the flat surface of the blade 638 or they can be
added as sub-systems as described above.
[0149] Referring now to FIG. 26, an embodiment of a high pressure
blade type heat exchange apparatus 800 is shown which comprises a
bundle 801 of hollow blade members 802 formed and stamped from
stainless steel sheet and welded and connected through a manifold
to form the apparatus, which is then assembled inside a low
pressure, atmospheric drain system envelope 803 through which grey
water 804 flows by gravity. Each blade member 802 is made from a
stainless steel sheet that is formed to obtain a hollow "flat"
tubular shaped passageway where the general shape is other than
cylindrical. Each blade member 802 includes a plurality of angled
ridges 805 or other tubulators located on at least a portion of a
blade surface, and/or as an alternative turbulators may be inserted
inside the blade or positioned outside the blade as a discrete
mechanical component.
[0150] Referring now to FIGS. 27, 28A and 28B, it is possible to
increase the performance of the blade type heat exchange apparatus
described herein by using blade members, which are based on
cylindrical, corrugated heat exchanger piping (also known as "club
grips"). As illustrated, a number of designs of "club grips" are
known in the art and have wall exchanger surface dimensions that
are maximized by the surface patterns. The patterns provide
internal and external helical or "threaded screw motion" of the
fluids resulting in fluid rotation. However, club grips lack the
ability to maximize fluid shear and fluid turbulence. As best
illustrated in FIGS. 28A and 28B, our blade design is based on a
flattened club grip and provides inwardly disposed projections 810,
which project into the cold water passageway 806, and outwardly
disposed projections 812, which project outward, typically by
stamping during the manufacturing process, from flat walls 814, and
which provides unexpectedly high chaotic blade passageway geometry,
leading to high levels of shear and turbulence generated in the
displaced fluids. Seam welds 816 are located along the length of
the blade member 802. Additional indentation shapes such as sharp
bends and corrugations are also permissible, as are additional
components (not shown) that can be welded onto either one or both
sides of the originally flat and smooth heat exchanger walls (or by
a combination of both) in order to delaminate and agitate the flow
(i.e. induce shear and turbulence) of cold water flowing in the
cold water passageway 806, as well as grey water flowing outside
the blade member 802 and in contact with the outer surface of the
blade member 802. It is to be noted that the chaotic helical cross
flow motion of fluids is obtained in the pressurized fluid, such as
the cold water flowing in the cold water passageway and also in the
atmospheric fluid, such as the grey water flowing externally of the
blade member 802. It is to be noted that the helical "club grips",
typically made from copper tubing, and other similar style "round"
tubing may also be employed in the high pressure apparatus 800,
whether straight or with 90 degrees bent ends, in place of the
"corrugated flat wall" stainless steel hollow blade members.
Additionally, turbulators can be inserted into the blade members
802.
[0151] It is known that greater thermal transfer performance and
ease of manufacturing are obtained by using a thin formed sheet
material in the manufacturing process of the heat exchanger
components. Using thin wall stainless steel composite sheets of
approximately 0.015'' to 0.035'' thicknesses in heat exchanger
apparatuses provides low resistance to burst due to possible
excessive high internal cold water pressure, such as those commonly
used in household or industrial plumbing systems.
[0152] Referring now to FIGS. 28B and 29, an example of a stiffened
geometrical heat exchange blade member, which includes fasteners
820 to maintain the structural integrity of the blade member. It is
therefore useful to use geometries of wall stiffening corrugation
as well as fasteners 820 where they can self reinforce the
structure of the pressurized cold water passageway. The fasteners
820 may be rivets, adhesives, or seam welds 816, as described
above, as well as spot welds. In order to maximize thermal energy
transfer as well as structural parameters, the internal projections
810 and the external projections 812 with respect to the originally
flat blade surfaces 814 and multiple blades located together may
intimately contact each other for added in a fastened confirmation
structural stability. The blade members 802 can be manufactured by
stamping, bending and crimping an originally flat metal sheet. This
can be advantageous when compared to using relatively slow linear
welding to produce the seam weld 816. It is possible to use a
combination of high speed edge crimping methods and tools to
produce crimped areas 824 in the sheet 814. Methods and tools, such
as those used to produce canned goods in the food industry can be
used, with the use of optional adhesives or sealants to ensure seal
intergrity where required. One such particularly useful technique,
when long and straight seams are fabricated, is named "Swage Roll",
in which the assembly of two sheets of metal is done by using
compression wheels that shape and form a sealed seam between the
two sheet metal surfaces. Progressive dies are also used for even
faster forming and sealing assembly of such parts.
