TECHNICAL FIELD
[0001] The present disclosure relates to an air conditioner.
BACKGROUND ART
[0002] Due to requirements by European refrigerant regulations and the like, it has been
required to use refrigerant having a low global warming potential (GWP) also as refrigerant
used for a refrigeration cycle of an air conditioner.
Japanese Patent Laying-Open No. 2009-162403 (PTL 1) discloses an air conditioner that uses HC refrigerant having a low GWP, that
is, propane (R290) or isobutane, as refrigerant for a refrigerant circuit. This air
conditioner uses an internal heat exchanger in order to increase efficiency.
CITATION LIST
PATENT LITERATURE
SUMMARY OF INVENTION
TECHNICAL PROBLEM
[0004] However, when the internal heat exchanger is used, the density of the refrigerant
suctioned into a compressor decreases. Accordingly, there may be a case where the
performance of a refrigeration cycle is not sufficiently improved even though the
internal heat exchanger is provided. Further, in a case where an attempt is made to
increase the amount of heat exchange in the internal heat exchanger, as heat exchange
between high-temperature refrigerant and low-temperature refrigerant within the internal
heat exchange proceeds, the temperature difference between the refrigerants decreases,
and thus heat exchange efficiency is worsened. Accordingly, it is necessary to increase
lengths of flow paths for the refrigerants that exchange heat in the internal heat
exchanger, and there has been a problem that the internal heat exchanger becomes too
large.
[0005] The present disclosure has been made in order to solve the aforementioned problem,
and an object thereof is to disclose an air conditioner capable of achieving further
improved performance of a refrigeration cycle that uses an internal heat exchanger,
while keeping the internal heat exchanger to have a small size.
SOLUTION TO PROBLEM
[0006] The present disclosure relates to an air conditioner. The air conditioner includes:
a refrigerant circuit including at least a compressor, a condenser, an expansion valve,
and an evaporator, the refrigerant circuit being configured to circulate refrigerant;
a first heat exchanger having a first flow path in which the refrigerant that has
passed through the condenser flows, and a second flow path in which the refrigerant
that is to be suctioned into the compressor flows, and being configured to exchange
heat between the refrigerant flowing through the first flow path and the refrigerant
flowing through the second flow path; a second heat exchanger having a third flow
path in which the refrigerant directed from an outlet of the second flow path toward
the compressor flows, and a fourth flow path in which a heat medium flows, and being
configured to exchange heat between the refrigerant flowing through the third flow
path and the heat medium flowing through the fourth flow path; a flow rate adjusting
device configured to adjust an amount of the heat medium supplied to the second heat
exchanger; a temperature sensor configured to detect a temperature of the heat medium;
and a controller configured to control the flow rate adjusting device in accordance
with an output of the temperature sensor.
ADVANTAGEOUS EFFECTS OF INVENTION
[0007] The air conditioner according to the present disclosure can obtain an effect caused
by an increase in enthalpy difference in the evaporator without reducing the density
of the refrigerant suctioned into the compressor. This enables further improved performance
of a refrigeration cycle that uses an internal heat exchanger.
BRIEF DESCRIPTION OF DRAWINGS
[0008]
Fig. 1 is a view showing a configuration of an air conditioner 1000 according to a
first embodiment.
Fig. 2 is a view showing a configuration of an air conditioner 2000 in a study example.
Fig. 3 is a PH diagram of a refrigeration cycle that uses R290 refrigerant and has
no internal heat exchanger, in the configuration in the study example.
Fig. 4 is a PH diagram of a refrigeration cycle that uses the R290 refrigerant and
has an internal heat exchanger, in the configuration in the study example.
Fig. 5 is a PH diagram of a refrigeration cycle that uses the R290 refrigerant and
has an internal heat exchanger and an external heat exchanger, in the configuration
in the first embodiment.
Fig. 6 is a perspective view showing an external appearance of an internal heat exchanger
250.
Fig. 7 is a cross-sectional view of internal heat exchanger 250 in a cross section
F1 in Fig. 6.
Fig. 8 is a perspective view showing an external appearance of an external heat exchanger
400.
Fig. 9 is a cross-sectional view of external heat exchanger 400 in a cross section
F2 in Fig. 8.
Fig. 10 is a flowchart for illustrating control of a flow rate adjusting device 420
during cooling.
Fig. 11 is a flowchart for illustrating control of an expansion valve 230 during cooling.
Fig. 12 is a view showing a configuration of an air conditioner 1001 having sensors
used during heating added thereto.
Fig. 13 is a flowchart for illustrating control of flow rate adjusting device 420
during heating.
Fig. 14 is a view showing a configuration of an air conditioner 1002 according to
a second embodiment.
