TECHNICAL FIELD
[0001] The present disclosure relates to a refrigeration device.
BACKGROUND ART
[0002] A refrigeration device that circulates a refrigerant therethrough to perform a refrigeration
cycle has been known in the art. Such a refrigeration device is widely used to cool
the interior of a refrigerator or a freezer and to perform other operations. For example,
Patent Document 1 discloses a refrigeration device including an outdoor unit and a
cooling unit (a utilization-side unit). The outdoor unit includes a compressor and
an outdoor heat exchanger. The cooling unit includes a utilization-side heat exchanger.
[0003] In the refrigeration device of Patent Document 1, the outdoor unit and the cooling
unit are connected together to form a refrigerant circuit. In a cooling mode of the
cooling apparatus, the cooling unit enters into either a thermo-on state (a state
where inside air is cooled with the utilization-side heat exchanger) or a thermo-off
state (a state where inside air is not cooled with the utilization-side heat exchanger),
depending on the temperature of the inside air (internal temperature) detected by
an internal temperature sensor. In the cooling apparatus, the cooling unit that has
entered into the thermo-off state allows the compressor to stop, and the cooling unit
that has entered into the thermo-on state allows the compressor to start.
CITATION LIST
PATENT DOCUMENTS
[0004] [Patent Document 1] Japanese Unexamined Patent Publication No.
2014-70830
SUMMARY OF THE INVENTION
TECHNICAL PROBLEM
[0005] In the refrigeration device of Patent Document 1, the operation frequency of the
compressor may be controlled so that the temperature of a refrigerant sucked into
the compressor (hereinafter referred to as the "suction temperature") is equal to
a predetermined target evaporation temperature. In this case, the target evaporation
temperature is set to be lower than a set internal temperature, with consideration
given to pressure loss in a pipe between the liquid end of the utilization-side heat
exchanger and a suction port of the compressor (specifically, the pipe length, the
pipe diameter, the height difference, and other elements).
[0006] Upon the start of the cooling mode, the utilization-side unit enters into a cooling
state (a state where the utilization-side heat exchanger functions as an evaporator
to cool inside air). Thus, the internal temperature gradually decreases. If a predetermined
period of time (a period of time for reducing the internal temperature) has elapsed
since the start of the cooling mode, the internal temperature becomes close to the
set internal temperature. As a result, the internal cooling load decreases. That is
to say, after the predetermined period of time has elapsed since the start of the
cooling mode, the internal temperature is stable near the set internal temperature.
Thus, the internal cooling load is considered to be relatively low. The period of
time during which the internal temperature is stable near the set internal temperature
and the internal cooling load is relatively low as above is hereinafter referred to
as the "low internal load period."
[0007] The cooling capability required of the utilization-side unit is relatively low for
the low internal load period in the cooling mode. Thus, the operation frequency of
the compressor is preferably reduced to increase the coefficient of performance (COP)
of the refrigeration device. However, the lower the target evaporation temperature
is, the less likely the operation frequency of the compressor is to decrease for the
low internal load period in the cooling mode. This makes it difficult to increase
the coefficient of performance of the refrigeration device.
[0008] It is therefore an object of the present disclosure to provide a refrigeration device
that can facilitate reducing the operation frequency of a compressor for a low internal
load period in a cooling mode to increase the coefficient of performance.
SOLUTION TO THE PROBLEM
[0009] A refrigeration device according to a first aspect of the disclosure includes: a
heat-source-side unit (11) including a compressor (21a) and a heat-source-side heat
exchanger (23); and a utilization-side unit (12) including a utilization-side heat
exchanger (51) and provided in an internal space. The heat-source-side unit (11) and
the utilization-side unit (12) are connected together to form a refrigerant circuit
(15) through which a refrigerant circulates. During a cooling mode in which the heat-source-side
heat exchanger (23) functions as a condenser, if an internal temperature (Tr) is above
a set internal temperature range including a set internal temperature (Tset), the
utilization-side unit (12) is placed in a cooling state where a refrigerant is passed
through the utilization-side heat exchanger (51) to allow the utilization-side heat
exchanger (51) to function as an evaporator. If the internal temperature (Tr) is below
the set internal temperature range, the utilization-side unit (12) is placed in a
suspended state where flow of a refrigerant through the utilization-side heat exchanger
(51) is interrupted so that cooling of the internal space is suspended. The refrigeration
device further includes: a compressor control section (83) configured to control an
operation frequency (FQ) of the compressor (21a) so that in the cooling mode, a temperature
of a refrigerant sucked into the compressor (21a) is equal to a target evaporation
temperature (Te); and a target temperature setting section (84) configured to set
the target evaporation temperature (Te) to be equal to the reference temperature (Teref)
lower than the set internal temperature (Tset) during a pull-down period (PD) for
reducing the internal temperature (Tr), which has elapsed since the start of the cooling
mode, the target temperature setting section (84) being configured to correct the
target evaporation temperature (Te) so that if, after the pull-down period (PD) has
elapsed, a frequency index value (FQi) dependent on the operation frequency (FQ) of
the compressor (21a) during a cooling duration during which the utilization-side unit
(12) is placed in the cooling state is above a predetermined reference value (FQref),
the target evaporation temperature (Te) is higher than the reference temperature (Teref).
[0010] According to the first aspect, the target evaporation temperature (Te) is set to
be equal to the reference temperature (Teref) between the time when the cooling mode
starts and the time when the pull-down period (PD) has elapsed since the start of
the cooling mode. This allows the utilization-side unit (12) to have sufficiently
high cooling capability during the pull-down period (PD). Thus, inside air can be
appropriately cooled during the pull-down period (PD).
