U.S. patent number 3,777,508 [Application Number 05/286,545] was granted by the patent office on 1973-12-11 for heat pump type air conditioning systems.
Invention is credited to Satoshi Imabayashi, Shiego Murase, Koichiro Yamaguchi.
United States Patent |
3,777,508 |
Imabayashi , et al. |
December 11, 1973 |
HEAT PUMP TYPE AIR CONDITIONING SYSTEMS
Abstract
A heat pump has a compressor, a discharge gas tube, a condenser,
a receiver, an expansion valve, an evaporator, and a suction gas
tube connected in series in the order named. The receiver is also
connected to the discharge gas tube by a by-pass line including a
liquid pump, a heat exchanger having an electric heater, and a
control valve. At times, such as at low outdoor temperatures or at
starting-up, with the control valve opened and simultaneously with
the liquid pump actuated, a portion of the refrigerant liquid
stored in the receiver is supplied into the heat exchanger where it
is evaporated by heat from the electric heater. Hot evaporated
refrigerant flows from the heat exchanger through the control valve
into the discharge gas tube, and through the latter into the
condenser. When condensed, the refrigerant gas releases the heat
received from the heat exchanger, greatly increasing the heating
effect.
Inventors: |
Imabayashi; Satoshi (Kadoma
City, Osaka, JA), Yamaguchi; Koichiro (Kadoma City,
Osaka, JA), Murase; Shiego (Kadoma City, Osaka,
JA) |
Family
ID: |
36587201 |
Appl.
No.: |
05/286,545 |
Filed: |
September 6, 1972 |
Foreign Application Priority Data
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Sep 6, 1971 [JA] |
|
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46/69105 (UTILITY MODEL) |
Sep 20, 1971 [JA] |
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46/73684 (UTILITY MODEL) |
Sep 8, 1971 [JA] |
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46/82036 (UTILITY MODEL) |
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Current U.S.
Class: |
62/324.3;
165/240; 62/160; 62/276; 62/151; 62/275 |
Current CPC
Class: |
F24F
3/153 (20130101); F25B 13/00 (20130101); F25B
2341/0014 (20130101); F25B 2341/0011 (20130101); F25B
2313/008 (20130101) |
Current International
Class: |
F24F
3/00 (20060101); F25B 13/00 (20060101); F25B
49/02 (20060101); F25B 47/02 (20060101); F25b
013/00 () |
Field of
Search: |
;62/160,324,151,275,276
;165/29 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Wye; William J.
Claims
What is claimed is:
1. A heat pump comprising a refrigerant compressor, reversal means,
a gas tube, indoor heat exchange means, means providing resistance
to the flow of refrigerant, outdoor heat exchange means, and a
suction gas tube connected in series in the order named, means for
feeding a portion of the refrigerant liquid leaving said indoor
heat exchanger back to the inlet thereof, and means for heating the
refrigerant liquid before entering said indoor heat exchanger.
2. A heat pump according to claim 1, in which receiver means is
provided for storing the refrigerant liquid flowing from said
indoor heat exchanger, and in which by-pass means is provided for
feeding refrigerant liquid from said receiver into said gas
tube.
3. A heat pump according to claim 1, in which said heating means is
provided in said by-pass means for heating the refrigerant liquid
before entering said gas tube.
4. A heat pump according to claim 1, in which said heating means is
provided in said gas tube for heating the refrigerant liquid after
being mixed with discharge gas flowing from said compressor.
5. A heat pump according to claim 1, in which a liquid pump is
provided in said by-pass means for supplying refrigerant liquid
from said receiver to said gas tube.
6. A heat pump according to claim 1, in which control valve means
is provided in said by-pass means for shutting off the flow of
refrigerant therethrough except during increased heating load.
7. A heat pump according to claim 1, in which ejector means is
provided in said gas tube for ejecting the refrigerant liquid
flowing from said receiver means into the refrigerant gas flowing
from said compressor.
8. A heat pump according to claim 3, in which said heating means
comprises:
a reservoir;
a heat accumulating medium stored in said reservoir;
a heat exchanger coil extending within said reservoir in heat
exchange contact with said heat accumulating medium; and
an electric heater provided in said reservoir to heat said heat
accumulating medium.