DESCRIPTION OF EMBODIMENTS
[0009] Hereinafter, embodiments of the present disclosure will be described in detail with
reference to the drawings. In the following, a plurality of embodiments will be described,
and it is originally intended from the time of filing the present application to combine
configurations described in the embodiments as appropriate. It should be noted that
identical or corresponding parts in the drawings will be designated by the same reference
characters, and the description thereof will not be repeated. In the following drawings,
the relation between components in terms of size may be different from the actual
one.
First Embodiment
[0010] Fig. 1 is a view showing a configuration of an air conditioner 1000 according to
a first embodiment. Air conditioner 1000 shown in Fig. 1 includes a refrigerant circuit
500, an internal heat exchanger 250, an external heat exchanger 400, a flow rate adjusting
device 420, and a controller 100.
[0011] Refrigerant circuit 500 includes at least a compressor 200, an outdoor heat exchanger
210, an expansion valve 230, and an indoor heat exchanger 110, and is configured to
circulate refrigerant. As the refrigerant, R290 is used, for example. In the example
in Fig. 1, refrigerant circuit 500 is constituted by compressor 200, outdoor heat
exchanger 210, an outdoor blower 220, expansion valve 230, a four-way valve 240, indoor
heat exchanger 110, and an indoor blower 120. Four-way valve 240 has ports P1 to P4.
As expansion valve 230, an electronic expansion valve (LEV: Linear Expansion Valve)
can be used, for example.
[0012] Compressor 200 is configured to change its operating frequency, in accordance with
a control signal received from controller 100. Specifically, compressor 200 includes
therein a drive motor variable in rotational speed under inverter control and, when
the operating frequency is changed, the rotational speed of the drive motor is changed.
By changing the operating frequency of compressor 200, an output of compressor 200
is adjusted. Compressor 200 of any of various types such as rotary type, reciprocating
type, scroll type, and screw type, for example, may be employed.
[0013] Four-way valve 240 is controlled into one of a cooling operation state and a heating
operation state, by a control signal received from controller 100. The cooling operation
state refers to a state in which port P1 and port P4 communicate with each other and
port P2 and port P3 communicate with each other, as indicated by broken lines. The
heating operation state refers to a state in which port P1 and port P3 communicate
with each other and port P2 and port P4 communicate with each other, as indicated
by solid lines. By operating compressor 200 in the cooling operation state, the refrigerant
circulates through the refrigerant circuit in a direction indicated by broken-line
arrows. Further, by operating compressor 200 in the heating operation state, the refrigerant
circulates through the refrigerant circuit in a direction indicated by solid-line
arrows.
[0014] Internal heat exchanger 250 includes a flow path R1 and a flow path R2. In flow path
R1, high-pressure and high-temperature refrigerant that has passed through a condenser
(outdoor heat exchanger 210) flows during cooling. In flow path R2, low-pressure and
low-temperature refrigerant that is suctioned by compressor 200 flows. Internal heat
exchanger 250 is configured to exchange heat between the high-pressure and high-temperature
refrigerant having passed through the condenser (outdoor heat exchanger 210) and the
low-pressure and low-temperature refrigerant to be suctioned by compressor 200, during
cooling.
[0015] External heat exchanger 400 includes a flow path R3 and a flow path R4. In flow path
R3, the refrigerant directed from an outlet of second flow path R2 toward compressor
200 flows. In flow path R4, external heat medium for cooling conveyed through a flow
path 410 flows. External heat exchanger 400 is configured to exchange heat between
the refrigerant that flows through flow path R3 and the external heat medium for cooling
that flows through flow path R4. Here, water is used as the heat medium for cooling.
The water may be circulated such that it passes through internal heat exchanger 250,
then is cooled at a cooling tower or the like, and thereafter is supplied again through
flow path 410, for example. Further, drain water from an evaporator, tap water, groundwater,
or the like may flow without circulation. It is sufficient as long as the heat medium
can cool the internal heat exchanger, and a flow path through which the heat medium
passes may not necessarily be provided inside. For example, external heat exchanger
400 may be cooled by spraying water from outside.
[0016] Flow rate adjusting device 420 adjusts the amount of the heat medium such as water
supplied to external heat exchanger 400 to cool external heat exchanger 400. As flow
rate adjusting device 420, a control valve having an opening degree that changes from
0 to 100% in accordance with a control signal, or the like can be used, for example.