[0011] In the first aspect, if the pull-down period (PD) has elapsed since the start of
the cooling mode, the internal temperature (Tr) becomes close to the set internal
temperature (Tset). Thus, the internal cooling load decreases. That is to say, after
the pull-down period (PD) has elapsed since the start of the cooling mode, the internal
temperature (Tr) is stable near the set internal temperature (Tset). Thus, the internal
cooling load is considered to be relatively low. The period during which the internal
temperature (Tr) is stable near the set internal temperature (Tset) and the internal
cooling load is relatively low is hereinafter referred to as the "low internal load
period."
[0012] In the first aspect, if, after the pull-down period (PD) has elapsed, the frequency
index value (FQi) during the cooling duration (the period of time during which the
utilization-side unit (12) is in the cooling state) is above the reference value (FQref),
the target evaporation temperature (Te) is corrected to be higher than the reference
temperature (Teref). Thus, if the compressor (21a) is driven at relatively high operation
frequencies during the low internal load period after the pull-down period (PD) has
elapsed, increasing the target evaporation temperature (Te) can facilitate reducing
the operation frequency (FQ) of the compressor (21a).
[0013] The second aspect of the disclosure is an embodiment of the first aspect. In the
second aspect, the frequency index value (FQi) corresponds to an average (FQave) of
operation frequencies (FQ) of the compressor (21a) during the cooling duration.
[0014] According to the second aspect, if, after the pull-down period (PD) has elapsed,
the average (FQave) of the operation frequencies (FQ) of the compressor (21a) during
the cooling duration is above the predetermined reference value (FQref), the target
evaporation temperature (Te) is corrected to be higher than the reference temperature
(Teref). Thus, if the compressor (21a) is driven at relatively high operation frequencies
during the low internal load period after the pull-down period (PD) has elapsed, increasing
the target evaporation temperature (Te) can facilitate reducing the operation frequency
(FQ) of the compressor (21a).
[0015] A third aspect of the disclosure is an embodiment of the first aspect. In the third
aspect, the frequency index value (FQi) corresponds to an operation frequency (FQ)
of the compressor (21a) obtained when the utilization-side unit (12) shifts form the
cooling state to the suspended state.
[0016] According to the third aspect, if, after the pull-down period (PD) has elapsed, the
operation frequency (FQ) of the compressor (21a) at a time when the utilization-side
unit (12) shifts from the cooling state to the suspended state is above the predetermined
reference value (FQref), the target evaporation temperature (Te) is corrected to be
higher than the reference temperature (Teref). Thus, if the compressor (21a) is driven
at relatively high operation frequencies during the low internal load period after
the pull-down period (PD) has elapsed, increasing the target evaporation temperature
(Te) can facilitate reducing the operation frequency (FQ) of the compressor (21a).
[0017] A fourth aspect of the disclosure is an embodiment of any one of the first through
third aspects. In the fourth aspect, the target temperature setting section (84) corrects
the target evaporation temperature (Te) to prevent the target evaporation temperature
(Te) from exceeding a predetermined upper-limit temperature (Temax).
[0018] According to the fourth aspect, correcting the target evaporation temperature (Te)
to prevent the target evaporation temperature (Te) from exceeding the upper-limit
temperature (Temax) can prevent the target evaporation temperature (Te) from becoming
too high.
[0019] A fifth aspect of the disclosure is an embodiment of any one of the first through
fourth aspects. In the fifth aspect, the target temperature setting section (84) corrects
the target evaporation temperature (Te) so that if the target evaporation temperature
(Te) is higher than the reference temperature (Teref), and the cooling duration is
longer than a predetermined duration threshold (Tth), the target evaporation temperature
(Te) decreases to be closer to, or equal to, the reference temperature (Teref).
[0020] During the low internal load period after a lapse of the pull-down period (PD), the
opening/closing of a door and other factors may cause outside heat to enter the internal
space. This may increase the internal cooling load. An increase in the internal cooling
load as above triggers an increase in the cooling duration (the period of time during
which the utilization-side unit (12) is in the cooling state).
[0021] According to the fifth aspect, if the cooling duration (the period of time during
which the utilization-side unit (12) is in the cooling state) is longer than the duration
threshold (Tth), the target evaporation temperature (Te) is reduced. This can increase
the cooling capability of the utilization-side unit (12) when the internal cooling
load is high during the low internal load period after a lapse of the pull-down period
(PD).
[0022] A sixth aspect of the disclosure is an embodiment of any one of the first through
fifth aspects. In the sixth aspect, the target temperature setting section (84) sets
the target evaporation temperature (Te) to be equal to the reference temperature (Teref)
after an end of the cooling mode and before start of a defrosting mode in which the
utilization-side heat exchanger (51) functions as a condenser and the heat-source-side
heat exchanger (23) functions as an evaporator.
[0023] The sixth aspect allows the utilization-side unit (12) to have sufficiently high
heat dissipation capability (specifically, allows the utilization-side heat exchanger
(51) to have sufficiently high heat dissipation capability) in the defrosting mode.
[0024] A seventh aspect of the disclosure is an embodiment of any one of the first through
sixth aspects. In the seventh aspect, the pull-down period (PD) corresponds to a shorter
one of a period of time from a time when the cooling mode starts to a time when the
utilization-side unit (12) shifts from the cooling state to the suspended state or
a period of time from the time when the cooling mode starts to a time when a predetermined
period of time (T1) has elapsed since the start of the cooling mode.
[0025] According to the seventh aspect, if the utilization-side unit (12) shifts from the
cooling state to the suspended state after the start of the cooling mode, the internal
temperature (Tr) can be considered to be close to the set internal temperature (Tset).
In addition, also if a sufficient period of time (i.e., the predetermined period of
time (T1)) has elapsed since the start of the cooling mode, the internal temperature
(Tr) can be considered to be close to the set internal temperature (Tset).
ADVANTAGES OF THE INVENTION
[0026] According to the first through third aspects of the disclosure, if a compressor (21a)
is driven at relatively high operation frequencies during a low internal load period
after a pull-down period (PD) has elapsed, increasing a target evaporation temperature
(Te) can facilitate reducing the operation frequency (FQ) of the compressor (21a).