9. A heat pump according to claim 3, in which said heating means
comprises:
an electric heater provided in said by-pass means.
10. A heat pump according to claim 3, in which said heating means
comprises:
burner means provided in said by-pass means.
11. A heat pump according to claim 4, in which said heating means
comprises:
an electric heater provided in said gas tube.
12. A heat pump comprising a refrigerant compressor, reversal
means, a discharge gas tube connecting said means to the discharge
side of said compressor, an indoor coil, a second tube connecting
said means to said indoor coil, receiver means, a third tube
connecting said indoor coil to said receiver means, an expansion
valve, an outdoor coil, a fifth tube connecting said expansion
valve to said outdoor coil, a sixth tube connecting said outdoor
coil to said reversal means, accumulator means, a seventh tube
connecting said reversal means to said accumulator means, a suction
gas tube connecting said accumulator means to the suction side of
said compressor, by-pass means for feeding refrigerant from said
receiver means into said second tube, a second valve for
controlling the flow of refrigerant through said by-pass means and
means for heating the refrigerant flowing from said receiver means,
said reversal means in heating position routing discharge gas
through said second tube into said indoor coil operating as a
condenser coil, and routing refrigerant from said outdoor coil
operating as an evaporator coil through said sixth and seventh
tubes into said accumulator means, said reversal means in cooling
position routing discharge gas through said sixth tube into said
outdoor coil operating as a condenser coil, and routing refrigerant
from said indoor coil operating as an evaporator coil through said
second and seventh tubes into said accumulator means, said second
valve being closed during cooling operation, said reversal means in
defrosting position routing discharge gas through said sixth tube
into said outdoor coil operating as a condenser coil, and routing
refrigerant from said heating means through said second and seventh
tubes into said accumulator means, said second valve being opened
during defrosting operation.
13. A heat pump according to claim 12, in which ejector means is
provided in said second tube for ejecting the refrigerant flowing
through said by-pass means into the refrigerant gas flowing from
said reversal means.
14. A heat pump according to claim 12, in which said heating means
is provided in said second tube downstream of said ejector
means.
15. A heat pump according to claim 12, in which said heating means
is provided in said by-pass means upstream of said ejector
means.
16. A heat pump comprising a refrigerant compressor, reversal
means, a discharge gas tube connecting said means to the discharge
side of said compressor, a first indoor coil, a second tube
connecting said means to said first indoor coil, a first valve, a
third tube connecting said first indoor coil to said first valve, a
second indoor coil, a fourth tube connecting said first valve to
said second indoor coil, a second valve, a fifth tube connecting
said second indoor coil to said second valve, receiver means, a
seventh tube connecting said second valve to said receiver means,
an expansion valve, a eighth tube connecting said receiver means to
said expansion valve, an outdoor coil, a ninth tube connecting said
expansion valve to said outdoor coil, a tenth tube connecting said
outdoor coil to said reversal means, accumulator means, an eleventh
tube connecting said reversal means to said accumulator means, a
suction gas tube connecting said accumulator means to the suction
side of said compressor, by-pass means for feeding refrigerant from
said receiver means into said second tube, a third valve for
controlling the flow of refrigerant through said by-pass means,
means for heating the refrigerant flowing from said receiver means,
a fourth valve for controlling communication between said fourth
and seventh tubes, a first capillary tube connecting said third and
fifth tubes, and a second capillary tube connecting said fifth and
seventh tubes, and fifth valve interconnecting said eighth and
ninth tubes, said reversal means in heating position routing
discharge gas through said second tube into said first indoor coil
operating as a condenser coil and from said first indoor coil
through said first valve and said third and fourth tubes into said
second indoor coil operating as a condenser coil, and routing
refrigerant from said outdoor coil operating as an evaporator coil
through said tenth and eleventh tubes into said accumulator means,
said fourth and fifth valves being closed during heating operation,
said reversal means in cooling position routing discharge gas
through said 10th tube into said outdoor coil operating as a
condenser coil, and routing refrigerant from said second indoor
coil operating as an evaporator coil through said first and fifth
valves into said first indoor coil operating as an evaporator coil
and from said first indoor coil through said second and 11th tubes
into said accumulator means, said second, third and fourth valves
being closed during cooling operation, said reversal means in
defrosting position routing discharge gas through said tenth tube
into said outdoor coil operating as a condesnser coil, and routing
refrigerant from said heating means through said second and 11th
tubes into said accumulator means, said third valve being opened
during defrosting operation, said reversal means in dehumidifying
position routing discharge gas through said tenth tube into said
outdoor coil operating as a condenser coil, and routing refrigerant
from said second indoor coil operating as a condenser coil through
said first capillary tube into said first indoor coil operating as
an evaporator coil and from said first indoor coil through said
second and 11th tubes into said accumulator means, said first,
second and third valves being closed during dehumidifying
operation.
