U.S. patent number 3,666,007 [Application Number 05/020,302] was granted by the patent office on 1972-05-30 for apparatus for effecting continuous and simultaneous transfer of heat and moisture between two air streams.
This patent grant is currently assigned to Mitsubishi Denki Kabushiki Kaisha. Invention is credited to Akima Kamiya, Shigeo Muramatsu, Nin Ogawa, Atsushi Oguri, Masataka Yoshino.
United States Patent |
3,666,007 |
Yoshino , et al. |
May 30, 1972 |
APPARATUS FOR EFFECTING CONTINUOUS AND SIMULTANEOUS TRANSFER OF
HEAT AND MOISTURE BETWEEN TWO AIR STREAMS
Abstract
Apparatus for effecting continuous and simultaneous transfer of
both heat and moisture between two air streams comprises a housing
having therein a plurality of heat and moisture transfer surfaces
statically disposed in superposed and spaced-apart relationship
defining therebetween static flow paths, and means for including
air from one locale through alternate ones of the flow paths to
another locale and for discharging air from said another locale
through the remaining flow paths to said one locale. The heat and
moisture transfer surfaces are each composed of a material, such as
Japanese paper, which is sufficiently heat conductive and permeable
to moisture to continuously and simultaneously effect both heat and
moisture exchange between the inducted and discharged air.
Inventors: |
Yoshino; Masataka (Naka-sugawa,
JA), Kamiya; Akima (Naka-sugawa, JA),
Ogawa; Nin (Naka-sugawa, JA), Oguri; Atsushi
(Naka-sugawa, JA), Muramatsu; Shigeo (Kamakura,
JA) |
Assignee: |
Mitsubishi Denki Kabushiki
Kaisha (Tokyo, JA)
|
Family
ID: |
21797852 |
Appl.
No.: |
05/020,302 |
Filed: |
March 17, 1970 |
Foreign Application Priority Data
|
|
|
|
|
Mar 20, 1969 [JA] |
|
|
44/21477 |
Apr 30, 1969 [JA] |
|
|
44/33375 |
Apr 30, 1969 [JA] |
|
|
44/33376 |
Apr 30, 1969 [JA] |
|
|
44/39556 |
May 8, 1969 [JA] |
|
|
44/35420 |
May 12, 1969 [JA] |
|
|
44/43466 |
Aug 15, 1969 [JA] |
|
|
44/77524 |
Aug 20, 1969 [JA] |
|
|
44/79027 |
Nov 4, 1969 [JA] |
|
|
44/88311 |
|
Current U.S.
Class: |
96/144; 165/59;
165/909; 165/122; 165/166; 96/11 |
Current CPC
Class: |
B60H
1/00021 (20130101); B60H 1/00335 (20130101); F24F
3/147 (20130101); Y10S 165/909 (20130101); F24F
2003/1464 (20130101) |
Current International
Class: |
B60H
1/00 (20060101); F24F 3/147 (20060101); F24F
3/12 (20060101); F28f 003/00 () |
Field of
Search: |
;165/157,166,57,122,165
;62/262,314 ;55/34,390 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Sprague; Kenneth W.
Claims
What we claim is:
1. A ventilating device for ventilating a room comprising, in
combination: a box-shaped housing including a suction port and an
exhaust port facing each of the interior and exterior portions of a
room to be ventilated; a plurality of partitions within said
housing defining a suction passage and an exhaust passage each
communicating one suction port and one exhaust port and wherein
said suction passage and exhaust passage open into a common
heat-exchange space; a suction fan disposed in said suction passage
operable to form a suction air stream along said suction passage;
an exhaust fan disposed in said exhaust passage operable to form an
exhaust air stream along said exhaust passage; and combined
heat-moisture transfer means disposed within said common
heat-exchange space for effecting continuous and simultaneous
transfer of heat and moisture between the suction air stream and
the exhaust air stream, said combined heat-moisture transfer means
including a plurality of laminations composed of a material
sufficiently thermally conductive and permeable to moisture to
effect continuous and simultaneous transfer therethrough of both
heat and moisture, said plurality of laminations being superposed
on one another at predetermined substantially equal intervals
defining therebetween a plurality of gaps, and means for
communicating alternate ones of gaps formed between said
laminations with said suction passage and the remaining gaps with
said exhaust passage.
2. A ventilating device as claimed in claim 1 wherein each of said
fans is of a centrifugal type.
3. A ventilating device as claimed in claim 1 wherein each of said
fans is of a cross flow type.
4. A ventilating device as claimed in claim 1 wherein said
laminations of said heat exchanger are composed of Japanese
paper.
5. A ventilating device as claimed in claim 1 wherein said suction
and exhaust fans are of a centrifugal type including a multi-vane
impeller and disposed so as to render said multi-vane impellers
coaxial with each other and wherein a common electric motor for
driving said fans is provided including a driving shaft connected
at the opposite ends to respective ones of said multi-vane
impellers.
6. A ventilating device as claimed in claim 1 wherein said suction
and exhaust fans are of a centrifugal type including a multi-vane
impeller and disposed so as to render said multi-vane impellers
coaxial with each other, a common electric motor including a
driving shaft connected at the opposite ends to said multi-vane
impellers respectively, and wherein said centrifugal suction fan is
disposed between said suction port communicating with said suction
passage and said heat-exchange space while said centrifugal exhaust
fan is the same in output as said suction fan and disposed between
said suction port communicating with said exhaust passage and said
heat-exchange space.
7. A ventilating device as claimed in claim 1 wherein said housing
includes an opening near to the interior of the room, and a front
decorated panel detachably closing said opening, and including said
suction port and said exhaust port facing the room, support means
disposed within said housing, and a support member secured to the
internal surface of said front panel cooperative with said support
means to removably support said heat exchanger therebetween such
that said front panel disengages from said housing to permit said
heat exchanger to be removed from said housing through said opening
thereof.
8. A ventilating device as claimed in claim 1 wherein the housing
includes an opening near to the interior of the room, and a front
decorated panel detachably closing said opening housing, and
including said suction port and said exhaust port facing the room,
support means disposed within said housing, a support member
secured to the internal surface of said front panel cooperative
with said support means to removably support said heat exchanger
therebetween such that said front panel disengages from the housing
to permit the heat exchanger to be removed from said housing
through said opening thereof, and an isolating plate capable of
being detachably sandwiched at the intersection of the suction and
exhaust passages between said support means and said support member
thereby to cause the exhaust stream to be sucked through said
exhaust port on the side of the room and simultaneously to cause
the suction stream to be discharged through said suction port on
the side of the room.