This can increase the coefficient of performance (COP) of a refrigeration device during
the low internal load period in the cooling mode.
[0027] The fourth aspect of the disclosure can prevent the target evaporation temperature
(Te) from becoming too high. This can prevent an increase in the target evaporation
temperature (Te) from causing lack of the cooling capability of the utilization-side
unit (12).
[0028] According to the fifth aspect of the disclosure, the cooling capability of the utilization-side
unit (12) can be increased when the internal cooling load is high during the low internal
load period after a lapse of the pull-down period (PD). This allows the internal temperature
(Tr) to be rapidly closer to the set internal temperature (Tset).
[0029] The sixth aspect of the disclosure allows the utilization-side unit (12) to have
sufficiently high heat dissipation capability in the defrosting mode. Thus, the utilization-side
heat exchanger (51) can be appropriately defrosted in the defrosting mode.
[0030] According to the seventh aspect of the disclosure, if a shorter one of the period
of time from a time when the cooling mode starts to a time when the utilization-side
unit (12) shifts from the cooling state to the suspended state and a period of time
from the time when the cooling mode starts to a time when a predetermined period of
time (T1) has elapsed since the start of the cooling mode is defined as the pull-down
period (PD), the internal temperature (Tr) can be reduced to a temperature close to
the set internal temperature (Tset) during the pull-down period (DP).
BRIEF DESCRIPTION OF THE DRAWINGS
[0031]
[FIG. 1] FIG. 1 is a piping system diagram showing an exemplary configuration for
a refrigeration device according to an embodiment.
[FIG. 2] FIG. 2 is a flowchart showing operations of the refrigeration device.
[FIG. 3] FIG. 3 is a piping system diagram showing the flow of a refrigerant in a
cooling mode.
[FIG. 4] FIG. 4 is a piping system diagram showing the flow of a refrigerant in a
defrosting mode.
[FIG. 5] FIG. 5 is a flowchart for explaining operations of a target temperature setting
section in the cooling mode.
[FIG. 6] FIG. 6 is a graph for explaining a frequency index value.
[FIG. 7] FIG. 7 is a graph for explaining how the internal temperature changes.
[FIG. 8] FIG. 8 is a graph for explaining how the operation frequency of a compressor
of a refrigeration device according to a comparative example changes.
[FIG. 9] FIG. 9 is a graph for explaining how the operation frequency of a compressor
of the refrigeration device according to the embodiment changes.
DETAILED DESCRIPTION
[0032] Embodiments will now be described in detail with reference to the drawings. Note
that like reference characters denote the same or equivalent components in the drawings,
and the description thereof will not be repeated.
(Refrigeration Device)
[0033] FIG. 1 shows an exemplary configuration for a refrigeration device (10) according
to an embodiment. The refrigeration device (10) includes a heat-source-side unit (11)
provided outside a refrigerator, a freezer, or any other similar device, an utilization-side
unit (12) provided inside the device, and a controller (80). The heat-source-side
unit (11) includes a heat-source-side circuit (16) and a heat-source-side fan (17).
The utilization-side unit (12) includes a utilization-side circuit (18) and a utilization-side
fan (19). In this refrigeration device (10), the heat-source-side circuit (16) of
the heat-source-side unit (11) and the utilization-side circuit (18) of the utilization-side
units (12) are connected together through a liquid interconnecting pipe (13) and a
gas interconnecting pipe (14) to form a refrigerant circuit (15) that circulates a
refrigerant therethrough to perform a vapor compression refrigeration cycle. Specifically,
a liquid stop valve (VI) and a gas stop valve (V2) are provided at the liquid and
gas ends of the heat-source-side circuit (16), respectively, and are connected to
one end of the liquid interconnecting pipe (13) and one end of the gas interconnecting
pipe (14), respectively. The liquid interconnecting pipe (13) and the gas interconnecting
pipe (14) are connected to the liquid and gas ends of the utilization-side circuit
(18), respectively.
<Heat-Source-Side Circuit>
[0034] The heat-source-side circuit (16) includes first and second compressors (21a, 21b),
a four-way valve (22), a heat-source-side heat exchanger (23), a supercooling heat
exchanger (24), a supercooling expansion valve (31), an intermediate expansion valve
(32), an intermediate open/close valve (33), an intermediate check valve (34), a receiver
(35), a heat-source-side expansion valve (36), first, second, and third check valves
(CV1, CV2, CV3), first and second oil separators (OSa, OSb), first and second discharge
check valves (CVa, CVb), first and second capillary tubes (CTa, CTb), and an oil return
check valve (CVc).
[0035] The heat-source-side circuit (16) further includes a discharge refrigerant pipe (41),
a suction refrigerant pipe (42), a heat-source-side liquid refrigerant pipe (43),
an injection pipe (44), first and second connection pipes (45, 46), and an oil return
pipe (47).
<<Compressors>>
[0036] The first compressor (21a) is configured to compress, and discharge, a refrigerant
sucked thereinto. The first compressor (21a) has a suction port, an intermediate port,
and a discharge port. The suction port communicates with a compression chamber (i.e.,
a compression chamber in a low pressure phase) during a suction stroke of the first
compressor (21a). The intermediate port communicates with a compression chamber (i.e.,
a compression chamber in an intermediate pressure phase) in the middle of a compression
stroke of the first compressor (21a). The discharge port communicates with a compression
chamber (i.e., a compression chamber in a high pressure phase) during a discharge
stroke of the first compressor (21a). The first compressor (21a) is configured as,
for example, a scroll compressor including a compression chamber defined between a
fixed scroll and an orbiting scroll, which mesh with each other. The second compressor
(21b) has a configuration similar to that for the first compressor (21a).
[0037] Note that the first compressor (21a) has a variable operation frequency (capacity).
Specifically, changing the output frequency of an inverter (not shown) triggers a
change in the rotational speed of an electric motor provided inside the first compressor
(21a). This causes the operation frequency of the first compressor (21a) to vary.