Description
FIELD OF THE INVENTION
The field of the invention is air conditioning systems of the heat
pump type in which atmospheric air is utilized as a heat source. It
is well known in the art that air conditioning systems of the heat
pump type operate to transfer heat from outdoor air to an indoor
heat exchanger operating as a condenser. In the systems of this
type, however, at low outdoor temperatures the heating capacity
becomes poor so that they cannot cope with the increased heating
load. Another disadvantage of a heat pump type air conditioner is
that the desired level of heating cannot be achieved quickly on
start-up of the system.
Various well-known arrangements are available for obviating the
above-mentioned disadvantages of the heat pump type air
conditioning equipment. For example, one arrangement includes an
electric heating device provided within the indoor heat exchanger
unit to heat the air circulating therethrough. In another
arrangement, the indoor heat exchanger comprises two separate coils
between which is located an electric heater for heating the
refrigerant flowing from the first coil to the second. A third
arrangement also includes an electric heater located in the suction
gas tube of a compressor so that the heat absorbed by the
refrigerant gas is transfered to the indoor heat exchanger. A
fourth arrangement includes a combined indoor unit of a heat pump
type air conditioner and of the one in which hot water is
circulated in the heat exchanger. However, these arrangements of
the existing type raise many problems in the design and engineering
thereof, especially in he location of electric heating, or have
other deficiencies which exclude their adaptation from use in an
air conditioning equipment of the present type.
SUMMARY OF THE INVENTION
The invention is embodied in an air conditioning system of the heat
pump type having means for feeding a portion of the high pressure
refrigerant liquid leaving an indoor heat exchanger back to the
inlet thereof, and having means for heating the high pressure
refrigerant liquid before entering the indoor heat exchanger.
An object of the present invention is to provide a by-pass line for
feeding regrigerant liquid from a receiver to the line connecting
the compressor discharge and the inlet of an indoor heat
exchanger.
Another object of the present invention is to provide an electric
heating means for heating the refrigerant liquid by-passed from a
receiver before or after being mixed into the discharge gas flowing
from the compressor.
A further object of the present invention is to provide an ejector
means for introducing the refrigerant liquid by-passed from a
receiver into the line connecting the compressor discharge and the
inlet of an indoor heat exchanger.
A further object of the present invention is to provide an air
conditioning system of the heat pump type that can perform a
heating operation in a satisfactory manner regardless of ambient or
load conditions.
A still further object of the present invention is to provide an
air conditioning system of the heat pump type in which the desired
level of heating can be achieved quickly on start-up of the
system.
Still another object of the present invention is to provide an air
conditioning system of the heat pump type in which "hot gas"
defrosting is accomplished with increased efficiency through
utilization of the heat of refrigerant liquid received from an
electric heating means.
A still further object of the present invention is to provide an
air conditioning system of the heat pump type characterized by its
ability to operate as a dehumidifier as well.
These and still other objects and advantages of the present
invention will become more apparent hereinafter.
FIG. 1 is a diagrammatic view of an air conditioning system
according to the present invention;
FIG. 2 is a Mollier diagram for use in explaining the heating
operation of the system shown in FIG. 1;
FIG. 3 is an illustration of a typical air conditioning system of
the invention;
FIG. 4 is an illustration of another form of the invention; and
FIG. 5 is an illustration of still another form of the
invention.
DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION
Referring now to FIG. 1, a refrigerant compressor C is connected by
a discharge gas tube 10 to a reversal valve 11 which is connected
by a tube 12 to an indoor doil 13, and by a tube 14 to an outdoor
coil 15. The reversal valve 11 is a four-way valve that is capable
of selectively directing the flow of refrigerant to the outdoor
coil 15 and the indoor coil 13 so as to set the system for cooling
and heating operations, respectively. The indoor coil 13 as
connected by a tube 20 to a parallel combination of an expansion
valve and a check valve, generally designated at 21, which is
connected by a tube 22 to a receiver 23 forming a liquid
refrigerant source for operating the system. The check valve of the
valve arrangement 21 is so arranged as to permit the flor of
refrigerant in one direction, i.e., from the indoor coil flow to
the receiver 23. The outlet of the receiver 23 is connected by a
tube 24 to another parallel combination of an expansion valve and a
check valve, generally designated at 25, which in turn is connected
by a tube 26 to the outdoor coil 15. The check valve of the valve
arrangement 25 is arranged so that it permits the flow of
refrigerant in one direction, i.e., from the outdoor coil 15 to the
receiver 23. The suction side of the compressor C is connected by a
suction gas tube 28 to the four-way valve 11 by which the tube 28
is kept in communication with the tube 12 leading to the indoor
coil 13 during cooling operation, and with the tube 14 leading to
the outdoor coil 15 during heating operation.
The receiver 23 has an outlet 30 connected by a by-pass tube 31 to
the inlet of a liquid pump 32 which is adapted to supply a portion
of the refrigerant liquid stored in the receiver 23, to a heat
exchanger 33 connected to the outlet of the pump 32. The heat
exchanger 33 includes a heat exchange coil (not shown) which is
surrounded by a heat accumulating medium to provide heat transfer
from the medium to the refrigerant flowing through the heat
exchange coil. The outlet of the heat exchanger 33 is connected by
a by-pass tube 35 to a valve 36, the outlet of which is connected
by a by-pass tube 37 to the tube 12 connecting the reversal valve
11 and the indoor coil 13.
The system is so designed that when, at low outdoor temperatures or
at starting-up, the pump 32 is actuated, and the valve 36 is
opened, the pump 32 supplies a portion of the refrigerant liquid
stored in the receiver 23 into he heat exchanger 33 where it is
evaporated by heat from the heat accumulating medium provided
therein. The refrigerant gas thus generated flows from the heat
exchanger 33 through the tube 35, the valve 36, and the tube 37
into the tube 12, and from the latter, together with the high
pressure discharge gas flowing from the compressor C, to the indoor
coil 13 operating as a condenser coil. During condensation, the
heat of the refrigerant gas received from the heat accumulating
medium is transfered to the indoor coil 13, thus greatly increasing
the heating effect.
The heating cycle of the system according to the invention will be
described in greater detail by reference to the Mollier diagram of
FIG. 2 in which the axis of abscissa indicates enthalpy (i) of the
refrigerant and the axis of ordinate indicates pressure thereof.
The refrigerant gas flowing from the outdoor coil 15, after being
adiabatically compressed by the compressor C, is in the state
indicated at (a) in the diagram. When the refrigerant flows from
the compressor C through the tube 12 into the indoor coil 13, the
state of the refrigerant will reach the point indicated at (b).
Within the indoor coil 13 the refrigerant is condensed while
releasing the heat stored, so that the state of the refrigerant is
changed from (b) to (c). Then, the refrigerant liquid flows through
the check valve of the valve arrangement 21 into the receiver 23.
Since, during normal heating operation, the valve 36 is in the
closed position, the refrigerant flows from the receiver 23 into
the expansion valve of the valve arrangement 25 where the expansion
of the refrigerant takes place. The expanded refrigerant, which is
in the state indicated at (d), flows from the expansion valve into
the outdoor coil 15 operating as an evaporator coil. The
evaporation of the refrigerant liquid within the outdoor coil 15 is
accomplished with heat from the outdoor air so that the state of
the refrigerant will change to the point indicated at (e). As
previously explained, the evaporated refrigerant is sucked into the
compressor C and then compressed thereby, returning to the state
(a), whereby one heating cycle is completed.
At times, such as at low outdoor temperatures or at starting-up,
the valve 36 is opened and simultaneously the liquid pump 32 is
actuatted. Under this condition, a portion of the refrigerant
liquid in the receiver 23 is diverted to the heat exchanger 33
where it is evaporated by heat from the heat accumulating medium.