9. In combination: a motor vehicle; a suction conduit and an
exhaust conduit opening externally of the motor vehicle; a housing
including an external suction port connected to said suction
conduit, an external exhaust port connected to said exhaust
conduit, and an internal suction port and an internal exhaust port
facing the interior of the vehicle; a plurality of partitions
within said housing defining a suction passage and an exhaust
passage extending within said housing from the interior to the
exterior of the vehicle and opening into a common heat-exchange
space; a suction fan disposed in said suction passage operable to
form a suction air stream along the suction passage; an exhaust fan
disposed in said exhaust passage operable to form an exhaust air
stream along said exhaust passage; and combined heat-moisture
transfer means disposed within said common heat-exchange space for
effecting continuous and simultaneous transfer of heat and moisture
between the suction air stream and the exhaust air stream, said
combined heat-moisture transfer means including a plurality of
laminations composed of a material sufficiently thermally
conductive and permeable to moisture to effect continuous and
simultaneous transfer therethrough of both heat and moisture, said
plurality of laminations being superposed on one another at
predetermined substantially equal intervals defining therebetween a
plurality of gaps, and means for communicating alternate ones of
gaps formed between said laminations with said suction passage and
the remaining gaps with said exhaust passage.
10. A combination as claimed in claim 9 wherein said laminations of
said heat exchanger are composed of Japanese paper.
11. An air conditioning equipment for conditioning a room
comprising: a main body having an inflow side; and a ventilating
device comprising a box-shaped housing including a suction port and
an exhaust port facing each of the interior and exterior portions
of the room to be conditioned; a plurality of partitions within
said housing defining a suction passage and an exhaust passage each
communication one suction port and one exhaust port and wherein
said suction passage and exhaust passage open into a common
heat-exchange space; a suction fan disposed in said suction passage
operable to form a suction air stream along said suction
passageway; an exhaust fan disposed in said exhaust passage
operable to form an exhaust air stream along said exhaust passage;
and combined heat-moisture transfer means disposed within said
common heat-exchange space for effecting continuous and
simultaneous transfer of heat and moisture between the suction air
stream and the exhaust air stream, said combined heat-moisture
transfer means including a plurality of laminations composed of a
material sufficiently thermally conductive and permeable to
moisture to effect continuous and simultaneous transfer
therethrough of both heat and moisture, said plurality of
laminations being superposed on one another at predetermined,
substantially equal intervals defining therebetween a plurality of
gaps, and means for communicating alternate ones of gaps formed
between said laminations with said suction passage and the
remaining gaps with said exhaust passage; and means for supplying
the suction air stream to said inflow side of said main body.
12. An airconditioning equipment as claimed in claim 11 wherein
said laminations of said heat exchanger are composed of Japanese
paper.
13. A ventilating device for ventilating a room comprising: a
housing having therein means defining an air induction system for
inducting air from outside the room to be ventilated into the room
and means defining an air discharge system for discharging air
contained within the room to the outside thereof; and combined
heat-moisture transfer means statically positioned within both said
air induction and air discharge system for effecting continuous and
simultaneous transfer of heat and moisture between the inducted and
discharged air comprising a plurality of spaced-apart and
superposed heat and moisture transfer surfaces defining
therebetween a plurality of superposed static air flow paths, means
communicating alternate ones of said flow paths with said air
induction system and the remaining alternate flow paths with said
air discharge system, and wherein said heat and moisture transfer
surfaces are composed of a material sufficiently heat conductive
and sufficiently permeable to moisture to allow moisture flow
therethrough to continuously and simultaneously effect both heat
and moisture exchange between the inducted and discharged air.
14. A ventilating device according to claim 13; including a spacer
member disposed in the flow path between each two adjacent heat and
moisture transfer surfaces, each said spacer member having an
undulating configuration dividing the flow path into a plurality of
individual and parallel flow paths.
15. A ventilating device according to claim 14; wherein the flow
paths in communication with said air induction system extend
transversely with respect to the flow paths in communication with
said air exhaust system.
16. A ventilating device according to claim 13; wherein said heat
and moisture transfer surfaces are composed of Japanese paper.
Description
BACKGROUND OF THE INVENTION
This invention relates to a ventilating device including a heat
exchanger for exhausting, as an exhaust stream, air from a room
externally of the room simultaneously with the suction of the open
air, as a suction stream, into the room while effecting heat
exchange between the exhaust and suction streams. The invention
also concerns an air conditioning system incorporating such a
ventilating device.
Upon air conditioning rooms in buildings, it is generally desirable
to comfortably and healthily air condition the rooms by introducing
a quantity of outside open air into the rooms. However if too much
the open air is introduced into the room, the introduced air can
vary the room temperature. As a result, an airconditioning
equipment involved is undesirably increased in operating costs.
Therefore it has been previously practiced to cool or warm the room
through the utilization of an air conditioner for effecting the
suction of the air simultaneously with the exhaust of the room air
in combination with a heat exchanger for warming or cooling the
suction stream with the exhaust stream to approximate both the
streams to each other in temperature for the purpose of saving
costs at which the air conditioner is operated. The conventional
type of such ventilating devices has comprised the multi-vane
rotary impeller having the heat accumulating and moisture absorbing
properties and bridging the suction and exhaust streams, resulting
in the disadvantages that they are complicated and troublesome to
be manufactured.
Lately motor vehicles have tended to be provided with a cooling
device in addition to the warming device. If either of the warming
and cooling devices is in operation while the associated windows
are kept shut to isolate the interior of the vehicle from the
exterior thereof, then air in the vehicle will have been
contaminated within a short time interval because the vehicle
interior has such a small volume. This has led to the necessity of
sometimes opening the windows or introducing the surrounding fresh
air into the vehicle interior through an air intake involved for
the purpose of ventilation. Due to the small capabilities of the
warming and cooling devices, the effects exhibited by the devices
could not be much expected when the open air was introduced too
much into the vehicle.
Further in the conventional type of air conditioning equipment for
warming or cooling the room while the open air is continuously
introduced into the latter, such has been disadvantageous in that
the intake of the open air in a large amount causes a decrease in
warming or cooling effect leading to an increase in operation costs
of the equipment.
SUMMARY OF THE INVENTION
Accordingly, it is an object of the invention to provide a new and
improved ventilating device having a heat exchanger for exhausting,
as an exhaust stream, air in a room externally of the room
simultaneously with the suction of the open air, as a suction
stream, into the room while continuously and simultaneously
effecting temperature and humidity exchanges between the exhaust
and suction streams with a simple construction capable of being
easily manufactured at low costs.
It is another object of the invention to provide a new and improved
ventilating device for use in a motor vehicle to ventilate the
interior thereof without deteriorating the cooling or warming
effect.