On the other hand, the second compressor (21b) has a fixed operation frequency (capacity).
Specifically, the second compressor (21b) includes therein an electric motor rotating
at a constant rotational speed, and has a constant operation frequency.
<<Four-Way Valve>>
[0038] The four-way valve (22) is switchable between a first state (indicated by the solid
curves shown in FIG. 1) and a second state (indicated by the dashed curves shown in
FIG. 1). In the first state, a first port communicates with a third port, and a second
port communicates with a fourth port. In the second state, the first port communicates
with the fourth port, and the second port communicates with the third port.
[0039] The first port of the four-way valve (22) is connected to the discharge ports of
the first and second compressors (21a, 21b) through the discharge refrigerant pipe
(41). The second port of the four-way valve (22) is connected to the suction ports
of the first and second compressors (21a, 21b) through the suction refrigerant pipe
(42). The third port of the four-way valve (22) is connected to the gas end of the
heat-source-side heat exchanger (23). The fourth port of the four-way valve (22) is
connected to the gas stop valve (V2).
<<Discharge Refrigerant Pipe>>
[0040] The discharge refrigerant pipe (41) includes first and second discharge pipes (41a,
41b) one end of each of which is connected to the discharge port of an associated
one of the first and second compressors (21a, 21b), and a main discharge pipe (41c)
connecting the other end of each of the first and second discharge pipes (41a, 41b)
to the first port of the four-way valve (22).
<<Suction Refrigerant Pipe>>
[0041] The suction refrigerant pipe (42) includes first and second suction pipe (42a, 42b)
one end of each of which is connected to the suction port of an associated one of
the first and second compressors (21a, 21b), and a main suction pipe (42c) connecting
the other end of each of the first and second suction pipes (42a, 42b) to the second
port of the four-way valve (22).
<<Heat-Source-Side Heat Exchanger>>
[0042] The heat-source-side heat exchanger (23) has its liquid end connected to one end
of the heat-source-side liquid refrigerant pipe (43), and has its gas end connected
to the third port of the four-way valve (22). The heat-source-side fan (17) is disposed
near the heat-source-side heat exchanger (23). The heat-source-side heat exchanger
(23) is configured to exchange heat between a refrigerant and heat-source-side air
(i.e., outside air) transferred by the heat-source-side fan (17). The heat-source-side
heat exchanger (23) is configured as, for example, a cross-fin, fin-and-tube heat
exchanger.
<<Heat-Source-Side Liquid Refrigerant Pipe>>
[0043] The heat-source-side liquid refrigerant pipe (43) has two ends respectively connected
to the heat-source-side heat exchanger (23) and the liquid stop valve (VI). In this
example, the heat-source-side liquid refrigerant pipe (43) includes a first heat-source-side
liquid pipe (43a) connecting the liquid end of the heat-source-side heat exchanger
(23) to the receiver (35), a second heat-source-side liquid pipe (43b) connecting
the receiver (35) to the supercooling heat exchanger (24), and a third heat-source-side
liquid pipe (43c) connecting the supercooling heat exchanger (24) to the liquid stop
valve (VI).
<<Injection Pipe>>
[0044] The injection pipe (44) connects a first intermediate portion (Q1) of the heat-source-side
liquid refrigerant pipe (43) to the intermediate ports of the first and second compressors
(21a, 21b). In this example, the injection pipe (44) includes a first main injection
pipe (44m) connecting the first intermediate portion (Q1) of the heat-source-side
liquid refrigerant pipe (43) to the supercooling heat exchanger (24), a second main
injection pipe (44n) one end of which is connected to the supercooling heat exchanger
(24), and first and second injection branch pipes (44a, 44b) each connecting the other
end of the second main injection pipe (44n) to the intermediate port of an associated
one of the first and second compressors (21a, 21b).
<<Subcooling Heat Exchanger>>
[0045] The supercooling heat exchanger (24) is connected to the heat-source-side liquid
refrigerant pipe (43) and the injection pipe (44), and is configured to exchange heat
between a refrigerant flowing through the heat-source-side liquid refrigerant pipe
(43) and a refrigerant flowing through the injection pipe (44). In this example, the
supercooling heat exchanger (24) has first channels (24a) connected between the second
heat-source-side liquid pipe (43b) and the third heat-source-side liquid pipe (43c),
and second channels (24b) connected between the first main injection pipe (44m) and
the second main injection pipe (44n), and is configured to exchange heat between a
refrigerant flowing through the first channels (24a) and a refrigerant flowing through
the second channels (24b). The supercooling heat exchanger (24) is configured as,
for example, a plate heat exchanger.
<<Subcooling Expansion Valve>>
[0046] The supercooling expansion valve (31) is provided on a portion of the injection pipe
(44) between the first intermediate portion (Q1) of the heat-source-side liquid refrigerant
pipe (43) and the supercooling heat exchanger (24) (in this example, on the first
main injection pipe (44m)). The supercooling expansion valve (31) has an adjustable
degree of opening. The supercooling expansion valve (31) is configured as, for example,
an electronic expansion valve (motor-operated valve).
<<Intermediate Expansion Valve>>
[0047] The intermediate expansion valve (32) is provided on a portion of the injection pipe
(44) between the supercooling heat exchanger (24) and the intermediate port of the
first compressor (21a) (in this example, on the first injection branch pipe (44a)).
The intermediate expansion valve (32) also has an adjustable degree of opening. The
intermediate expansion valve (32) is configured as, for example, an electronic expansion
valve (a motor-operated valve).
<<Intermediate Open/Close Valve and Intermediate Check Valve>>
[0048] The intermediate open/close valve (33) and the intermediate check valve (34) are
provided on a portion of the injection pipe (44) between the supercooling heat exchanger
(24) and the intermediate port of the second compressor (21b) (in this example, on
the second injection branch pipe (44b)). The intermediate open/close valve (33) and
the intermediate check valve (34) are arranged on the second injection branch pipe
(44b) in this order from the inlet toward the outlet of the second injection branch
pipe (44b).