[0017] Air conditioner 1000 further includes temperature sensors 260 to 263 and 411. Temperature
sensor 260 is arranged on a suction pipe of compressor 200 to measure a suction temperature
T260 of the refrigerant. Temperature sensor 261 is arranged on a pipe that connects
flow path R2 of internal heat exchanger 250 and flow path R3 of external heat exchanger
400 to measure a refrigerant temperature T261. Temperature sensor 262 is arranged
in indoor heat exchanger 110 to measure a refrigerant temperature T262, which serves
as an evaporation temperature during cooling and as a condensation temperature during
heating. Temperature sensor 263 is arranged on a pipe that connects indoor heat exchanger
110 and port P3 of four-way valve 240 to measure a refrigerant temperature T263.
[0018] Temperature sensor 411 detects a temperature T411 of the heat medium such as water.
If the water temperature is lower than the temperature of the low-pressure refrigerant
at an inlet portion of external heat exchanger 400 obtained by temperature sensor
261, the water can cool external heat exchanger 400. Thus the temperature of the low-pressure
refrigerant having its temperature increased through heat exchange with the high-pressure
refrigerant in internal heat exchanger 250 can be reduced.
[0019] Controller 100 is configured to control flow rate adjusting device 420 in accordance
with an output of temperature sensor 411. Further, controller 100 controls the opening
degree of expansion valve 230 to adjust an SH (superheat) of the refrigerant at an
outlet portion of the evaporator.
[0020] Controller 100 has a configuration including a CPU (Central Processing Unit) 101,
a memory 102 (ROM (Read Only Memory) and a RAM (Random Access Memory)), input/output
buffers (not shown), and the like. CPU 101 expands programs stored in the ROM onto
the RAM or the like and executes the programs. The programs stored in the ROM are
programs describing processing procedures of controller 100. In accordance with these
programs, controller 100 performs control of devices in air conditioner 1000. This
control can be processed not only by software but also by dedicated hardware (electronic
circuitry).
[0021] Fig. 2 is a view showing a configuration of an air conditioner 2000 in a study example.
Air conditioner 1000 in Fig. 1 includes external heat exchanger 400 that can be cooled
with water, whereas air conditioner 2000 differs from air conditioner 1000 in that
air conditioner 2000 does not include external heat exchanger 400. Internal heat exchanger
550 shown in Fig. 2 is configured to exchange heat between high-temperature and high-pressure
refrigerant that has flowed out of an outlet of outdoor heat exchanger 210 and low-temperature
and low-pressure refrigerant that is suctioned into compressor 200 during cooling.
[0022] How the PH diagram changes due to such a difference in the internal heat exchanger
will be described below using Figs. 3 to 5.
[0023] Fig. 3 is a PH diagram of a refrigeration cycle that uses R290 refrigerant and has
no internal heat exchanger, in the configuration in the study example. Fig. 4 is a
PH diagram of a refrigeration cycle that uses the R290 refrigerant and has an internal
heat exchanger, in the configuration in the study example. Fig. 5 is a PH diagram
of a refrigeration cycle that uses the R290 refrigerant and has an internal heat exchanger
and an external heat exchanger, in the configuration in the first embodiment.
[0024] The result in the case of having no internal heat exchanger shown in Fig. 3 was calculated
under the conditions of a suction superheat (SH) of 5 deg, a supercool (SC) of 5 deg,
an evaporation temperature (ET) of 17°C, a condensation temperature (CT) of 40°C,
and a compressor efficiency of 1. On the other hand, the result in the case of having
an internal heat exchanger shown in Fig. 4 was calculated assuming that the low-temperature
and low-pressure refrigerant at an outlet of an evaporator exchanged heat with the
high-temperature and high-pressure refrigerant at an outlet of a condenser by means
of internal heat exchanger 550, and as a result the temperature thereof increased
by 10°C. Since the capacity of the compressor is the same in both Figs. 3 and 4, evaporation
temperature (ET) is the same regardless of the evaporator outlet temperature.
[0025] Here, the reason why the performance of the refrigeration cycle is improved by using
external heat exchanger 400 for the refrigeration cycle that uses the R290 refrigerant
will be described. It can be seen from the comparison between Fig. 3 and Fig. 4 that,
in the case of using external heat exchanger 400, an enthalpy difference between an
inlet and the outlet of the evaporator increases by Δh [kJ/kg]. Actually, enthalpy
difference Δhe of the evaporator in Fig. 3 is represented by Δhe = h(A1)-h(D1) = 309.7,
whereas enthalpy difference Δhe of the evaporator in Fig. 4 is represented by Δhe
= h(A2)-h(D2) = 328.8, indicating that enthalpy difference Δhe of the evaporator increases
by Δh = 19.1 (6.2%) which is the amount of heat exchange in the internal heat exchanger.