It is still another object of the invention to provide a new and
improved airconditioning equipment for effectively ventilating
rooms without deteriorating the effect thereof.
The invention accomplishes these objects by the provision of a
ventilating device with a heat exchanger, comprising a box-shaped
housing including a suction port and an exhaust port facing each of
the interior and exterior of the associated room, a plurality of
partitions within the housing for forming a suction passage and an
exhaust passage extending within the housing from the associated
suction to the exhaust port, a suction fan disposed in the suction
passage to form a suction stream along the suction passage, an
exhaust fan disposed in the exhaust passage to form an exhaust
stream along the exhaust passage, and a heat exchanger,
characterized in that the suction passage intersects the exhaust
passage, and that the heat exchanger is positioned at the
intersection of the suction and exhaust passages and includes a
plurality of laminations of a material thermally conductive and
permeable to moisture and superposed on one another at
predetermined equal intervals, and means within gaps formed between
the laminations for passing the suction stream through alternate
ones of the gaps and for passing the exhaust stream through the
remaining gaps.
The suction and exhaust fans each may be preferably either a
centrifugal fan or a cross flow fan.
The laminations of the heat exchanger may be advantageously of a
Japanese paper.
The housing may conveniently comprise a front decorated panel
facing the interior of the room and having disposed thereon the
suction and exhaust ports, the front panel detachably closing the
associated end of the housing, a support member attached to the
interior surface of the front panel, and support means disposed in
the housing to cooperate with the support member on the front panel
to removably support the heat exchanger. In this arrangement the
support member and means may engage an isolating plate rather than
the heat exchanger to isolate the suction passage from the exhaust
passage without the passages intersecting each other for purpose of
ventilation alone.
The ventilating device may also be installed in a motor vehicle to
ventilate the interior of the vehicle without deteriorating the
cooling or warming effect.
Further the ventilating device may be operatively associated with
an air conditioning equipment such that the suction stream
resulting from the open air is supplied to the equipment while the
exhaust stream from the associated room is partly exhausted through
the ventilating device with no decrease in efficiency of the
latter.
BRIEF DESCRIPTION OF THE DRAWINGS
The invention will become more readily apparent from the following
detailed description taken in conjunction with the accompanying
drawings in which:
FIG. 1 is a fragmental perspective view of a heat exchanger for use
with a ventilating device constructed in accordance with the
principles of the prior art with parts broken away to illustrate
the internal structure thereof;
FIG. 2 is an elevational view, partly in section of a ventilating
device with a heat exchanger constructed in accordance with the
principles of the invention with parts broken away, and with parts
illustrated in phantom;
FIG. 3 is a perspective view of the essential part of the heat
exchanger shown in FIG. 2;
FIG. 4 is a perspective view of one portion of the heat exchanger
shown in FIG. 3;
FIG. 5a is a schematic plan view of air streams flowing through the
heat exchanger shown in FIG. 3;
FIGS. 5b and c are graphs illustrating the temperature
distributions on the discharge side of the air streams shown in
FIG. 5a;
FIG. 6 is a graph plotting the temperature distributions shown in
FIG. 5b and c in a common temperature unit for comparison
purpose;
FIG. 7 is a graph plotting a temperature and an absolute humidity
on the discharge side of the suction stream against a flow rate of
air for one embodiment of the invention in one mode of
operation;
FIG. 8 is a graph similar to FIG. 7 but illustrating the embodiment
in another mode of operation;
FIG. 9 is a graph plotting a flow rate of air against efficiencies
of exchange as to the temperature, humidity and total heat
calculated on the basis of the data shown in FIGS. 7 and 8;
FIG. 10 is a graph similar to FIG. 9 but illustrating another
embodiment of the invention;
FIG. 11 is an elevational view, partly in section of a modification
of the invention with parts broken away;
FIG. 12 is a front elevational view of the fan shown in FIG.
11;
FIGS. 13, 14 and 15 are views of different modifications of the
invention;
FIG. 16 is an elevational view, partly in section of the device
shown in FIG. 15 and put in a particular mode of operation;
FIG. 17 is a schematic elevational view of a motor vehicle
incorporating the invention with parts broken away to illustrate
the manner in which the ventilating device of the invention is
installed therein;
FIG. 18 is a view illustrating the details of the ventilating
device shown in FIG. 17;
FIG. 19 is an elevational view, partly in section of an
airconditioning equipment constructed in accordance with the
principles of the invention with parts cut away; and
FIG. 20 is a view illustrating the details of the ventilating
device shown in FIG. 19.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings and FIG. 1 in particular there is
illustrated a heat exchanger of the conventional construction used
in ventilating devices. The arrangement illustrated comprises a
driving electric motor 1 including a driving shaft 2, and a main
body 3 of the heat exchanger including a rotary shaft 4 operatively
connected to the driving motor shaft 2 and a plurality of radial
vanes 5 secured in substantially equal angular intervals on the
rotary shaft 4. The vanes 5 are formed of any suitable material
having heat accumulating and moisture absorbing properties. The
main body 3 of the heat exchange is encircled by a cylindrical wind
channel or tunnel 6(only one thereof illustrated in FIG. 1).
In operation, the motor 1 is driven to rotate the main exchanger
body 3 in the direction of the arrow A illustrated in FIG. 1. On
the other hand the suction stream is adapted to pass through the
region of the upper half of the rotating main body 3 in the
direction of the arrows A shown in FIG. 1, while the exhaust stream
is adapted to pass through the region of the lower half thereof in
the direction of the arrows C shown in FIG. 1. Under these
circumstances, those vanes 5 located in the region of the lower
half of the main exchanger body 3 are warmed or cooled and
humidified or dehumidified, as the case may be, with the exhaust
stream while they are successively moved to the region of the upper
half of the main body 3 as the latter is rotated in the direction
of the arrow A. Those vanes 5 reaching the region of the upper half
of the main exchanger body 3 are operated to warm or cool and
humidify or dehumidify the suction stream until the latter stream
approximates the state of air within the associated room. As a
result, temperature and humidity exchanges are effected between the
suction and exhaust stream by the medium of the rotating vanes 5.
That is the total heat exchange is effected between both
streams.
The heat exchanger as shown in FIG. 1 has been satisfactorily
operated to some extent as the ventilating device for effecting the
total heat exchange between the suction and exhaust streams for
practical purposes. However heat exchangers such as shown in FIG. 1
include a rotary portion leading to various disadvantages. For
example, that rotary portion is complicated in construction while
being troublesome and expensive to be manufactured. Also the rotary
portion has been permitted to be only formed into a circular cross
section which is, in turn, accompanied by a circular or nearly
circular cross section of the resulting device. Therefore the
entire device could not be formed into an elongated shape giving a
smart appearance.