Double Wall Construction
[0153] Cross-connection of plumbing devices is ruled by strict, but
variable, local regulations, where grey water and fresh cold water
are present within the same heat exchanger apparatus. Universally,
a double wall design is preferred over any other protection means
to prevent fresh water contamination by grey water in the event of
system failure, such as if the heat exchanger wall is ruptured or
pierced.
[0154] Referring now to FIGS. 30A and 30B, for single walled
construction of a hollow blade member, that is, one without a
lining such as a bladder, the external wall surfaces 840 and the
internal wall surfaces 842 are the thermal transfer surfaces of the
blade member and provide two work surfaces. For the double wall
blade construction, four heat exchange "work" surfaces are
available. In the double wall construction, as illustrated, the
internal wall (bladder) 850 includes an inner thermal transfer
surface 852 and an outer thermal transfer surface 854, and the
outer wall includes the internal wall surface 842 and the external
wall surface 840. An inter-surface space 856 is a void located
between surfaces 842 and 854. The space 856 creates the separation
between the blade surfaces in the double wall configuration, and
allows atmospheric venting via a vent 860. The bladder 850
optionally includes a sealed wall overlap portion 862 located
adjacent the vent 860. The overlap portion 862 is sealed using a
weld or adhesive. The bladder 850 further includes a cold water
inlet 864 and a warmed water outlet 866. The bladder 850 is
constructed of a relatively flexible, possibly pre-crushed and
later pressure expanded, micro-corrugated, folded, ribbed or
patterned material, with a typical wall thickness of between 0.001
inch to 0.015 inch. A metallic material is preferred, but other
wall compositions are contemplated. As best illustrated in FIG.
30B, the double wall configuration includes macroscopic peaks (or
ridges) 812 and a macroscopic recesses 810. Microscopic textures
844a and 844b are located on respectively the external and internal
surfaces 840 and 842, and microscopic textures 845a and 845b are
located respectively on the external and internal surfaces 854 and
852. The microscopic textures provide additional surface turbulence
to the fluids in motion.
[0155] The shell 802 of the blade assembly is essentially the same
as in the single wall construction described above except for the
fact that a plurality of atmospheric venting ports 860 are present
in order to immediately evacuate any fluid penetrating into the
defined inter-surface zone space 856. Leaking fluid immediately
evacuates to the atmosphere either by gravity or by water pressure,
whichever is greater, and depending on the origin of the leak.
Leaking fluid evacuation is, however, increased by the textures
described above. The inner pressure of the cold water compresses
the bladder 850 with great force against the pressure bearing
surface of the external shell 802 to provide acceptable heat
transfer rates between the grey water and cold water. A suitable
thermal paste or porous filler material may be optionally used to
fill the inter-surface zone space 856 to further enhance the
thermal transfer rate.
[0156] Blade surface dimensions and shapes, areas and thicknesses,
wall and surface compositions and the nature of the material used
to construct the blades, as well as surface treatment, macroscopic
and microscopic surface shape and texture, all determine the
blade's ability to transfer heat and become non-adhesive, or
self-cleaning. Additionally, non adhesion of dirt, soap, scum, hair
and debris to all heat exchanger walls and surface features, can be
controlled by fluid flow management by fluid velocity and surface
turbulence control, as well as chemical anti-fouling and surfaces
geometrical self-cleaning properties.
[0157] Referring again to FIGS. 25A, 25B, 30A, 30B and 31A, blade
wall surface geometry controls and generates both deep
(macroscopic) and surface (microscopic) directional turbulence
mechanisms in given fluid dynamic conditions, resulting in combined
and mutually reinforced convection patterns 642, 644, and 858,
which enhance fluid-to-fluid heat transfer rate and performance.
The increased heat transfer rate is obtained by the sum of a
surface (or microscopic) fluid velocity caused by microscopic fluid
surface textures 844a, 844b, 845a and 845b, which act as
turbulators, on the heat exchanger walls as well as those
turbulences created macroscopically as shown by the convention
patterns 642, 644. The microscopic textures 844a, 844b, 845a and
845b are used to further delaminate the fluids circulating within
the larger internal and external projections (ribs or ridges) 810,
812. A variety of microscopic and macroscopic shapes and textures
are contemplated and may be combined to achieve maximum turbulence.