[0026] On the other hand, a suction density ρs [kg/m
3] in the case of having no internal heat exchanger is represented by ρs = 16.22, whereas
suction density ρs in the case of having an internal heat exchanger is represented
by ρs = 15.38, indicating a decrease by Δρ = 0.84 (5.2%). A capability Q is represented
by Q = GrΔhe (∝ ρsΔhe) using a circulation flow rate Gr. Therefore, it is found that
capability Q can be increased if an increased amount of evaporator enthalpy difference
Δhe acts more greatly than a decreased amount of suction density ρs by using an internal
heat exchanger.
[0027] As capability Q increases, a COP of air conditioning equipment increases. Actually,
in the case of using the R290 refrigerant, the increased amount of evaporator enthalpy
difference Δhe acts more greatly than the decreased amount of suction density ρs as
described above, and thus it is possible to improve the COP of the air conditioning
equipment by using an internal heat exchanger.
[0028] However, when internal heat exchanger 550 is used, a compressor suction point deviates
to the right to cross an isothermal line, a gas temperature rises, and the suction
density decreases. Accordingly, the effect caused by the increase in evaporator enthalpy
difference cannot necessarily be enjoyed to the maximum. For example, in the case
of using refrigerant such as R32 or R410, the decrease in suction density and the
increase in evaporator enthalpy difference offset each other, and thus the effect
of the internal heat exchanger cannot be obtained. Further, in a case where an attempt
is made to increase the amount of heat exchange in the internal heat exchanger, as
heat exchange between high-temperature refrigerant and low-temperature refrigerant
within the internal heat exchange proceeds, the temperature difference between the
refrigerants decreases, and thus heat exchange efficiency is worsened. Accordingly,
it is necessary to increase lengths of flow paths for the refrigerants that exchange
heat in the internal heat exchanger, and the internal heat exchanger becomes too large.
[0029] In contrast, in the present embodiment, the refrigerant to be suctioned into compressor
200 is cooled by external heat exchanger 400. While the compressor suction point is
deviated to the right to cross the isothermal line in Fig. 4, this deviation can be
eliminated. Thus, reduction of the suction density can be avoided. When the PH diagram
of the refrigerant circuit in the present embodiment is calculated under the same
conditions as those in Fig. 4 (an evaporation temperature of 17°C, a condensation
temperature of 40°C, an evaporator superheat of 5 deg, a supercool of 5 deg, and a
compressor efficiency of 1), the PH diagram as shown in Fig. 5 is obtained. It should
be noted that the calculation was made assuming that the temperature of the water
as an external cooling source was 22°C.
[0030] In the example shown in Fig. 5, the enthalpy at the high-pressure side refrigerant
outlet of internal heat exchanger 250 becomes smaller than that in the case of using
ordinary internal heat exchanger 550, and the evaporator enthalpy difference increases
to h(D3)-h(A3).
[0031] Concerning suction density ρs, in the case of using ordinary internal heat exchanger
550, it is represented by ρs = 15.4 kg/m
3 as described above, whereas in the case of using internal heat exchanger 250 and
external heat exchanger 400, it increases to ρs = 16.2 kg/m
3 because a suction temperature also decreases to 22°C.
[0032] As described above, in the configuration shown in Fig. 1, it is possible to decrease
a specific enthalpy at the inlet of the evaporator to increase enthalpy difference
Δhe in the evaporator and improve COP. More preferably, when the temperature of the
water is lower than the temperature of the low-pressure refrigerant obtained by temperature
sensor 261, heat exchange using the water is performed in external heat exchanger
400. In this manner, in addition to the effect of the increase in evaporator enthalpy
difference, the suction density of compressor 200 can be increased, and further, COP
can be improved, when compared with the case of using internal heat exchanger 550
that does not use an external cooling medium. Further, when the temperature of the
water is higher than the temperature of the high-pressure refrigerant at the inlet
of internal heat exchanger 250, it is more preferable to prevent the water from being
conveyed to internal heat exchanger 250.
[0033] Fig. 6 is a perspective view showing an external appearance of internal heat exchanger
250. Fig. 7 is a cross-sectional view of internal heat exchanger 250 in a cross section
F1 in Fig. 6. Internal heat exchanger 250 shown in Figs. 6 and 7 has a double-tube
structure including an inner tube 251 and an outer tube 252. Inner tube 251 serves
as a flow path R1 through which the low-pressure refrigerant returning to a suction
portion of compressor 200 flows. Outer tube 252 serves as a flow path R2 through which
the high-pressure refrigerant that has flowed out of the outlet of outdoor heat exchanger
210 flows. As indicated by arrows in Fig. 7, the refrigerant that flows through flow
path R1 and the refrigerant that flows through flow path R2 have a relation of counterflows.