The invention contemplates to eliminate the disadvantages of the
conventional devices as above described.
Referring now to FIG. 2 of the drawings there is illustrated one
embodiment constructed in accordance with the ventilating device of
the invention. The ventilating device illustrated is attached to
one wall 10 of the associated room by having its box-shaped housing
12 extending through and fixed to wall 10. The housing 12 includes
a front decorated panel 14 of angled shape rigidly secured to that
end portion thereof near to the room and provided on the upper
portion with a suction port 16 and on the lower portion with an
exhaust port 18. A combined heat-moisture transfer means comprises
a heat exchanger 20 having a vertical diagonal portion thereof
sealed through a vertical partition 30 extending across the
abovementioned end portion of the housing 12 and a horizontal
diagonal portion fixed at both ends to a horizontal partition 32
secured to the inner surface of the front panel 14 and to a
horizontal partition 34 opposite to the partition 32. The partition
34 terminates on the inner surface of a rear panel 36 closing the
other end of the housing 12. The rear panel is exposed to the open
air and provided on the upper and lower portions with a suction
port 36 and an exhaust port 38 respectively. All the ports are
rectangular and horizontally positioned and all the partitions
along with the heat exchanger form a suction passage 40 and an
exhaust or discharge passage 42 extending within the housing 12
from the outdoor suction port 36 to the indoor exhaust port 18 and
from the indoor suction port 16 to the outdoor exhaust port 38
respectively. Thus both the passages intersect each other and open
into a common heat-exchange area in the region of the heat
exchanger 20. The suction passage 40 and the associated ports 18
and 36 comprise an air exhaust system for exhausting air contained
within the room to the outside wheras the exhaust passage 42 and
the associated ports 16 and 38 comprise an air induction system for
inducting outside air into the room.
A filter 44 for cleaning air is disposed adjacent the indoor
suction port 16 within the housing 12 to fully cover that port and
another filter 46 for cleaning air is disposed adjacent the outdoor
suction port 36 within the housing 12 to fully cover that port.
Then a suction and an exhaust fans generally designated by the
reference numerals 48s and e respectively are disposed in the
suction and exhaust passages 40 and 42 respectively so as to have
their axes of rotation coaxial to each other with discharge ends
thereof directed downstream of the respective passages. The fans
48s and e are shown here as being of the centrifugal type and
identical in construction to each other. Therefore one of the fans,
in this case, the suction fan 48s will now be described in detail.
The components of the exhaust or discharge fan 48e are designated
by the same reference numerals denoting the corresponding
components of the suction fan 48s with the suffix "e" in place of
the suffix "s" and need not be described.
The suction fan 48s comprises a casing 50s open at one end to
provide a discharge opening 52s, a pair of opposite inflow openings
54s disposed on the periphery of the casing 50s, an impeller 56s
within the casing including a plurality of strip-shaped radial
vanes 56s formed into a cylindrical configuration about their
rotary shaft (not shown). Only one of the vanes 56s is illustrated
in FIG. 2.
As shown in FIG. 2, the suction and exhaust fans 48s and e are
operatively connected to a common electric motor 58 sealed through
the horizontal partition 34. Specifically, the motor 58 includes a
driving shaft 60 having connected to both ends thereof the rotary
shafts of the vanes 56s and e respectively. The suction fan 48s has
its discharge opening 52s comminicating with the inflow side of the
heat exchanger 20 through a space defined by partitions 60 and 62
extending from that discharge opening 52s to a pair of the adjacent
corner edges of the heat exchanger 20 while the exhaust fan 48e has
its discharge opening 52e communicating with the outdoor exhaust
port 38 through a space defined by partitions 64 and 66 extending
from that discharge opening 52e to the outdoor exhaust port 38.
In operation, the electric motor 58 is driven to rotate the fans
48s and e. Then the suction fan 48s sucks the open air or primary
air into the suction passage 40 through the outdoor suction port 36
to form a suction stream. After having been cleaned by the air
filter 46 the suction flows through the inflow and discharge
opening 54s and 52s respectively of the suction fan 48s into the
heat exchanger 20. Simultaneously the exhaust fan 48e is operative
to introduce air in the room or the secondary air into the exhaust
passage 42 through the indoor suction port 16 to form an exhaust
stream. The exhaust stream is cleaned by the filter 44 and flows
into the heat exchanger 20. After the suction and exhaust streams
have passed through the heat exchanger 20, in the manner as will be
fully described hereinafter, the suction stream or primary air is
introduced into the room through the indoor exhaust port 18 while
the exhaust stream or secondary air is exhausted into the
atmosphere along the exhaust passage 42 through the inflow and
discharge openings 54e and 52e respectively of the exhaust fan 48e.
In FIG. 2 the arrows shows the directions of the respective
streams. As a result, the room is ventilated.
Referring now to FIG. 3, it is seen that the combined heat-moisture
transfer means comprises a plurality of heat and moisture transfer
surfaces or heat-exchange surfaces composed of flat partitions or
laminations 22 in the form of squares superposed on one another at
predetermined, substantially equal intervals to form gaps or flow
paths therebetween and one undulated spacer member 24 disposed in
each of the gaps to be sandwiched between the adjacent laminations
22 thereby to form a multi-layer stack. Alternate ones of the
undulated spacer members 24 have their wave crests substantially
parallel to one side of the laminations 22 to form air channels 26
between the associated laminations. The remaining spacers 24 have
their wave crests substantially parallel to the adjacent side of
the laminations 22 to form air channels 28 between the associated
laminations. In the example illustrated the air channels 26 are
intersected substantially perpendicularly with the air channels 28.
For example the uppermost spacer 24 forms the air channels 26
substantially parallel to the righthand side as fully viewed in
FIG. 3 of the stack between the uppermost and succeeding
laminations 22 to permit an air current flowing in the direction of
the arrows D shown in FIG. 3 to pass therethrough but to prevent an
air current flowing in the direction of the arrows E shown in FIG.
3 from passing therethrough. Similarly the lowermost spacer 24
forms the air channels 28 substantially parallel to the lefthand
side as fully viewed in FIG. 3 of the stack between the lowermost
and succeeding laminations 22 to permit the air current flowing in
the direction of the arrows E to pass therethrough but to prevent
the aircurrent flowing in the direction of the arrows D from
passing therethrough. Therefore it will be appreciated at the air
currents flowing in the direction of the arrows D and E are
completely isolated from each other within the heat exchangers. It
is to be noted that in the arrangement of FIG. 2, both the passages
40 and 42 communicated with the air channels 26 and 28 respectively
and therefore that both the passages 40 and 42 intersect each other
on the region of the heat exchanger 20 without communicating with
each other by virtue of the above-mentioned structure of the heat
exchanger 20 cooperating to the partitions 30, 32 and 34.