Within the space 856, the textures 844a, 844b, 845a and 845b are
used to increase atmospheric venting efficiency, by providing an
easier path to eventual leaks to the atmospheric vents 860.
[0158] Referring again to FIG. 30B, 31A and now FIGS. 32A and 32B,
different patterns and strategies can be used or combined on
different sections of the blades as well as individual fins, as
described above, to maximize heat transfer rates for the whole
blade assembly. In one example, a "golf ball icosahedron" surface
pattern 832 in a specific location, such as on the nose of the
external surface 840 of the blade, can be used to greatly reduce
the accumulation of material, such as hair, at this particularly
critical location.
Blade Member Design Variations
[0159] It should be noted that the wall materials, shapes,
thicknesses, widths and heights, surface textures and cross
sections of the blade members and of their inner components do not
need to be symmetrical, fixed or constant in any manner with
respect to given geometrical axes of the assembly. For example, it
is possible to use a blade with a large "front-end" and a slimmer
"tail-end", in order to precisely control heat transfer surface
dimensions and corresponding heat transfer rates between two fluids
in cross-flow configurations. Variations where the effective cross
section and the height and width of a blade or inter-blade spacing
varies according to a mathematical function along the length of the
blade or blade bundle assemblies are also contemplated to further
enhance performance.
[0160] One of the advantages of the blade assembly is that whole
assembly or even an individual blade can be removed for cleaning,
inspection and maintenance and replaced if necessary. Moreover, the
grey water can flow unfiltered along its passageway. Specialized
cleaning tools such as wire brushes or enzyme or bacteria based
solutions, as well as chemical cleaners, or combinations thereof
can be periodically applied via the floor drain of the shower in
order to dissolve any dirt accumulated over time on the heat
exchanger grey water walls within the drainage system in order to
maintain optimal said grey water flow characteristics and thermal
transfer rates of the system, without affecting the environment or
the drainage components in any significant matter. A strainer
located at the grey water floor drain will also advantageously
reduce debris entering the drain.
[0161] Referring now to FIGS. 33, 34, and 35, a plurality of blade
members 802 are illustrated for use in a blade-type heat exchanger
868. The blade members 802 are located in a housing 870 in which a
lower portion 874 of the housing 870 is optionally open to allow
atmospheric venting in double wall configurations. The of the
manifolds 622 are located substantially lower than the lower plane
627 of the grey water passageway and are also optionally open to
allow atmospheric venting. The blade members 802 are located
substantially parallel to each other with gaps 876 between each
blade 802 which define a grey water passageway 847. In the
embodiment shown, each blade member 802 has first and second walls
853 and 855, each with an inner thermal transfer surface 849 and an
outer thermal transfer surface 851. Each wall 853, 855 includes a
plurality of ridges and recesses 844, 845 located thereon. As
illustrated, the ridges and recesses 844, 845 are disposed
diagonally relative to a longitudinal axis 878 of the blade member
802 in one direction along the first wall 853 and disposed in
opposite directions along the second wall 855 relative to the first
wall. This arrangement of ridges and recessed defines a
"criss-cross" pattern, when viewed from the side in which a central
cross area 857 is a location where opposing ridge of opposing inner
thermal transfer surfaces make contact. Although not illustrated,
it is to be understood that similar ridges and recesses may also be
located in the grey water passageway. This alternating pattern of
ridges and recesses induces high levels of shear within the fluids
leading to rapidly developing turbulent flow conditions in both the
cold water and the grey water by causing cross flow near or at the
central cross area 857, and on the planes located in the centre of
the fluid passageways.
[0162] When the ridges and recesses 844, 845 are disposed
diagonally, the relative "criss cross" configuration of the ridges
on the walls of the blade members causes high levels of fluid
shear, turbulence and cross flow within both the grey water and the
cold water. However, it is to be understood that the ridges and
recesses may be orientated at any angle relative to the
longitudinal axis of the blade member, and may also interdigitate,
or contact with each other at the central cross area, or they may
be spaced apart from each other. In the example shown, the
manifolds 622 for receiving the cold water are disposed generally
orthogonal to the longitudinal axis 878 of the blade members and
downwardly away from the longitudinal axis, as best shown in FIG.