[0049] The intermediate open/close valve (33) is switchable between an open state and a
closed state. The intermediate open/close valve (33) is configured as, for example,
a solenoid valve. The intermediate check valve (34) allows a refrigerant to flow from
the inlet toward the outlet of the second injection branch pipe (44b), but disallows
a refrigerant to flow in the reverse direction.
<<Receiver>>
[0050] The receiver (35) is connected to a portion of the heat-source-side liquid refrigerant
pipe (43) between the heat-source-side heat exchanger (23) and the supercooling heat
exchanger (24), and is capable of temporarily storing a refrigerant condensed in the
condenser (specifically, the heat-source-side heat exchanger (23) or a utilization-side
heat exchanger (51), which will be described below). In this example, the receiver
(35) has its inlet and outlet respectively connected to the first and second heat-source-side
liquid pipes (43a, 43b).
<<First Connection Pipe>>
[0051] The first connection pipe (45) connects second and third intermediate portions (Q2,
Q3) of the heat-source-side liquid refrigerant pipe (43) together. The second intermediate
portion (Q2) is a portion of the heat-source-side liquid refrigerant pipe (43) between
the first intermediate portion (Q1) and the liquid stop valve (VI), and the third
intermediate portion (Q3) is a portion of the heat-source-side liquid refrigerant
pipe (43) between the liquid end of the heat-source-side heat exchanger (23) and the
receiver (35).
<<Second Connection Pipe>>
[0052] The second connection pipe (46) connects fourth and fifth intermediate portions (Q4,
Q5) of the heat-source-side liquid refrigerant pipe (43) together. The fourth intermediate
portion (Q4) is a portion of the heat-source-side liquid refrigerant pipe (43) between
the first intermediate portion (Q1) and the second intermediate portion (Q2), and
the fifth intermediate portion (Q5) is a portion of the heat-source-side liquid refrigerant
pipe (43) between the liquid end of the heat-source-side heat exchanger (23) and the
third intermediate portion (Q3).
<<Heat-Source-Side Expansion Valve>>
[0053] The heat-source-side expansion valve (36) is provided on the second connection pipe
(46). The heat-source-side expansion valve (36) has an adjustable degree of opening.
The heat-source-side expansion valve (36) is configured as, for example, an electronic
expansion valve (motor-operated valve).
<<First Check Valve>>
[0054] The first check valve (CV1) is provided between the third and fifth intermediate
portions (Q3, Q5) of the heat-source-side liquid refrigerant pipe (43), and is configured
to allow a refrigerant to flow from the fifth intermediate portion (Q5) toward the
third intermediate portion (Q3) and to disallow a refrigerant to flow in the reverse
direction.
<<Second Check Valve>>
[0055] The second check valve (CV2) is provided between the second and fourth intermediate
portions (Q2, Q4) of the heat-source-side liquid refrigerant pipe (43), and is configured
to allow a refrigerant to flow from the fourth intermediate portion (Q4) toward the
second intermediate portion (Q2) and to disallow a refrigerant to flow in the reverse
direction.
<<Third Check Valve>>
[0056] The third check valve (CV3) is provided on the first connection pipe (45), and is
configured to allow a refrigerant to flow from the second intermediate portion (Q2)
toward the third intermediate portion (Q3) of the heat-source-side liquid refrigerant
pipe (43) and to disallow a refrigerant to flow in the reverse direction.
<<First Oil Separator and First Discharge Check Valve>>
[0057] The first oil separator (OSa) and the first discharge check valve (CVa) are provided
on a portion of the discharge refrigerant pipe (41) between the first compressor (21a)
and the first port of the four-way valve (22) (specifically, on the first discharge
pipe (41a)). The first oil separator (OSa) and the first discharge check valve (CVa)
are arranged on the first discharge pipe (41a) in this order from the inlet toward
the outlet of the first discharge pipe (41a). The first oil separator (OSa) is capable
of separating refrigerating machine oil from a refrigerant discharged from the first
compressor (21a) and storing therein the refrigerating machine oil. The first discharge
check valve (CVa) allows a refrigerant to flow from the inlet toward the outlet of
the first discharge pipe (41a), but disallows a refrigerant to flow in the reverse
direction.
<<Second Oil Separator and Second Discharge Check Valve>>
[0058] The second oil separator (OSb) is provided on a portion of the discharge refrigerant
pipe (41) between the second compressor (21b) and the first port of the four-way valve
(22) (specifically, on the second discharge pipe (41b)). The second oil separator
(OSb) and the second discharge check valve (CVb) are arranged on the second discharge
pipe (41b) in this order from the inlet toward the outlet of the second discharge
pipe (41b). The second oil separator (OSb) is capable of separating refrigerating
machine oil from a refrigerant discharged from the second compressor (21b) and storing
therein the refrigerating machine oil. The second discharge check valve (CVb) allows
a refrigerant to flow from the inlet toward the outlet of the second discharge pipe
(41b), but disallows a refrigerant to flow in the reverse direction.
<<Oil Return Pipe>>
[0059] The oil return pipe (47) is used to supply the refrigerating machine oil stored in
the first and second oil separators (OSa, OSb) to the injection pipe (44). In this
example, the oil return pipe (47) includes first and second oil return sub-pipes (47a,
47b) one end of each of which is connected to an associated one of the first and second
oil separators (OSa, OSb), and a main oil return pipe (47c) connecting the other ends
of the first and second oil return sub-pipes (47a, 47b) to an intermediate portion
of the injection pipe (44) (specifically, an intermediate portion (Q6) of the second
main injection pipe (44n)).
<<First Capillary Tube>>
[0060] The first capillary tube (CTa) is provided on a portion of the oil return pipe (47)
between the first oil separator (OSa) and the intermediate portion (Q6) of the injection
pipe (44) (specifically, on the first oil return sub-pipe (47a)).