The laminations should be formed of any suitable material which is
sufficiently thermally conductive and permeable to moisture to
enable both heat and moisture transfer therethrough, for example
Japanese paper. The undulated spacer 24 is shown in FIG. 4 as
having a triangular waveform. However it is to be understood that
the spacer 24 may be undulated into a sawtoothed or sinusoidal or
any other desired waveform.
The operation of the heat exchanger 20 will now be described in
more detail with reference to FIGS. 5a, b and c. In FIG. 5a the
heat exchanger 20 is diagramatically shown at block 20 and the
warmed air or the secondary air forming the exhaust stream enters
the heat exchanger 20 on its inflow side 70 to form exhaust
currents 72 along the air channels 26 or 28 on the spacers 24 and
leaves the heat exchanger 20 through its discharge side 74.
Similarly the primary air or the cold air forming the suction
stream enters the heat exchanger 60 on its inflow side 76
perpendicular to the inflow side 70 for the secondary air to form
suction current 78 and leave the heat exchanger 20 through its
discharge side 80. Thereby the temperature exchange is effected
between the exhaust and suction currents. In this event, the warmed
or secondary air has a temperature distribution as shown at curve a
in FIG. 5b wherein a temperature t is plotted against a distance
measured from one end of the discharge side 74 therealong and
P.sub.13, P.sub.23 and P.sub.33 typically represent imaginary
intersections of the exhaust currents 72 and that suction current
78 nearest to the discharge side 74 for the exhaust currents 72 as
shown in FIG. 5a. From FIG. 5b, it is seen that the temperatures at
points P.sub.13 and P.sub.33 are maximum and minimum respectively
with the mean temperature equal to the temperature at point
P.sub.23. The primary or cold air has a temperature distribution as
shown at curve b in FIG. 5c similar to FIG. 5b. Points P.sub.11,
P.sub.12 and P.sub.13 typically represent imaginary intersections
of the suction currents 78 and that exhaust current 72 nearest to
the discharge side 80 for the suction current. As in the warmed
exhaust currents the temperatures at points P.sub.11 and P.sub.13
of the cold currents are maximum and minimum respectively with the
mean temperature equal to the temperature at point P.sub.12.
For comparison purpose, curves a and b as shown in FIGS. 5b and c
are illustrated together in FIG. 6 wherein t.sub.w1 and t.sub.w2
designate the maximum temperature on the inflow side and the mean
temperature in the discharge side of the secondary or exhaust
current in degrees Centigrade and t.sub.c1 and t.sub.c2 represent
the maximum temperature on the inflow side and the mean temperature
in the discharge side of the primary or suction current in degrees
Centigrade. From FIG. 6 it is seen that the maximum temperature of
the exhaust currents 72 on the discharge side (which corresponds to
the temperature at P.sub.13) is approximately equal to the minimum
temperature of the suction currents 78 on the discharge side (which
corresponds to the temperature at P.sub.13). Accordingly the mean
temperature of the suction currents on the discharge side or at
P.sub.12 is appreciably higher that of the exhaust currents on the
same side or at P.sub.23.
As previously described, the laminations 22 of the heat exchanger
20 are also permeable to moisture so that the moisture contained in
the exhaust currents 72 is transferred to the suction currents 78
until the exhaust and suction currents have the respective
distributions of humidity and strictly, the absolute humidity
similar to the temperature distributions as above described.
Therefore the suction currents are appreciably higher in mean
humidity on the discharge side than the exhaust currents which is
accompanied by the mean enthalpy on the discharge side appreciably
higher in the suction currents 78 than in the exhaust currents
72.
By using the t.sub.w1, t.sub.w2, t.sub.c1 and t.sub.c2 as above
defined, the heat exchanger 20 has an efficiency of temperature
exchange E.sub.1 for the suction currents expressed by the
equation
E.sub.1 = (t.sub.w1 - t.sub.w2 )/(t.sub.w1 - t.sub.c1)
Similarly an efficiency of temperature exchange E.sub.2 for the
exhaust currents is expressed by the equation
E.sub.2 = (t.sub.c2 - t.sub.c1)/(t.sub.w1 - t.sub.c1)
Also the heat exchanger 20 has efficiencies of humidity exchanges
H.sub.1 and H.sub.2 for the suction and exhaust currents expressed
respectively by the equations
H.sub.1 = (h.sub.w1 - h.sub.w2)/(h.sub.w1 - h.sub.c1)
and
H.sub.2 = (h.sub.c2 - h.sub.c1)/(h.sub.w1 - h.sub.c1)
where
h.sub.w1 = humidity on inflow side of exhaust current
h.sub.w2 = mean humidity on discharge side of exhaust current
h.sub.c1 = humidity on inflow side of suction current
and
h.sub.c2 = mean humidity on discharge side of suction current.
Further the efficiencies of total heat exchange U.sub.1 and U.sub.2
for the suction and exhaust currents taking into account of both
their temperature and humidity exchanges are expressed respectively
by the equations
U.sub.1 = (U.sub.w1 - U.sub.w2)/(U.sub.w1 - U.sub.c1)
and
U.sub.2 = (U.sub.c2 - U.sub.c1)/(U.sub.w1 - U.sub.c1)
where
U.sub.w1 = enthalpy on inflow side of exhaust current
U.sub.w2 = mean enthalpy on discharge side of exhaust current
U.sub.c1 = enthalpy on inflow side of suction current
and
U.sub.c2 = mean enthalpy on discharge side of suction current.
As an example, partitions or laminations such as shown at 22 in
FIG. 3 were into 110 mm long squares of a Japanese paper having a
thickness or a basis weight of 70 grams per square centimeter and
including 3 percent by weight of a synthetic fibrous material. On
the other hand, spacers such as shown at 24 in FIG. 3 were formed
of a Kraft paper having a thickness or a basis weight of 120 grams
per square centimeter such that they were undulated into triangular
waveforms having a peak-to-peak amplitude of about 1.8 millimeters
and a wavelength of about 2.1 millimeters. Then the laminations
alternating the undulated spacers supperposed one another to form a
stacks of 110 layers having the overall height of 220 millimeters
and a spacing of about 18 millimeters between each pair of adjacent
laminations. Then the stacks each were formed into a unitary
structure by any suitable means (not shown) to provide a heat
exchangers.