33. In this example, the housing 870 together with the plurality of
blade members 802 can be located in a tray 879 through which the
grey water is flowing or the blade members 802 can be manufactured
as a unitary body with the tray located near the lower portion of
the blade members 802. The grey water passageway 847 dimensions
will depend largely on the nature of the debris that is expected to
be found in the grey water as it flows along the passageway 847 as
well as on the fluid characteristics, such as volume, velocity and
viscosity, expected in normal operating conditions also in order to
optimize heat exchanger performance. A screen (not shown) can be
used over the entrance to the grey water passageway 847 to prevent
debris from entering the grey water passageway 847. The screen can
be located before the P-trap in a household shower/bath system.
Moreover, the shape and location of each blade member 802 can be
changed to allow passage of a variety of debris types and fluid
hydrodynamic characteristics. Thus, the grey water flowing along
its passageway 847 contacts the outer thermal surfaces of the
plurality of blade members 802 such that turbulence is induced in
the grey water, while simultaneously, turbulent cold water moving
along the cold water passageway contacts the inner thermal surface
thereby allowing for efficient thermal energy transfer across the
walls of the blade members 802.
[0163] Ridges can be evenly spaced and shaped (depth and 3D forms)
or follow a pattern defined mathematically along the blade walls,
to increase blade surfaces and generate turbulent flow for various
grey water and cold water flow conditions, thereby maximizing heat
transfer. Fluid shear inducing ridges may be located at the bottom
of the grey water passageway 847. Additionally, scale-type/shaped
ridges can be used to create turbulent flow at the bottom of the
grey water passageway 847, with a reduced risk for clogging. The
same scales structure may be useful for location on the periphery
of vertical heat exchange embodiment, as described below.
[0164] In the example illustrated in FIG. 36, a bottom tray 880 is
designed to receive a plurality of the blade members 802 in a
pre-defined grey water passageway 881. In the example illustrated,
the manifolds 622 are disposed upwardly away from the longitudinal
axis 878 of the blade members 802. This design aids the location of
the blade members 802 into the tray 880. This design is
particularly well suited large laundry facilities such as those
used in hospitals where a large of volume grey water is generated
and flows in open channels when discarded at high temperatures. The
heat exchangers of this design can be easily retrofitted into the
existing plumbing and easily maintained and cleaned by lifting the
blade member assemblies from the grey water passageway.
[0165] As best illustrated in FIGS. 373 to 40, the scale of the
design may be increased substantially to include a plurality of
blade members 882 of larger dimensions, namely in increased height
dimensions leading to a further theoretical increase in convective
heat transfer performance. A housing 884 is designed to accommodate
the larger blade members 882 and includes inlet and outlet grey
water pipes 885, 886 and inlet and outlet cold water pipes 888,
890. The housing 884 includes a removable upper portion 892, which
allows for easy access to the blade members 882. Referring now to
FIG. 39, the larger dimension blade member 882 include a plurality
of ridges and recesses 894, which cover substantially the entire
surface areas of each inner and outer sidewall of each blade
member. For ease of illustration, only one outer sidewall is shown
in FIG. 46. As above, the criss-cross pattern of ridges (ribs)
causes shear and turbulence in the flow of both the grey water and
the cold water traveling along the internal and external portions
of the blade. The pattern of ridges may include other previously
mentioned shapes and may comprise combinations of them. The
orientation of the grey water flow may be orthogonal to the flow if
the cold water as is illustrated by the location of the grey water
inlet and outlet pipes 885, 886 in FIG. 40. Additionally, a
plurality of spot weld points 896 and/or seam welds 898 are located
to fasten and seal each sidewall of the blade members together. If
a double wall design is used, the welds can pass through the
opening in the bladder, which is sealed around the punctured holes
to maintain integrity of the double wall. Additional features of
the larger blades 882 include a plurality of flow management
disrupters 899 located along the edges of the blades 882.
[0166] In the previously described examples of the blade-like heat
exchange apparatus, the manifolds are disposed downwardly away from
the longitudinal axis 878 of the blades to facilitate maintenance.
This design is for use in household shower arrangements in which
water typically drains at 10 litres/hour. For commercial
applications, however, the manifolds may be disposed upwardly away
from the longitudinal axis 878 of the blades. In larger
applications, the larger blades are rigidified by welds and can
also provide a double wall arrangement. The bladder is punctured
and sealed around each structural weld. Moreover, if required, a
section of the blade can be enlarged by adding additional sections
of blade thereto. The additional blade sections can be embossed
with flow disrupters. Alternatively, one can use a turbulator
insert to induce flow turbulence inside the blades.