<<Second Capillary Tube and Oil Return Check Valve>>
[0061] The second capillary tube (CTb) and the oil return check valve (CVc) are provided
on a portion of the oil return pipe (47) between the second oil separator (OSb) and
the intermediate portion (Q6) of the injection pipe (44) (specifically, on the second
oil return sub-pipe (47b)). The oil return check valve (CVc) and the second capillary
tube (CTb) are arranged on the second oil return sub-pipe (47b) in this order from
the inlet toward the outlet of the second oil return sub-pipe (47b). The oil return
check valve (CVc) allows a refrigerant to flow from the inlet toward the outlet of
the second oil return sub-pipe (47b), but disallows a refrigerant to flow in the reverse
direction.
<Utilization-Side Circuit>
[0062] The utilization-side circuit (18) includes a utilization-side heat exchanger (51),
a utilization-side open/close valve (52), a utilization-side expansion valve (53),
and a utilization-side check valve (54). The utilization-side circuit (18) is provided
with a utilization-side liquid refrigerant pipe (61), a utilization-side gaseous refrigerant
pipe (62), and a bypass pipe (63).
<<Utilization-Side Heat Exchanger>>
[0063] The utilization-side heat exchanger (51) has its liquid end connected to the liquid
interconnecting pipe (13) through the utilization-side liquid refrigerant pipe (61),
and has its gas end connected to the gas interconnecting pipe (14) through the utilization-side
gaseous refrigerant pipe (62). The utilization-side fan (19) is disposed near the
utilization-side heat exchanger (51). The utilization-side heat exchanger (51) is
configured to exchange heat between a refrigerant and utilization-side air (i.e.,
inside air) transferred by the utilization-side fan (19). The utilization-side heat
exchanger (51) is configured as, for example, a cross-fin, fin-and-tube heat exchanger.
<<Utilization-Side Liquid Refrigerant Pipe and Utilization-Side Gaseous Refrigerant
Pipe>>
[0064] One end of the utilization-side liquid refrigerant pipe (61) is connected to the
liquid interconnecting pipe (13), and the other end thereof is connected to the liquid
end of the utilization-side heat exchanger (51). One end of the utilization-side gaseous
refrigerant pipe (62) is connected to the gas end of the utilization-side heat exchanger
(51), and the other end thereof is connected to the gas interconnecting pipe (14).
<<Utilization-Side Open/Close Valve and Utilization-Side Expansion Valve>>
[0065] The utilization-side open/close valve (52) and the utilization-side expansion valve
(53) are provided on the utilization-side liquid refrigerant pipe (61). The utilization-side
open/close valve (52) and the utilization-side expansion valve (53) are arranged on
the utilization-side liquid refrigerant pipe (61) in this order from the one end toward
the other end of the utilization-side liquid refrigerant pipe (61).
[0066] The utilization-side open/close valve (52) is switchable between an open state and
a closed state. The utilization-side open/close valve (52) is configured as, for example,
a solenoid valve. The utilization-side expansion valve (53) has an adjustable degree
of opening. In this example, the utilization-side expansion valve (53) is configured
as an externally equalized thermostatic expansion valve. Specifically, the utilization-side
expansion valve (53) includes a feeler bulb (53a) provided on the utilization-side
gaseous refrigerant pipe (62), and an equalizer (not shown) connected to an intermediate
portion of the utilization-side gaseous refrigerant pipe (62), and has its degree
of opening adjusted in accordance with the temperature of the feeler bulb (53a) and
the pressure of a refrigerant in the equalizer.
<<Bypass Pipe>>
[0067] One end of the bypass pipe (63) is connected to an intermediate portion of the utilization-side
liquid refrigerant pipe (61) between the utilization-side expansion valve (53) and
the utilization-side heat exchanger (51). The other end of the bypass pipe (63) is
connected to an intermediate portion of the utilization-side liquid refrigerant pipe
(61) between the liquid interconnecting pipe (13) and the utilization-side open/close
valve (52).
<<Utilization-Side Check Valve>>
[0068] The utilization-side check valve (54) is provided on the bypass pipe (63). The utilization-side
check valve (54) allows a refrigerant to flow from the utilization-side heat exchanger
(51) toward the liquid interconnecting pipe (13), but disallows a refrigerant to flow
in the reverse direction.
<Various Sensors>
[0069] The refrigeration device (10) is provided with various sensors such as a suction
temperature sensor (71), a suction pressure sensor (72), and an internal temperature
sensor (76).
<<Suction Temperature Sensor>>
[0070] The suction temperature sensor (71) is configured to sense the temperature of a refrigerant
sucked into the first and second compressors (21a, 21b) (hereinafter referred to as
the "suction temperature"). In this example, the suction temperature sensor (71) is
installed on the main suction pipe (42c) to sense the refrigerant temperature at its
installation location as the suction temperature.
<<Suction Pressure Sensor>>
[0071] The suction pressure sensor (72) is configured to sense the pressure of a refrigerant
sucked into the first and second compressors (21a, 21b) (hereinafter referred to as
the "suction pressure"). In this example, the suction pressure sensor (72) is installed
on the main suction pipe (42c) to sense the refrigerant pressure at its installation
location as the suction pressure.
<<Internal Temperature Sensor>>
[0072] The internal temperature sensor (76) is configured to sense the temperature of inside
air (hereinafter referred to as the "internal temperature (Tr)"). In this example,
the internal temperature sensor (76) is installed on a portion of the utilization-side
unit (12) downstream of the air flow from the utilization-side fan (19) to sense the
air temperature at its installation location as the internal temperature (Tr).
<Controller>
[0073] The controller (80) controls components of the refrigeration device (10), based on
values sensed by the various sensors, to control operations of the refrigeration device
(10). In this example, the controller (80) includes a main controller (81) included
in the heat-source-side unit (11), and a utilization-side controller (86) included
in the utilization-side unit (12).