The heat exchanger thus produced was put under the operating
conditions that the associated room was to be maintained at a
temperature t.sub.w1 of 20.degree. C at a relative humidity
h.sub.w1 of 50 percent or an absolute humidity of 0.0072 kg/kg
kilogram per each kilogram of dried air in the open air having a
temperature t.sub.c1 of 5.degree. C and a relative humidity
h.sub.c1 of 65 percent or an absolute humidity of 0.0035 kg/kg
kilogram per each kilogram of dried air as during the winter season
requiring to heat the room. Then the exhaust stream from the room
and the suction stream from the open air passed through the heat
exchanger in the manner as above described in conjunction with FIG.
4 while both the streams varied in flow rate but they were
continuously equal in flow rate to each other. Under these
circumstances the temperature t.sub.w2 and humidity h.sub.w2 on the
discharge side of the exhaust streams were measured as were the
temperature t.sub.c2 and humidity h.sub.c2 on the discharge side of
the suction stream. The mean values of the respective parameters
determined by the measurents are plotted in FIG. 7 wherein the axis
of abscissas represents a flow rate of air in m.sup.3 /min of
either of the exhaust and suction streams and the axis of ordinates
represents an absolute humidity in kg/kg.sub.dried air or a
temperature in .degree.C.
Also the heat exchanger were put in under the operating conditions
that the room was to be maintained at a temperature t.sub.w1 of
25.degree. C and at a relative humidity h.sub.w1 of 50 percent or
an absolute humidity of 0.01 kg/kg.sub.dried air in the open air
having a temperature t.sub.c1 of 30.degree. C and a relative
humidity h.sub.w1 of 50 percent or an absolute humidity of 0.01
kg/kg.sub.dried air as during the summer season requiring to cool
the room. Under these conditions the measurements as above
described were repeated to provide the mean values of the various
parameters as plotted in FIG. 8.
From FIGS. 7 and 8 it is seen that with the abovementioned heat
exchanger used to effect the total heat exchange between the
exhaust and suction streams for the ventilating device of FIG. 2,
the suction stream is supplied to the associated room while it is
maintained in this state substantially equal to the air state
within the room both under the heating conditions during the winter
season and under the cooling conditions during the summer
season.
On the basis of the data as shown in FIGS. 7 and 8 the efficiencies
of temperature exchange (E.sub.2).sub.a, humidity exchange
(H.sub.2).sub.a and total heat exchange (U.sub.2).sub.a of the
suction streams were calculated so that their figures remained
substantially unchanged between the heating conditions during the
winter season and the cooling conditions during the summer season
as shown in FIG. 9 wherein the axis of abscissas represents a flow
rate of air in m.sup.3 /min and the axis of ordinates represents an
efficiency of each parameter in percent. Also curves are labelled
the same reference characters representing the corresponding
parameters as in FIGS. 7 and 8.
Further heat exchangers such as shown in FIG. 3 were formed of a
Japanese paper including 60 percent by weight of a synthetic
fibrous material for use with sliding screens and Kent paper. That
is, the Japanese paper was cut into squares having one side 105
millimeters long to form laminations such as shown at 22 in FIG. 3
and the Kent paper was formed into undurated spacers such as shown
at 24 in FIG. 3. Then the laminations and spacers thus formed were
assembled into a unitary structure including a stack of 144 layers
having the overall length of 325 millimeters and a spacing of from
2.0 to 2.3 mm formed between each pair of adjacent laminations as
previously described.
The measurements as above described in conjunction with FIGS. 7 and
8 were repeated to obtain the efficiencies of temperature exchange
E.sub.2, humidity exchange H.sub.2 and total heat exchange U.sub.2
as shown in FIG. 10. While FIG. 10 is similar to FIG. 9 it is noted
that the various efficiencies are plotted against the flow rate of
air under two different sets of operating conditions. More
specifically, curves labelled the reference characters
(E.sub.2).sub.b, (H.sub.2).sub.b and (U.sub.2).sub.b were obtained
with a difference between temperatures on the inflow sides of the
exhaust and suction streams ranging from 7.degree. to 12.degree. C
and with a difference in absolute humiditily on the inflow sides of
both the streams ranging from 0.03 to 0.049 kg/kg.sub.dried air. If
such differences in temperature and humidity range from 20.degree.
to 25.degree. C and from 0.0084 to 0.0123 kg/kg.sub.dried air
respectively the respective efficiencies are expressed at curves
(E.sub.2).sub.c, (H.sub.2).sub.c and (U.sub.2).sub.c.
From FIG. 10 it is seen that the efficiencies of temperature
exchange E.sub.2, humidity exchange H.sub.2 and total exchange
U.sub.2 are not much affected by both differences between the
temperatures on the inflow sides of the exhaust and suction streams
and a difference between the humidities on the same and rather
greatly change with a flow rate of each stream. For example FIG. 10
indicates that for a flow rate of about 0.5 m.sup.3 /min, the
efficiencies of temperature exchange E.sub.2, humidity exchange
H.sub.2 and total heat exchange U.sub.2 are as high as about 80
percent, about 60 percent and about 70 percent respectively whereas
with the flow rate increased to about 2.5 m.sup.3 /min, those
efficiencies all decrease as much as by 20 to 30 percent.
While the heat exchanger has been shown in FIG. 3 as being of a
square cross section it is to be understood that it may be of any
desired shape. For example, the laminations and spacers may be
rhombic or circular while the exhaust channels intersect the
suction channels at the corresponding angle other than right
angles. Also if desired, the undulated spacer may change in
waveform. For example, they may be undulated into sawtoothed,
sinusoidal rectangular waveform or any other desired waveform.
Referring to FIG. 11 wherein like reference numerals designate the
components identical or corresponding to those shown in FIG. 2,
there is illustrated a modification of the invention having a cross
flow type fan substituting each of the centrifugal fans as shown in
FIG. 2. As shown in FIG. 11, a cross flow type suction fan 48a s
and a line flow type exhaust fan 48a e are disposed in the suction
and exhaust passageways 40 and 42 respectively so as to direct
their discharge openings 52a s and a e to the heat exchange 20 and
the outdoor exhaust port 38 repsectively.
Both the fans are identical in construction to each other and only
one of the fans for example, the suction fan 48a s , will now be
described with reference to FIG. 12. The line flow type fan 48a s
comprises a casing 50a s having the form of a curved hollow
cylinder open at both ends one of which provides a discharge
opening 52a s in the form of a laterally elongated rectangle.