Absorbing the heat from the medium, the refrigerant is changed from
the state (c) to (f). The refrigerant with increased enthalpy
i.sub.f is then mixed with the discharge gas flowing from the
compressor C, and the resulting flow of refrigerant gas is supplied
to the indoor coil 13 operating as an evaporator coil. When
evaporated, the refrigerant gas releases the heat received from the
heat accumulating medium, returning to the point (c), whereby one
heating subcycle is completed.
Now, if it is assumed that the amount of refrigerant circulating in
the system during the normal heating operation is represented by
G.sub.1 kg/Hr, then the heating capacity of the system operating as
a heat pump is expressed by the following:
(i.sub.b - i.sub.c).sup.. G.sub.1 Kcal/Hr. Further, if it is
assumed that, during the operation of the subcycle, the amount of
refrigerant supplied from the compressor C and that of the
refrigerant circulating in the subcycle are represented by G'.sub.1
and G'.sub.2, respectively, then the total of the amount of the
refrigerant flowing through the indoor coil 13 will be (G'.sub.1 +
G'.sub.2) Kg/Hr. Under this condition, the heating capacity of the
entire system will be approximately equal to (i.sub.b -
i.sub.c)(G'.sub.1 + G'.sub.2) K Kcal/Hr, if i.sub.f is
approximately equal to i.sub.b. Since G'.sub.1 is approximately
equal to G.sub.1, it will be appreciated that there is a marked
increase of (i.sub.b - i.sub.c).sup.. G'.sub.2 in the heating
capacity of the entire system. If the heat accumulating medium is
maintained at such high temperatures that i.sub.f >i.sub.b, the
heating effect becomes still stronger, and the desired level of
heating can be achieved more quickly on start-up of the system.
Thus, it will be appreciated that the operation of the subcycle may
be initiated by opening the valve 36 and simultaneously actuating
the liquid pump 32, when there is greater heating load being
imposed on the system, such as at low outdoor temperatures or at
starting-up.
The air conditioning system operates as a heat pump in the
above-mentioned manner, resulting in the formation of frost or ice
on the outdoor coil operating as an evaporator coil. In the present
system, hot gas defrosting is employed by reversing the flow of
refrigerant as in the case of cooling operation. In so doing, the
reversal valve 11 is first switched to provide communication
between the gas discharge tube 10 and the tube 14. As a result, the
compressed discharge gas flows from the compressor C through the
discharge tube 10, the reversal valve 11, and the tube 14 into the
outdoor coil 15 operating as a condenser coil. Since the gaseous
refrigerant flowing into the outdoor coil 15 is at high
temperatures, it heats the coil 15, removing the frost or ice
accumulation. The condensed refrigerant gas flows from the outdoor
coil 15 through the check valve of the valve arrangement 25 into
the receiver 23, and from the latter through the liquid pump 32
into the heat exchanger 33 where it is evaporated by heat from the
heat accumulating medium. Hot evaporated refrigerant flows from the
heat exchanger 33 through the tube 35, the valve 36, the tube 37,
the tube 12, the reversal valve 11, an accumulator (not shown), and
the suction gas tube 28 into the compressor C. This hot gas
defrosting method is highly effective in removing the frost or ice
accumulation, due to the utilization of the heat stored in the heat
accumulating medium. Further, since the indoor coil 13 is not
included in the hot gas defrost arrangement, the indoor coil does
not operate as an evaporator coil during defrosting operation. This
means that the air circulating through the indoor coil 13 is not
cooled.
During cooling operation, the valve 36 is held in the closed
position and the liquid pump 32 is kept deactuated. The compressor
C supplies discharge gas through the tube 10, the reversal valve
11, and the tube 14 into the outdoor coil 15 operating as a
condenser coil. Refrigerant liquid flows from the outdoor coil 15
through the tube 26, the check valve of the valve arrangement 25,
and the tube 24 into the receiver 23, and from the latter through
the tube 22 into the expansion valve of the valve arrangement 21.
Expanded refrigerant flows from the expansion valve through the
tube 20 into the indoor coil 13 operating as an evaporator coil.