[0167] Referring now to FIGS. 41, 42, 43, 44A and 44B, another
example of a heat exchange apparatus is shown generally at 900 and
is particularly useful, but not limited to applications when used
in a vertical orientation, that is, the apparatus is disposed
generally orthogonal to the ground. In this design, a housing 902
is generally tube-like and includes a central grey water conduit
904, around which is disposed a cold water passageway 906 having an
inlet 908 and an outlet 910. The cold water passageway 906 includes
a double "slinky" turbulator 912 which is modeled on the wire
"slinky" children's toy, which efficiently generates shear forces
within the fluid when the slinkies are arranged in a clockwise and
counter clockwise configuration producing a criss cross pattern
such as the one illustrated. Also, slinkies are highly flexible and
will allow the heat exchange apparatus to be used in locations that
require bending of the grey water and cold water passageways. One
wire of the slinky 914 is coiled around the grey water passageway
in clockwise orientation and the other wire 916 of the slinky is
coiled in a counter clockwise orientation relative to the
longitudinal axis of the grey water conduit 904. As in a hollow
blade 802, 638 or 882 the "double helical" criss cross arrangement
of the two slinky wires creates a turbulator and promotes high
turbulence in the cold water flowing downwardly or upwardly such
that the cold water is constantly sheared all within a single
cavity located around the grey water passageway, such as that
described for within the blade member 802. Additionally, where each
of the slinky wires 914, 916 crosses each other, a cross area 911
is formed which is similar to the central cross area 857 described
above for the ridges 844. Cold water when following the path
defined by the slinky wire 914 travels in one direction, and
simultaneously when follows the path defined by the slinky wire 916
travels in an orthogonal direction, very high shear and turbulence
is induced within the cold water passageway 906. Since this highly
turbulated cold water is trapped in the cavity between the housing
902 and the grey water conduit 904, highly efficient heat exchange
occurs between the optionally smooth thermal transfer surfaces of
the conduit 904. Again, the shearing effects is similar to the one
that is caused by the criss cross surfaces of the design as
described above. This heat exchange design advantageously allows
the design of compact and pressure self supporting heat exchange
apparatuses, which can be used either with the single wall
configuration as described or with a bladder to provide the double
wall capability. For increased heat exchange performance, a
turbulator 108 can be located inside the grey water passageway
904.
[0168] Referring now to FIGS. 45A to 45C, a mesh type turbulator
918 is shown in the heat exchanger. The mesh type turbulator 918
includes a plurality of criss crosses 911, which are defined by a
first plurality of clockwise helically orientated wires and a
plurality of other helical wires disposed counterclockwise to the
first plurality of wires. Although not illustrated, the mesh may
also include a plurality of orthogonally orientated wires. The
turbulator mesh can comprise of a variety or a combination of shear
inducing short path turbulent flow inducing surfaces such as, but
not limited to, perforation open cell porous medica, molded,
composite, stacked, slit, interdigitated, semi-rigid and
symmetrical, textured elements. As described above, turbulators may
be inserted in the grey water passageway or also in the cold water
passageway.
[0169] An alternative to the double helical wire criss cross
turbulator is a double slinky wire criss cross turbulator which
consists of an insertion of a single clockwise slinky wire into a
counter-clockwise patterned corrugated tube (club grip) or even
into an axial internal finned tube or any other criss cross
generating wire pattern.
Compact Heat Exchangers
[0170] As best illustrated in FIGS. 46A to 46H, and 47A and B and
51, a compact heat exchange apparatus 1000 is a generally arcuate
blade, where criss cross turbulator 1001 is located in a cold water
passageway or could be imprinted on the surface of the blade as
described above for the other embodiments. The criss cross
turbulator 1001 includes a series of helically and diagonally
disposed ribs 1006 and 1006.
[0171] The suitably dimensioned blade can be located inside a
tubular pipe 1002 for heat exchange of calibrated or known volumes
of grey water and cold water. The heat exchange apparatus 1000 can
also be located externally of the tubular pipe 1002. In another
example, the tubular pipe 1002 may be manufactured such that the
arcuate heat exchange apparatus is integral with the pipe
sidewall.
[0172] The arcuate blade heat exchanger apparatus 1000 can be used
singly for applications in which a small volume of grey water is
traveling along the pipe 1002 and located adjacent the area of the
pipe where heat is to be exchanged. The arcuate design of the heat
exchange apparatus means that multiple arcuate heat exchange
apparatuses can be used to fully or partially encase the pipe 1002.