Rotatably disposed at the other end of the casing 50 a s is an
impeller 56a s formed into a cylinder having a plurality of
strip-shaped vanes disposed at predetermined equal angular
intervals about its axis of rotation. One half of the inpeller 56a
s projects beyond the open end of the casing 50a s providing an
inflow opening 54a s in the form of a laterally elongated
rectangle. As shown in FIG. 12, an electric motor 58a s is secured
to one side of the casing 50a s to drive the impeller 56a s . The
components of the exhaust fan 48a e are designated by the same
reference numerals denoting the corresponding components of the fan
48a s with the suffix e in place of the suffix s.
Since the cross flow type fans 48a s and a e include their own
motors 58a s and a e , the common motor 58 as shown in FIG. 2 is
omitted from the arrangement of FIG. 11. Further the partitions 60,
64 and 66 connected to the fans are omitted and support plates 60a
and 64a are fixed to the partition 34 to support the respective
fans 48a s and e s . In other respects the arrangement is
substantially identical to that shown in FIG. 2.
FIG. 13, wherein like reference numerals designate the components
identical or corresponding to those shown in FIG. 2, shows another
modification of the invention capable of maintaining the primary or
suction stream substantially equal in flow rate to the secondary or
exhaust stream. In FIG. 13, the housing 16 is of a rectangular
cross section and extends through and is fixed to the wall 10 at
its position where it has be rotated from its position as
illustrated in FIG. 2 by an angle of 90.degree. . All the
components are disposed in bilateral symmetery with respect to the
central plane of the wall 10. For example, the indoor and outdoor
exhaust ports 18 and 38 are disposed in opposite relationship on
the upper portions of the opposite panels of the housing 12 and a
pair centrifugal fans 48s and e are disposed in opposite
relationship on the lower portion of the housing 12 and include the
respective inflow openings 54s and e facing the outdoor and indoor
suction ports 36 and 16 opposing to each other. The suction and
exhaust fans 48s and e are sealed through a partition 30a extending
across the interior of the housing 12 and their discharge openings
52s and e are open toward the heat exchanger 20. Therefore the
exhaust stream from the room passes through the exhaust fan 48e and
then to the heat exchanger 20 whereas the same first passes through
the heat exchanger 20 and then through the exhaust fan 48e in the
arrangement of FIG. 2. In other respect the arrangement
substantially identical to that shown in FIG. 2.
The arrangement of FIG. 13 is particularly advantageous in that the
disposition of the suction and exhaust fans having the same
capability on the inflow sides of the heat exchanger, ensures that
the primary and secondary streams pass at an equal flow rate and
therefore at an equal speed through the heat exchanger to increase
the efficiency of total heat exchange to the order of 70 percent to
provide excellent means for thermally isolating the interior of the
room from the open air. Further due to its symmetric construction,
the resulting device is simple and compact in construction and
inexpensive to manufacture.
If desired, the heat exchanger 20 may be detachably disposed in the
housing 12 as shown in FIGS. 14 and 15 wherein like reference
numerals designate the components identical or corresponding to
those shown in FIGS. 2 and 11.
The arrangement of FIG. 14 is identical to that shown in FIG. 11
excepting that the heat exchanger 20 is detachably disposed in the
housing 12. More specifically the heat exchanger 20 has its
vertical diagonal portion detachably supported to tilted ends 82 of
a pair of vertical partitions b disposed in opposite relationship
to that portion and its horizontal diagonal portion sandwiched at
the opposite corner edges between a pair of opposite angle brackets
84 and 86 fixed to the partition 32 secured to the front panel 14
and to the support plate 60a for the suction fan 48s respectively.
Then the front panel 14 provided with the indoor suction and
exhaust ports 16 and 18 is fixedly secured to the open end of the
housing 12 by having its slit on its upper edge (as viewed in FIG.
14) engaging the corresponding protrusion 88 upper edge of the
housing 12 and its lower edge fixed to the lower edge of the
housing 12 by screws 90 having the knob. In other respects the
arrangement is identical to that shown in FIG. 11.
In FIG. 15, the upper edge of the front panel 14 is fixed to the
housing by screws 92 but not by the engagement of the protrusion 88
with the slit. In other respects the arrangement is identical to
that shown in FIG. 2 except that the heat exchanger 20 is
detachably disposed in the housing 12 in the similar manner as
above described in conjunction with FIG. 14.
If the heat exchanger 20 is desired to be removed from the device
for replacement or for other reasons, it is only required for the
arrangement of FIG. 14 to release the screws 98 to disengage the
lower edge of the front panel 14 from the housing 12. Then the
panel is raised to disengage the slit thereon from the protrusion
88 on the housing 12 whereupon it can be removed from the open end
of the housing. This is accompanied by the disengagement of the
angle bracket 84 from the heat exchanger 20. Then the heat
exchanger 20 can readily be pulled out from the housing 12.
Thereafter the heat exchanger 20 may be checked, cleaned or
replaced by a new heat exchanger and then the process reversed from
that just described is effected until the front panel 14 is secured
to the housing 12.
In the arrangement of FIG. 15 corresponding to that shown in FIG.
2, the front panel 14 can disengage from the housing 16 through the
release of the screws 92. Then the process as above described in
conjunction with FIG. 14 is repeated.
Thus the arrangements shown in FIGS. 14 and 15 are facilitated in
maintenance to permit the efficiency of total heat exchange to be
always held high.
Alternatively, the arrangement shown in either of FIGS. 14 and 15
may readily be used only to ventilate the associated room without
effecting the temperature and humidity exchanges. In this event the
heat exchanger 20 is removed from the housing 12 in the manner as
above described after which an isolating plate 94 is hermetically
supported by the opposite angle brackets 84 and 86 to isolate the
suction passageway 40 from the exhaust passage 42 as shown in FIG.
16. Namely, FIG. 16 illustrates the arrangement of FIG. 15 having
the shield plate 94 substituting the heat exchanger 20.
In the arrangement of FIG. 16, the suction fan 48s is operated to
suck the open air as a suction stream from the outdoor suction port
36 directly into the associated room. On the other hand, the
exhaust fan 48e is operated to such the room air, as an exhaust
stream from the indoor exhaust port 16 through the outdoor exhaust
port 38 into the atmosphere while the room air is not affected by
the suction stream. As a result, the temperature and humidity
exchanges are not effected between the suction and exhaust streams
and instead the room is effectively ventilated. Thus the
arrangement can be advantageously operated during the spring and
autumn seasons in which the interior of the room is not required to
be thermally isolated from the exterior thereof and without
wastefully using the heat exchanger.
From the foregoing it will be appreciated that the invention has
provided ventilating devices comprising the heat exchanger
including no movable part and disposed the intersection of the
suction and exhaust streams caused by the respective fan, so as to
permit both streams to passed therethrough in cross relationship.
Therefore the devices can be manufactured into simple construction
with low costs as well as being formed into smart appearance having
any desired width.