Gas and unevaporated refrigerant liquid flow from the indoor coil
13 through the tube 12, the reversal valve 11 into an accumulator
(not shown). The refrigerant gas flows from the accumulator through
the suction gas tube 28 into the compressor C.
Referring to FIG. 3, there is illustrated a typical air
conditioning system constructed in accordance with the teachings of
FIG. 1. The system comprises an indoor unit 50, an outdoor unit 51
and two conduits or tubes 52 and 53 connecting both units. The
conduits 52 and 53 each have a covering of thermally insulating
material attached therearound which provides thermal insulation of
the refrigerant flowing therethrough from outdoor air.
As shown, the outdoor unit 51 is divided into two compartments, the
lower of which forms a machinery space and the upper of which is
used for mounting the heat exchanger 33. Situated on the bottom of
the machinery space is a refrigerant compressor C' having a
discharge or high pressure side 60 with a discharge tube 10'
through which hot compressed gaseous refrigerant is discharged to a
reversal valve 11'. The reversal valve 11' is a four-way valve
adapted to direct the flow of refrigerant selectively to an indoor
coil 13' and an outdoor coil 15'. During heating operation, the
reversal valve 11' provides communication between the tubes 10' and
12' so as to permit the flow of refrigerant from the compressor C'
to the indoor coil 13', while, during the operations of both
cooling and defrosting, the tube 10' is kept in communication with
a tube 14' by the reversal valve 11' so that the refrigerant gas
flows through the tube 10', the reversal valve 11', and the tube
14' into the outdoor coil 15'. The outdoor coil 15' operates as a
condenser coil during both the cooling and defrosting operations,
and as an evaporator coil during the heating operation. An electric
fan 64 is provided adjacent the outdoor coil 15' to cool the coil
and is electrically driven by a motor 65. The wall of the outdoor
unit 51 is provided with a louver 66 adjacent the outdoor coil 15'.
The lower end of the outdoor coil 15' is connected by a tube 26' to
a valve arrangement 25' comprising an expansion valve 67 and a
unidirectional or check valve 68 connected in parallel with each
other. As previously explained in connection with the diagram of
FIG. 1, the check valve 68 is so arranged as to permit refrigerant
flow from the outdoor coil 15' to a receiver 23'. The receiver 23'
is connected to a liquid pump 32' which in turn is connected by a
tube 70 to one end of a coil 72 forming a part of the heat
exchanger 33'. The other end of the heat exchange coil 72 is
connected by a tube 35' to a valve 36'. In the illustrated
embodiment, the heat exchanger 33' comprises a reservoir 73 for
storing a heat accumulating medium 74, such as water, which is kept
at high temperatures to heat the refrigerant flowing through the
heat exchange coil 72. Extending generally horizontally within the
reservoir 73 is an electric heater 76 for heating the heat
accumulating medium 74. It would be advantageous to energize the
electric heater 76 to store heat in the medium in the nighttime,
such as at off-peak time of power demand, since an economical
surplus power is available. The reservoir 73 is surrounded or
covered by a thermally insulating material 78 and has an inlet 79
on its top for use in introducing the heat accumulating medium
thereinto, the inlet 79 being closed by a closure member 80.
The valve 36' is connected by a tube 37' to a tube 12' which in
turn is connected by a joint 85 to the tube 52. A tube 22' leading
from the receiver 23' is connected by a joint 87 to the tube 53.
The reversal valve 11' is connected by a tube 28' to the suction
side 89 of the compressor C'. An accumulator 90 is provided
intermediate the suction gas tube 28'.
The indoor unit 50 is, as shown, situated on a shelf 100 and
includes an indoor coil 13' which operates as an evaporator coil
during the cooling operation, and as a condenser coil during the
heating operation. The indoor coil 13' has its top end connected to
a tube 102 which in turn is connected by a joint 104 to the tube
52. The bottom end of the indoor coil 13' is connected by a tube
20' to a valve arrangement 21' comprising an expansion valve 106
and a check valve 107, which arrangement is connected by a joint
108 to the tube 53. The check valve 107 is arranged to permit
refrigerant flow from the indoor coil 13' toward the outdoor unit
51. An electric fan 110 is provided within the indoor unit 50 also,
which serves to circulate through a grill 112 the air cooled or
heated by the indoor coil 13'. A description of the operation of
the system shown in FIG. 3 is herein omitted, since the system as
shown is identical in structure to that of FIG. 1.