[0034] Fig. 8 is a perspective view showing an external appearance of external heat exchanger
400. Fig. 9 is a cross-sectional view of external heat exchanger 400 in a cross section
F2 in Fig. 8. External heat exchanger 400 shown in Figs. 8 and 9 has a double-tube
structure including an inner tube 401 and an outer tube 402. Inner tube 401 serves
as a flow path R3 through which the low-pressure refrigerant returning to the suction
portion of compressor 200 flows. Flow path R3 is located between flow path R2 and
the suction portion of compressor 200. Outer tube 402 serves as a flow path R4 through
which water externally conveyed through flow path 410 flows. As indicated by arrows
in Fig. 9, the refrigerant that flows through flow path R3 and the refrigerant that
flows through flow path R4 have a relation of counterflows.
[0035] It should be noted that, although the water may flow through inner tube 401 and the
low-pressure refrigerant may flow through outer tube 402, flowing the water through
outer tube 402 is more advantageous in the following point.
[0036] For example, if a crack appears in the outer circumference of outer tube 402, it
is the water that may leak to the outside of external heat exchanger 400, which is
less problematic than the case where the refrigerant flows through outer tube 402.
In particular, when an inflammable refrigerant is used as the refrigerant, the inflammable
refrigerant can be prevented from being discharged to the outside. Further, when a
chlorofluorocarbon-based refrigerant is used, the refrigerant is less likely to leak
to the outside, which can suppress influence on global wanning.
[0037] In the present embodiment, external heat exchanger 400 includes flow path R4, the
cooling medium that flows through flow path R4 is water, and external heat exchanger
400 is of a double-tube type. It should be noted that the cooling medium may not be
water. Further, external heat exchanger 400 may not be of a double-tube type, but
may be a plate-type heat exchanger or the like. Further, a flow path through which
the cooling medium such as water flows may not be a closed space. For example, flow
path R3 of internal heat exchanger 250 may be a tube, and the tube may be immersed
in a groove-like water channel to cool refrigerant flowing through flow path R3. Moreover,
the pipe to the suction inlet of compressor 200 may be cooled by spraying water. Furthermore,
although internal heat exchanger 250 is installed to act during cooling, no problem
occurs when it is installed to act during heating.
[0038] Regarding internal heat exchanger 250 as well, internal heat exchanger 250 may be
a plate heat exchanger or the like, for example, instead of the double tube. It may
also be in the form where a low-pressure pipe and a high-pressure pipe contact each
other by means of solder or the like to allow heat to be exchanged.
[0039] Moreover, instead of using temperature sensor 260 that measures the temperature of
the refrigerant to be suctioned, the water temperature at the outlet may be obtained
to estimate the suction temperature from the amount of heat exchange by the water.
[0040] In Fig. 1, the flow of the refrigerant during heating is indicated by solid-line
arrows, and the flow of the refrigerant during cooling is indicated by broken-line
arrows. As in an ordinary air conditioner, controller 100 changes the frequency of
compressor 200 such that a room temperature reaches a target (setting) temperature.
Further, controller 100 controls flow rate adjusting device 420 during cooling, as
described below.
[0041] Fig. 10 is a flowchart for illustrating control of flow rate adjusting device 420
during cooling. First, in step S11, controller 100 obtains refrigerant temperature
T261 at the outlet of flow path R2 of internal heat exchanger 250 from temperature
sensor 261, and obtains temperature T411 of the water from temperature sensor 411.
In step S12, controller 100 determines whether or not temperature T261 obtained from
temperature sensor 261 is higher than temperature T411 obtained from temperature sensor
411.
[0042] When T261 > T411 is not satisfied (NO in S12), the temperature of the water is higher
and thus cannot be used to cool the refrigerant in external heat exchanger 400, and
therefore, in step S13, controller 100 controls flow rate adjusting device 420 to
be fully closed, to prevent the water from flowing to external heat exchanger 400.
On the other hand, when T261 > T411 is satisfied (YES in S12), in step S14, controller
100 controls flow rate adjusting device 420 to be fully opened.
[0043] Subsequently, in step S15, controller 100 determines whether a superheat of the suctioned
refrigerant (hereinafter referred to as a suction SH) is smaller than a determination
value α (> 0). The suction SH is calculated by subtracting the evaporation temperature
obtained by temperature sensor 262 from the suction temperature obtained by temperature
sensor 260. Here, determination value α is set to a value at which it is possible
to determine that the refrigerant suctioned into compressor 200 is sufficiently gasified,
for example, 5K.