<<Main Controller>>
[0074] The main controller (81) controls components of the heat-source-side unit (11). In
this example, the main controller (81) includes an operation control section (82),
a compressor control section (83), and a target temperature setting section (84).
The operation control section (82) controls the heat-source-side fan (17), the various
valves (in this example, the four-way valve (22), the supercooling expansion valve
(31), the intermediate expansion valve (32), and the intermediate open/close valve
(33)), and other components included in the heat-source-side unit (11). The compressor
control section (83) controls the first and second compressors (21a, 21b). The target
temperature setting section (84) sets a target evaporation temperature (Te) described
below.
<<Utilization-Side Controller>>
[0075] The utilization-side controller (86) controls components of the utilization-side
unit (12) (in this example, the utilization-side fan (19) and the utilization-side
open/close valve (52)).
[0076] The utilization-side controller (86) determines whether or not the refrigeration
device (10) should start operating. If the utilization-side controller (86) determines
that the refrigeration device (10) should start operating, the utilization-side controller
(86) allows a cooling mode (for cooling inside air) to start, and transmits an operation
start signal to the main controller (81). The utilization-side controller (86) further
determines whether or not the refrigeration device (10) should finish operating. If
the utilization-side controller (86) determines that the refrigeration device (10)
should finish operating, the utilization-side controller (86) allows the cooling mode
to end, and transmits an operation end signal to the main controller (81). For example,
the utilization-side controller (86) determines whether or not the refrigeration device
(10) should start operating and whether or not the refrigerating apparatus (10) should
finish operating, in response to user's operations (operations for instructing the
refrigerating apparatus (10) to start operating and to finish operating).
[0077] The utilization-side controller (86) determines whether or not a defrosting mode
(an operation for defrosting the utilization-side heat exchanger (51)) should be started
during a period of time during which an operation is performed in the cooling mode.
If the utilization-side controller (86) determines that the defrosting mode should
be started, the utilization-side controller (86) allows the defrosting mode to start,
and transmits a defrosting start signal to the main controller (81). The utilization-side
controller (86) determines whether or not the defrosting mode should be ended during
a period of time during which the operation is performed in the defrosting mode. If
the utilization-side controller (86) determines that the defrosting mode should be
ended, the utilization-side controller (86) allows the defrosting mode to end, allows
the cooling mode to start, and transmits a defrosting end signal to the main controller
(81). For example, if a predetermined period (a cooling mode period) has elapsed since
the start of the cooling mode, the utilization-side controller (86) determines that
the defrosting mode should be started. If a predetermined period (a defrosting mode
period) has elapsed since the start of the defrosting mode, the utilization-side controller
(86) determines that the defrosting mode should be ended.
<Operation of Refrigeration Device>
[0078] Next, operations of the refrigeration device (10) will be described with reference
to FIG. 2.
<<Step (ST10)>>
[0079] The target temperature setting section (84) that has received the operation start
signal from the utilization-side controller (86) sets the target evaporation temperature
(Te) to be equal to a predetermined reference temperature (Teref). Note that the target
evaporation temperature (Te) is a target temperature set for the temperature of a
refrigerant sucked into the first and second compressors (21a, 21b). The reference
temperature (Teref) is set to be lower than a set internal temperature (Tset). The
set internal temperature (Tset) is a target temperature set for the internal temperature
(Tr). The reference temperature (Teref) is preferably set with consideration given
to pressure loss in a pipe between the liquid end of the utilization-side heat exchanger
(51) and the suction ports of the first and second compressors (21a, 21b) (specifically,
the pipe length, the pipe diameter, the height difference, and other elements). Specifically,
the reference temperature (Teref) is set to be a temperature obtained by subtracting
a predetermined temperature (e.g., a temperature falling within the range from 10°C
to 17°C) from the set internal temperature (Tset).
<<Step (ST11): Cooling Mode>>
[0080] Next, the main controller (81) and the utilization-side controller (86) control components
of the refrigeration device (10) so that the refrigeration device (10) operates in
the cooling mode. In the cooling mode, a refrigeration cycle is performed to cool
inside air. In this refrigeration cycle, the heat-source-side heat exchanger (23),
the supercooling heat exchanger (24), and the utilization-side heat exchanger (51)
of the refrigerant circuit (15) serve as a condenser, a supercooler, and an evaporator,
respectively. How a refrigerant flows through the refrigerant circuit (15) during
the cooling mode and how the target temperature setting section (84) operates in the
cooling mode will be described in detail below.
[0081] The operation control section (82) that has received the operation start signal (or
the defrosting end signal) from the utilization-side controller (86) places the four-way
valve (22) in a first state, and places the heat-source-side fan (17) in a driven
state. The operation control section (82) adjusts the degree of opening of the supercooling
expansion valve (31) so that the degree of supercooling of a refrigerant in the supercooling
heat exchanger (24) (specifically, the degree of supercooling of a refrigerant at
the outlets of the first channels (24a) of the supercooling heat exchanger (24)) is
equal to a predetermined target degree of supercooling, and adjusts the degree of
opening of the intermediate expansion valve (32) so that the degree of superheat of
a refrigerant discharged from the first compressor (21a) is equal to a predetermined
target degree of superheat. The operation control section (82) places the intermediate
open/close valve (33) in an open state, and places the heat-source-side expansion
valve (36) in a fully-closed state.
[0082] The compressor control section (83) that has received the operation start signal
(or the defrosting end signal) from the utilization-side controller (86) places the
first and second compressors (21a, 21b) in a driven state. Then, if the pressure of
a refrigerant sensed by the suction pressure sensor (72) (i.e., the suction pressure)
is above a predetermined low pressure range, the compressor control section (83) places
the first and second compressors (21a, 21b) in a driven state. If the suction pressure
is below the low pressure range, the compressor control section (83) places the first
and second compressors (21a, 21b) at rest. The low pressure range will be described
in detail below.