Referring to FIG. 4, there is illustrated another from of the air
conditioning system of the present invention which differs from
that of FIG. 3 in the provision of an ejector means 120 for
introducing the high pressure refrigerant liquid into the discharge
gas flowing from the compressor C". Another difference of the
present system lies in the fact that an electric heating means 122
is provided to heat the high pressure refrigerant liquid after
having been mixed with the discharge gas.
In this embodiment, a receiver 23" is connected by a tube 125 to a
valve 36", with the end of the tube 125 in the bottom of the
receiver 23". The valve 36" is connected by a tube 127 to the
ejector 120 which operates to suck the refrigerant liquid stored in
the receiver 23" and to supply it in a sprayed form into the
discharge gas flowing from the compressor C". The ejector 120 is
connected to the electric heating means 122 including a U-shaped
heating element 129. The electric heating means 122 in turn is
connected by a tube 130 to the tube 52" leading to an indoor coil
13".
Where it is desired to operate the system as a heat pump, the
reversal valve 11" is arranged to provide communication between a
discharge gas tube 10" and the tube 12" and between a tube 14" and
a tube 28". With the reversal valve 11" in this position, the
compressor C" supplies discharge gas through the tube 10", the
reversal valve 11", the tube 12", the ejector 120, the electric
heating means 122, the tube 130, the tube 52", and a tube 102" into
the indoor coil 13" operating as a condenser coil. Condensed
refrigerant flows from the coil 13" through a tube 20", a check
valve 107", a tube 53", a tube 22" into the receiver 23", and from
the latter through the tube 24" into an expansion valve 67".
Expanded refrigerant flows from the valve 67" through a tube 26"
into the outdoor coil 15" operating as an evaporator coil. Gas and
unevaporated refrigerant liquid flow from the coil 15" through a
tube 14", the reversal valve 11", the tube 28", and an accumulator
90" into the suction side of the compressor C".
When, at low outdoor temperatures or at starting-up, the valve 36"
is opened and the electric heating means 122 is energized, the
refrigerant liquid by-passed from the receiver 23" is mixed in a
sprayed form with the discharge gas by the ejector 120, the
resulting refrigerant being supplied to the electric heating means
122 where the evaporation of the refrigerant liquid takes place.
The refrigerant gas, when condensed within the indoor coil 13",
releases the heat received from the electric heating means 122,
thus greatly increasing the heating effect. On the other hand,
during both the cooling and defrosting operations, the system
operates in a manner identical to that already explained in
connection with the embodiment of FIG. 3.
Referring to FIG. 5, there is illustrated a further modification of
the air conditioning system according to the present invention. One
feature of this embodiment lies in the ability to operate as a
dehumidifier as well for removing atmospheric moisture present in
the room.
In this embodiment, a receiver 23'"is connected by a tube 140 to
the inlet of an electric heating means 122'" for heating the
refrigerant liquid flowing from the receiver 23'". The electric
heating means 122'" includes a U-shaped heating element 129'" and
has its outlet connected to a valve 36'". The valve 36'" is
connected to one inlet of an ejector means 120'" of the type
similar to that shown in FIG. 4. The ejector means 120'" is
provided intermediate a tube 12'" connecting a reversal valve 11'"
to a tube 52'" which in turn is connected by a tube 102'" to a
first indoor coil 13a'". As will be readily apparent, the outdoor
unit 51'" of this embodiment is different from that shown in FIG. 4
in that the location of the electric heating means 122'" is
modified so that the refrigerant liquid is heated before being
mixed with the discharge gas flowing from the compressor C'".
The first indoor coil 13a'" has its bottom end connected by a tube
150 to a valve 152 which in turn is connected by a tube 154 to the
top end of a second indoor coil 13b'". The bottom ends of the first
and second indoor coils 13a'" and 13b'" are connected to each other
by a capillary tube 156. The bottom end of the second indoor coil
13b'" is also connected to a parallel combination of a capillary
tube 158 and a check valve 160, which combination is connected by a
tube 162 to a tube 53'" leading to the receiver 23'" located in the
outdoor unit 51'". A valve 164 is provided between the tube 154 and
the tube 162.