[0044] When the suction SH ≥ α is satisfied (NO in S15), it is possible to determine that
the refrigerant suctioned into compressor 200 is sufficiently gasified, and thus controller
100 exits the flowchart in Fig. 10. On the other hand, when the suction SH < α is
satisfied (YES in S15), it is not possible to determine that the refrigerant suctioned
into compressor 200 is sufficiently gasified, that is, liquid refrigerant may be suctioned
into compressor 200. Therefore, in step S16, controller 100 closes flow rate adjusting
device 420 by a certain opening degree. By decreasing the flow rate of the water in
this manner to reduce the amount of heat exchange, the value of the suction SH can
be increased. Thereafter, the processing in step S15 is performed again.
[0045] It should be noted that, although the flow rate of the water to internal heat exchanger
250 is adjusted using flow rate adjusting device 420 in the present embodiment, the
flow rate of the water may be controlled using a pump.
[0046] Next, control of expansion valve 230 during cooling will be described. Fig. 11 is
a flowchart for illustrating control of expansion valve 230 during cooling.
[0047] First, in step S21, controller 100 determines whether or not a superheat of the refrigerant
at the outlet portion of the evaporator (hereinafter referred to as an evaporator
outlet SH) is smaller than a determination value β (≥ 0). The evaporator outlet SH
is calculated by subtracting evaporation temperature T262 obtained by temperature
sensor 262 from evaporator outlet temperature T263 obtained by temperature sensor
263. Here, determination value β is set to a value smaller than determination value
α. For example, when determination value α is 5K, determination value β is set to
2K. The reason for setting determination value β to be smaller than determination
value α is that, since the evaporator has a good heat exchange efficiency when it
is used with the refrigerant being in a gas-liquid two phase state, it is desired
to control the state of the refrigerant in the evaporator to minimize gas refrigerant.
[0048] When the evaporator outlet SH ≥ β is satisfied (NO in S21), it is possible to determine
that the refrigerant at the outlet of the evaporator is gasified. Therefore, in step
S22, controller 100 opens the opening degree of expansion valve 230 by a certain value.
Thereby, the value of the evaporator outlet SH can be decreased. Thereafter, the processing
in step S21 is performed again.
[0049] On the other hand, when the evaporator outlet SH < β is satisfied (YES in S21), it
is determined that the refrigerant at the outlet of the evaporator is not gasified
(i.e., the evaporator is used efficiently). Therefore, in step S23, controller 100
determines whether flow rate adjusting device 420 is fully closed.
[0050] When flow rate adjusting device 420 is not fully closed (NO in S23), the suction
SH is controlled to an appropriate value by flow rate adjusting device 420 as shown
in steps S15 and S16 in Fig. 10, and thus controller 100 temporarily exits the processing
of the flowchart in Fig. 11. On the other hand, when flow rate adjusting device 420
is fully closed (YES in S23), heat exchange with the externally supplied water is
not performed in external heat exchanger 400, and thereby the evaporator outlet SH
≈ the suction SH is satisfied. Accordingly, the suction SH ≈ β (< α) is satisfied,
which leads to a state where the refrigerant suctioned into compressor 200 is not
heated appropriately. Therefore, in step S24, controller 100 closes the opening degree
of expansion valve 230 by a certain value to increase the value of the suction SH,
and thereafter performs determination processing in step S25.
[0051] In step S25, controller 100 determines whether or not the suction SH is smaller than
determination value α (> 0). When the suction SH ≥ α is satisfied (NO in S25), it
is possible to determine that the refrigerant suctioned into compressor 200 is sufficiently
gasified, and thus controller 100 temporarily exits the processing of the flowchart
in Fig. 11. On the other hand, when the suction SH < α is satisfied (YES in S25),
it is not possible to determine that the refrigerant suctioned into compressor 200
is sufficiently gasified, that is, liquid refrigerant may be suctioned into compressor
200. Therefore, in step S26, controller 100 closes the opening degree of expansion
valve 230 by a certain value. By controlling the opening degree of expansion valve
230 in this manner, the value of the suction SH can be increased. Thereafter, the
processing in step S25 is performed again.
[0052] The flows of control of flow rate adjusting device 420 and expansion valve 230 during
cooling have been described above.
[0053] During heating, flow rate adjusting device 420 may be fully closed and controlled
as in an ordinary air conditioner, or flow rate adjusting device 420 may be controlled
as described below.
[0054] Fig. 12 is a view showing a configuration of an air conditioner 1001 having sensors
used during heating added thereto. Specifically, air conditioner 1001 further includes
temperature sensors 264, 265 in addition to the configuration of air conditioner 1000
shown in Fig. 1. Fig. 13 is a flowchart for illustrating control of flow rate adjusting
device 420 during heating.
[0055] First, in step S31, controller 100 obtains outlet refrigerant temperature T261 of
flow path R2 of internal heat exchanger 250 from temperature sensor 261, and obtains
temperature T411 of the water from temperature sensor 411. In step S32, controller
100 determines whether or not temperature T261 obtained from temperature sensor 261
is higher than temperature T411 obtained from temperature sensor 411.