Two or three or more arcuate blade heat exchange apparatuses 1000
can be used to fully encase the pipe 1002. Also, if the arcuate
blades are located inside the pipe, the arcuate blades are
typically constructed from metal with the turbulators 1001 located
on one or both sides of the blade. If located outside the pipe, the
blade is manufactured with metal on one side and the turbulators
1001 on one or both sides or inserted. Metal surfaces on both sides
of the arcuate blade along with turbulators is a favoured
construction for the blades.
[0173] Sections of the compact designs are particularly useful for
drain pipe heat exchange applications where drains are installed in
a position other than vertical relative to the ground, and where
one side of the pipe carries the energy to be exchanged.
[0174] Although in the examples described above, hollow, planar
blades and hollow arcuate blades have been described, it is to be
understood that the blades can be of any three-dimensional shape,
such as cylindrical, conical, triangular, disk-like, and the like.
Moreover, we also contemplate that planar hollow blades having
surface projections and recesses can be formed into a tube, the
tube being optionally open along the longitudinal axis in order to
be attached and clamped onto a central grey water drain.
[0175] Referring now to FIG. 46, a control system 700 may be used
to monitor or to control the function of any of the heat exchange
apparatuses described herein. This is particularly useful if the
heat exchange apparatus is to be imbedded in a wall or behind an
inaccessible structure. Moreover, if multiple heat exchangers are
being used throughout a building, the ability to monitor the
functions such as the performance or the energy transfer of the
individual heat exchangers is advantageous. Thus, the system 700
may include a unidirectional or a bi-directional data transmission
and communication, data acquisition function. The physiochemical
properties of the fluids flowing in the heat exchangers can be
monitored by the control system 700 and any changes to such can be
monitored and a user alerted if any deleterious changes occur. This
is particularly useful in heat exchangers that are used in the
food, pharmaceutical, farming and water treatment industries. The
control system 700 is constructed and programmed, and can be a
wireless system, as well as conventional wire assisted system or
alternatively, a combination of both and individually embedded or
externally integrated to one or more heat exchanger systems. The
system 700 can be manually operated, or computer controlled using
telemetric applications involving well-known standard process
operation parameters measurement, analysis and data acquisition at
strategic locations such as, but not limited to entry and exit
points. Additional parameters that can be measured and monitored
include fluid viscosities, fluid temperatures, fluid pH, fluid
hardness, fluid ppm data, fluid mineral and chemical content, fluid
lighting and imaging, fluid chromatography, fluid collection and
sampling, fluid aeration, fluid velocity and flow rate, fluid
pressure, fluid turbulence, heat exchanger sub-systems and overall
system integrity and malfunction detection, heat exchanger system
overall performance, heat exchanger instantaneous workload as well
as efficiency computations. Additionally, rather than measuring
within the fluid or acting upon the fluid, measurements and
monitoring can be carried out within the system and sub-system
components such as the heat exchanger walls, discrete system
components, nozzles, sensors, actuators, fluid passageways,
interstitial wall components, additional sub-systems. Fluid
physical properties can be monitored, data acquisition can be made,
and modifications to the heat exchange system operation can also be
made. Such modifications include, but are not limited to,
activation of sensors and actuators, as well as passive component
temperatures, vacuum levels, pressure levels, vibration, moisture
as well as other process related operating parameters related to
the integrity and the performance of the heat exchanger system and
other sub-systems. Manually operated, or computer controlled
process control applications can include the operation and
actuation of valves and sensors in order to modify working
parameters of the heat exchanger system as well as actively or
passively modifying the fluid physical properties. Also, the system
700 can maintain or optimize the operation of individual or
remotely located heat exchange apparatuses in a larger heat
exchange circuit by varying the individual workload or maintenance
requirements over time, or by modifying the fluids for a subsequent
process in terms of physical or chemical property requirement.
[0176] In addition to monitoring the heat exchange apparatuses, it
is possible to use the system 700 to monitor and compute tariffs
and fees based on heat exchanger workload and efficiency or other
measurable physical workloads performed by the systems over time.
Energy savings provided by the heat exchanger and peripheral
systems can be evaluated, charged and billed to the user.
OTHER EMBODIMENTS
[0177] From the foregoing description, it will be apparent to one
of ordinary skill in the art that variations and modifications may
be made to the invention described herein to adapt it to various
usages and conditions. Such embodiments are also within the scope
of the present invention.
* * * * *