In order to operate the system as a heat pump, the valve 152 should
be kept in the open position with the valve 164 closed. The
compressor C'" supplies discharge gas through the tube 10'", the
reversal valve 11'", the tube 12'", the ejector means 120'", the
tube 52'", the tube 102'" into the first indoor coil 13a'"
operating as a condenser coil. Liquid and uncondensed refrigerant
gas flow from the first indoor coil 13a'" through the tube 150, the
valve 152, and the tube 154 into the second indoor coil 13b'" also
operating as a condenser coil. Condensed refrigerant flows from the
second indoor coil 13b'" through the check valve 160, the tube 162,
the tube 53'", a tube 22'", and the receiver 23'", and from the
latter through a tube 24'" into an expansion valve 67'". Expanded
refrigerant flows from the valve 67'" through a tube 26'" into an
outdoor coil 15'" operating as an evaporator coil. Gas and
unevaporated refrigerant liquid flow from the outdoor coil 15'"
through a tube 14'", the reversal valve 11'", a tube 28'", and an
accumulator 90'" into the suction side of the compressor C'".
At times, such as at low outdoor temperatures or at starting-up,
the valve 36'" is opened and the electric heating means 122'" is
energized. Under this condition, portion of the refrigerant liquid
stored in the receiver 23'" is sucked into the electric heating
means 122'" where it is evaporated by heat therefrom. The hot
refrigerant gas thus produced is sucked within the ejector means
120'" into the flow of compressed discharge gas from the compressor
C'" and then is supplied to the first and second indoor coils 13a'"
and 13b'", thereby greatly increasing the heating effect.
During the cooling operation, the valves 152 and 164 remain opened
and closed, respectively. The compressor C'" supplies discharge gas
through the tube 10'", the reversal valve 11'", and the tube 14'"
into the outdoor coil 15'" operating as a condenser coil. Liquid
and condensed refrigerant gas flow from the outdoor coil 15'"
through the tube 26'", and a check valve 68'" into the receiver
23'", and from the latter through the tube 22'", the tube 53'", the
tube 162, and the capillary tube 158 into the second indoor coil
15b'" operating as an evaporator coil. Gas and unevaporated
refrigerant liquid flow from the second indoor coil 15b'" through
the tube 154, the valve 152, and the tube 150 into the first indoor
coil 13a'" also operating as an evaporator coil. Evaporated
refrigerant flows from the first indoor coil 13a'" through the tube
102'", the tube 52'", the tube 12'", the ejector means 120'", the
reversal valve 11'", the tube 28'", and the accumulator 90'" into
the compressor C'".
For the system to operate as a dehumidifier, the valves 152 and 164
are closed and opened, respectively, with the reversal valve 11'"
in the same position as during the cooling operation. The
compressor C'" supplies discharge gas through the tube 10'", the
reversal valve 11'", the tube 14'" into the outdoor coil 15'"
operating as a condenser coil. Refrigerant liquid flows from the
outdoor coil 15'" through the tube 26'" and the check valve 68'"
into the receiver 23'", and from the latter through the tube 22'",
the tube 53'", the tube 162, the valve 164, and the tube 102'" into
the second indoor coil 13b'" operating as a condenser coil.
Condensed refrigerant flows from the second indoor coil 13b'"
through the capillary tube 156 into the first indoor coil 13a'"
operating as an evaporator coil. Evaporated refrigerant flows from
the first indoor coil 13a'" through the tube 102'", the tube 52'",
the tube 12'", the ejector means 120'", the reversal valve 11'",
the tube 28'", and the accumulator 90'" into the compressor C'". As
described above, during the dehumidifying operation, the first and
second indoor coils 13a'" and 13b'" operate as an evaporator coil
and a condenser coil, respectively. Thus, the air in the room is
first cooled and dehumidified by the first indoor coil 13a'" and
then is heated by the second indoor coil 13b'" up to approximately
the room temperature. Accordingly, it should be understood that the
system is capable of dehumidifying the air in the room without
causing any reduction in room temperature.
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