[0056] When T261 > T411 is not satisfied (NO in S32), the temperature of the water is higher
and thus cannot be used to cool the refrigerant in external heat exchanger 400. Therefore,
in step S33, controller 100 controls flow rate adjusting device 420 to be fully closed,
to prevent the water from flowing to external heat exchanger 400. On the other hand,
when T261 > T411 is satisfied (YES in S32), in step S34, controller 100 controls flow
rate adjusting device 420 to be fully opened.
[0057] Subsequently, in step S35, controller 100 determines whether the superheat of the
suctioned refrigerant (suction SH) is smaller than determination value α (> 0). The
suction SH is calculated by subtracting an evaporation temperature T264 obtained by
temperature sensor 264 from suction temperature T260 obtained by temperature sensor
260. Here, determination value α is set to a value at which it is possible to determine
that the refrigerant suctioned into compressor 200 is sufficiently gasified, for example,
5K.
[0058] When the suction SH ≥ α is satisfied (NO in S35), it is possible to determine that
the refrigerant suctioned into compressor 200 is sufficiently gasified, and thus controller
100 temporarily exits the flowchart in Fig. 13. On the other hand, when the suction
SH < α is satisfied (YES in S35), it is not possible to determine that the refrigerant
suctioned into compressor 200 is sufficiently gasified, that is, liquid refrigerant
may be suctioned into compressor 200. Therefore, in step S36, controller 100 closes
flow rate adjusting device 420 by a certain opening degree. By decreasing the flow
rate of the water in this manner to reduce the amount of heat exchange, the value
of the suction SH can be increased. Thereafter, the processing in step S35 is performed
again.
[0059] It should be noted that, also during heating, the flow rate of the water may be controlled
using a pump instead of flow rate adjusting device 420.
[0060] For the control of expansion valve 230 during heating, it is only necessary to perform
the same processing as that performed during cooling shown in Fig. 11. However, the
evaporator outlet SH is calculated by subtracting the evaporation temperature obtained
by temperature sensor 264 from the value of temperature sensor 265.
[0061] As has been described above, according to the air conditioner in the first embodiment,
the coefficient of performance, COP, of the air conditioner that uses R290 as the
refrigerant and uses an internal heat exchanger can be improved. Further, while using
R290 as the refrigerant is most effective, even when R32 or R410 is used as the refrigerant,
the effect caused by an internal heat exchanger can be obtained and COP can be improved,
because the suction density changes from that in the case shown in Fig. 2.
[0062] Further, also when internal heat exchanger 250 is used during heating, the evaporator
enthalpy difference increases as is the case during cooling, and improved efficiency
can be expected.
Second Embodiment
[0063] In the configuration in Fig. 1 described in the first embodiment, an air heat exchanger
is employed as outdoor heat exchanger 210, considering the case that the cooling source
for the refrigeration cycle is not in a situation where it can always be used. For
example, when tap water is employed, there may be a case where it cannot be used due
to suspension of water supply or the like. Therefore, in order to cause the refrigeration
cycle to always function, it is appropriate to employ outdoor air, which can always
be utilized, as a target of heat exchange of outdoor heat exchanger 210. Further,
when a water-refrigerant heat exchanger is employed as outdoor heat exchanger 210,
it is also necessary to draw a water pipe. Accordingly, the configuration as in Fig.
1 is employed to achieve a simple configuration.
[0064] However, when the cooling source can be stably secured, it may be better to downsize
the outdoor heat exchanger. Fig. 14 is a view showing a configuration of an air conditioner
1002 according to a second embodiment.
[0065] Only a difference from the configuration shown in Fig. 1 will be described. In air
conditioner 1002 shown in Fig. 14, outdoor heat exchanger 210 in Fig. 1 is changed
to a heat exchanger 270. Unlike outdoor heat exchanger 210, heat exchanger 270 is
configured to exchange heat with the water as the external cooling source. The water
may be circulated and cooled at a cooling tower or the like, and then is supplied
again through a water supply pipe, for example. When hot water warmed by heat exchanger
270 is used, tap water or the like may newly be supplied. Heat exchanger 270 is a
plate heat exchanger, for example. Further, the water used by heat exchanger 270 and
internal heat exchanger 250 is supplied through the same water supply pipe.
[0066] It should be noted that, since the control of flow rate adjusting device 420 and
expansion valve 230 is the same as that in the first embodiment, the description thereof
will not be repeated.