Referring now to FIG. 17, there is illustrated a motor vehicle
incorporating the ventilating device of the invention. The motor
vehicle is generally designated by the reference numeral 100 and
comprises a front portion 102 a rear portion 104 provided on both
sides with windows 106 (only those windows on one side being
illustrated), a floor plate 108, front wheels 110 and rear wheels
112. The internal space of the vehicle is schematically shown as
being confined by dotted line 114 and has the ventilating device
116 of the invention sealed through that wall 118 adjacent the
front portion 102. The device 116 includes the indoor suction and
exhaust ports 16 and 18 respectively opening in the space 114. The
ventilating device 116 is illustrated in detail in FIG. 18 wherein
like reference numerals designate the components identical to those
shown in FIG. 2. The arrangement illustrated in FIG. 18 is
identical to that shown in FIG. 2 excepting that the outdoor
suction and exhaust ports 36 and 38 respectively include axial
flanges 96 and 98 respectively. Then the flange 96 serves to
connect the suction port 36 to a suction conduit 120 opening in the
surface of the front portion 102 while the flange serves to connect
the exhaust port 38 to an exhaust conduit 122 opening in the floor
plate 108. The details of the ventilating device 116 need not be
further described because it is substantially identical to the
device of FIG. 2. If desired, the centrifugal fans illustrated may
be replaced by the cross flow type fans such as shown in FIG.
11.
In operation the suction fan 48s is operated to suck the fresh open
air through the suction conduit 120, the suction port 36 to supply
it through a heat exchanger 20 to the space 114 while at the same
time the exhaust fan 48e is operated to suck air in the space 114
through the suction port 16, the heat exchanger 20 and the exhaust
conduit 122 and thence to below the floor plate 108. As a result,
the space 114 is ventilated while the heat exchanger 20 serves to
effect the temperature and humidity exchanges or the so-called
total heat exchange in the manner as previously described. Thus the
ventilation is effected while the space 114 is kept in an
approximately adiabatic state with respect to the exterior of the
vehicle. This results in the advantages that air within the vehicle
is kept fresh and comfortable in respective of whether the motor
vehicle is in operation or stopped and without deteriorating the
heating or cooling effect upon the space within the vehicle.
FIG. 19 illustrates an air conditioning equipment constructed in
accordance with the principles of the invention. The reference
numeral 200 generally designates a room to be airconditioned. The
room 200 is confined by a floor 202 and walls one of which is
denoted by the reference numeral 204 and typically shown as being
means for isolating the interior from the exterior thereof.
Disposed in one corner of the room 200 is an air conditioning
equipment according to the principles of the invention generally
designated by the reference numeral 206. The equipment 206
comprises a housing 208 including a front wall provided on the
lower portion with an exhaust port 212. The exhaust port 212 serves
to discharge air conditioned air as will be described hereinafter
to the room 200 and the suction port 210 serves to suck air from
the room 200. A horizontal partition 214 extends across the
interior of the housing 208 to isolate the side of the exhaust port
212 from the side of the suction port 210 and has centrally sealed
therethrough a main body 216 of the airconditioning equipment 206
including its own heat exchanger and blower (not shown). The main
body 216 is provided on the lower surface as viewed in FIG. 19 with
an inflow opening 218 and on the upper surface with a discharge
opening 220.
A ventilating device generally designated by the reference numeral
222 is sealed through a lower portion of a rear wall opposite to
the front wall provided with the exhaust and suction ports 212 and
210 respectively of the airconditioning housing 208. The
ventilating device 222 is illustrated in detail in FIG. 20 wherein
like reference numerals designate the components identical to those
shown in FIG. 11. By comparing FIG. 20 with FIG. 11 it is readily
seen that both arrangements are substantially identical in
construction to each other.
Another horizontal partition 224 extends from the front panel 14 of
the device 222 at a point intermediate both the ports 16 and 18 to
the inner surface of the front wall of the housing 208 at a point
immediately above the suction port 210 for the purpose of
preventing any short-circuiting air current from occurring directly
between the airconditioning exhaust and suction ports 210 and 212
respectively. The partition 224 provided with a vent hole 216 to
permit the secondary air sucked from the room 200 to partly flow
toward the inflow opening 218 of the main air conditioning body
216. The rear end portion of the ventilating device 222 is fitted
into an air intake 228 disposed on the wall 204 with the external
surface of the wall 204 substantially flush with the rear end face
of the device 222 having disposed thereon the outdoor suction and
exhaust port 36 and 38 respectively. The details of the ventilating
device 222 will readily be understood from the description for FIG.
11. If desired, the cross flow type fans illustrated may be
replaced by the centrifugal fans such as shown in FIG. 2.
In operation, the airconditioning equipment 206 is operated to suck
air in the room 200 through the suction port 210 the vent hole 226
and the inflow port 218 into the main body 216 where the air is
warmed or cooled as the case may be. Then the warmed or cooled air
is supplied to the room 200 through the discharge opening 220 and
the exhaust port 212 whereby the interior of the room 200 is warmed
or cooled. The direction of the air current is designated at the
arrows F,G, H, I and J in FIG. 19.
On the other hand, the exhaust fan 48a s disposed in the
ventilating device 222 is operated to suck one portion of the air
sucked through the air conditioning port 210, through the suction
port 16 into the device 222 as shown at the arrows K in FIG. 20.
Then the sucked air is passed through the device and exhausted
externally of the room 200 through the exhaust port 38 along a path
as shown at the arrows L, M and N in FIG. 20. Simultaneously the
suction fan 48a e in the ventilating device 222 is operated to suck
the open air through the suction port 36 into the device and then
supply it through the exhaust port 18 to the inflow opening 218 of
the main body 216.
As a result, that air supplied to the room 200 from the main body
216 has added thereto the fresh open air while one portion of air
contaminated in the room is exhausted externally of the room.
Therefore the interior of the room 200 is warmed or cooled while at
the same time it is ventilated. At that time the heat exchanger 20
within the ventilating device 222 is operated to effect the
temperature and humidity exchanges or the total heat exchange
between the exhaust and suction streams flowing through the
ventilating device 222 in the manner as previously described in
conjunction with FIGS. 3 through 10. Therefore although the exhaust
and suction streams flow from and into the room 200 the interior of
the room 200 is maintained in approximately adiabatic state with
respect to the exterior thereof with the result that the
ventilation effected by the ventilating device 222 does not much
change the temperature and humidity in the room 200.
The arrangement is advantageous in that the fresh open air is used
to warm or cool the interior of the associated room with a high
efficiency because the open air is introduced into the room with an
approximately adiabatic state maintained between the interior and
exterior of the room.
* * * * *