[0067] In air conditioner 1002 in the second embodiment, the same effect as that in the
first embodiment is obtained. In addition, since the amount of heat exchange by the
water increases when compared with the configuration shown in the first embodiment,
the returned water has a higher temperature and can be used for hot-water supply or
the like. Further, since plate heat exchanger 270 is employed as the outdoor heat
exchanger and thereby heat exchange performance is improved, the heat exchanger can
be downsized when compared with the first embodiment.
(Supplement)
[0068] Although the refrigerant circuit includes a four-way valve in the first and second
embodiments described above, external heat exchanger 400 may be used for an air conditioner
for cooling only that does not include a four-way valve.
[0069] Further, although the first and second embodiments have provided the description
based on an example where the R290 refrigerant is used as refrigerant circulating
through the refrigerant circuit, another refrigerant such as R32 or R410 may be used.
For example, in the case of using R32 refrigerant, since influence of the increase
in enthalpy difference in the evaporator and influence of the decrease in the density
of the suctioned refrigerant offset each other in internal heat exchanger 550 shown
in the study example in Fig. 2, there is no merit in introducing the R32 refrigerant.
In contrast, since external heat exchanger 400 shown in Fig. 1 can suppress the decrease
in the density of the suctioned refrigerant using the external cooling source, the
performance of the air conditioner can be improved even in the case of using the R32
refrigerant.
(Conclusion)
[0070] The present embodiment will be summarized below with reference to the drawings again.
It should be noted that items within parentheses describe units applicable during
cooling.
[0071] Air conditioner 1000 shown in Fig. 1 includes: refrigerant circuit 500 including
at least compressor 200, a condenser (outdoor heat exchanger 210), expansion valve
230, and an evaporator (indoor heat exchanger 110), the refrigerant circuit being
configured to circulate refrigerant; a first heat exchanger (internal heat exchanger
250) having first flow path R1 in which the refrigerant that has passed through the
condenser (outdoor heat exchanger 210) flows, and second flow path R2 in which the
refrigerant that is to be suctioned into compressor 200 flows, and being configured
to exchange heat between the refrigerant flowing through first flow path R1 and the
refrigerant flowing through second flow path R2; a second heat exchanger (external
heat exchanger 400) having third flow path R3 in which the refrigerant directed from
an outlet of second flow path R2 toward compressor 200 flows, and fourth flow path
R4 in which a heat medium flows, and being configured to exchange heat between the
refrigerant flowing through third flow path R3 and the heat medium flowing through
fourth flow path R4; flow rate adjusting device 420 configured to adjust an amount
of heat medium supplied to the second heat exchanger (external heat exchanger 400);
temperature sensor 411 configured to detect a temperature of the heat medium; and
controller 100 configured to control flow rate adjusting device 420 in accordance
with an output of temperature sensor 411.
[0072] Preferably, as shown in Fig. 10, controller 100 is configured to control flow rate
adjusting device 420 such that the heat medium is supplied to the second heat exchanger
(external heat exchanger 400) when temperature T411 of the heat medium is lower than
temperature T261 of the refrigerant flowing into the second heat exchanger (external
heat exchanger 400). Controller 100 is configured to control flow rate adjusting device
420 such that the heat medium is not supplied to the second heat exchanger (external
heat exchanger 400) when temperature T411 of the heat medium is higher than temperature
T261 of the refrigerant flowing into the second heat exchanger (external heat exchanger
400).
[0073] Preferably, as shown in Figs. 8 and 9, the second heat exchanger (external heat exchanger
400) is a double-tube heat exchanger in which inner tube 401 and outer tube 402 are
arranged. Inner tube 401 is third flow path R3 in which refrigerant flows, and outer
tube 402 is fourth flow path R4 in which the heat medium flows.
[0074] Preferably, as shown in Fig. 14, the condenser (outdoor heat exchanger 270) is configured
to exchange heat between the heat medium and the refrigerant.
[0075] Preferably, the refrigerant is propane.
[0076] It should be understood that the embodiments disclosed herein are illustrative and
non-restrictive in every respect. The scope of the present disclosure is defined by
the scope of the claims, rather than the description of the embodiments described
above, and is intended to include any modifications within the scope and meaning equivalent
to the scope of the claims.
REFERENCE SIGNS LIST
[0077] 100: controller; 101: CPU; 102: memory; 110, 210, 250, 270, 325, 400, 550: heat exchanger;
120: indoor blower; 200: compressor; 220: outdoor blower; 230: expansion valve; 240:
four-way valve; 251, 401: inner tube; 252, 402: outer tube; 260 to 265, 411: temperature
sensor; 410, R1, R2, R3, R4: flow path; 420: flow rate adjusting device; 500: refrigerant
circuit; 1000, 1001, 1002, 2000: air conditioner; P1, P2, P3, P4: port.