[0083] The compressor control section (83) controls the operation frequency (FQ) of the
first compressor (21a) so that the temperature of a refrigerant sensed by the suction
temperature sensor (71) (i.e., the suction temperature) is equal to the target evaporation
temperature (Te) set by the target temperature setting section (84). Specifically,
if the suction temperature is higher than the target evaporation temperature (Te),
the compressor control section (83) increases the operation frequency (FQ) of the
first compressor (21a). This reduces the suction temperature to allow the suction
temperature to be closer to the target evaporation temperature (Te). On the other
hand, if the suction temperature is lower than the target evaporation temperature
(Te), the compressor control section (83) reduces the operation frequency (FQ) of
the first compressor (21a). This increases the suction temperature to allow the suction
temperature to be closer to the target evaporation temperature (Te).
[0084] If the utilization-side controller (86) determines that the refrigeration device
(10) should start operating (or should finish operating in the defrosting mode), the
utilization-side controller (86) places the utilization-side fan (19) in a driven
state. If the temperature of air sensed by the internal temperature sensor (76) (i.e.,
the internal temperature (Tr)) is above a set internal temperature range including
the set internal temperature (Tset) (e.g., the temperature range including the set
internal temperature (Tset) as a median value), the utilization-side controller (86)
places the utilization-side open/close valve (52) in an open state to circulate a
refrigerant through the utilization-side heat exchanger (51). Thus, the utilization-side
heat exchanger (51) functions as an evaporator. On the other hand, if the internal
temperature (Tr) is below the set internal temperature range, the utilization-side
controller (86) places the utilization-side open/close valve (52) in a closed state
to interrupt the flow of a refrigerant in the utilization-side heat exchanger (51).
[0085] As can be seen, if the internal temperature (Tr) is above the set internal temperature
range in the cooling mode, the utilization-side unit (12) enters into a cooling state
where a refrigerant is circulated through the utilization-side heat exchanger (51)
to allow the utilization-side heat exchanger (51) to function as an evaporator. If
the internal temperature (Tr) is below the set internal temperature range, the utilization-side
unit (12) enters into a suspended state where the flow of a refrigerant in the utilization-side
heat exchanger (51) is interrupted to suspend the cooling of inside air.
[0086] In the utilization-side unit (12), the degree of opening of the utilization-side
expansion valve (53) varies in accordance with the temperature of the feeler bulb
(53a) and the refrigerant pressure in the equalizer (not shown) so that the degree
of superheat of a refrigerant at the outlet of the utilization-side heat exchanger
(51) is equal to a predetermined degree of superheat.
<<Step (ST12)>>
[0087] The utilization-side controller (86) determines whether or not the defrosting mode
should be started during the cooling mode period (the period during which an operation
is performed in the cooling mode). If the utilization-side controller (86) determines
that the defrosting mode should be started, the utilization-side controller (86) transmits
the defrosting start signal to the main controller (81). Next, the process proceeds
to step (ST13).
<<Step (ST13)>>
[0088] The target temperature setting section (84) that has received the defrosting start
signal from the utilization-side controller (86) sets the target evaporation temperature
(Te) to be equal to the reference temperature (Teref). That is to say, the target
temperature setting section (84) sets the target evaporation temperature (Te) to be
equal to the reference temperature (Teref) after the cooling mode has ended and before
the defrosting mode is started.
<<Step (ST14): Defrosting Mode>>
[0089] Next, the main controller (81) and the utilization-side controller (86) control components
of the refrigeration device (10) so that the refrigeration device (10) operates in
the defrosting mode. In the defrosting mode, the refrigerant circuit (15) performs
a refrigeration cycle to defrost the utilization-side heat exchanger (51). In this
refrigeration cycle, the utilization-side heat exchanger (51) and the heat-source-side
heat exchanger (23) serve as a condenser and an evaporator, respectively. How a refrigerant
flows through the refrigerant circuit (15) during the defrosting mode will be described
in detail below.
[0090] The operation control section (82) that has received the defrosting start signal
from the utilization-side controller (86) places the four-way valve (22) in the second
state, and places the heat-source-side fan (17) in the driven state. The operation
control section (82) further places the supercooling expansion valve (31) and the
intermediate expansion valve (32) in the fully-closed state, places the intermediate
open/close valve (33) in the closed state, and adjusts the degree of opening of the
heat-source-side expansion valve (36) so that the degree of superheat of a refrigerant
at the outlet of the heat-source-side heat exchanger (23) is equal to a predetermined
target degree of superheat.
[0091] The compressor control section (83) that has received the defrosting start signal
from the utilization-side controller (86) places the first and second compressors
(21a, 21b) in the driven state. As in the cooling mode, the compressor control section
(83) controls the operation frequency (FQ) of the first compressor (21a) so that the
temperature of a refrigerant sensed by the suction temperature sensor (71) (i.e.,
the suction temperature) is equal to the target evaporation temperature (Te) set by
the target temperature setting section (84).
[0092] If the utilization-side controller (86) determines that the defrosting mode should
be started, the utilization-side controller (86) places the utilization-side fan (19)
at rest. The utilization-side controller (86) places the utilization-side open/close
valve (52) in the open state to circulate a refrigerant through the utilization-side
heat exchanger (51). Thus, the utilization-side heat exchanger (51) functions as a
condenser. Specifically, the utilization-side unit (12) circulates a refrigerant through
the utilization-side heat exchanger (51), and is thus placed in a heat dissipation
state where the utilization-side heat exchanger (51) functions as a condenser. In
the utilization-side unit (12), the utilization-side expansion valve (53) is placed
in the open state.
<<Step (ST15)>>
[0093] Next, the utilization-side controller (86) determines whether or not the defrosting
mode should be ended during the defrosting mode period (the period during which an
operation is performed in a defrosting mode). If the utilization-side controller (86)
determines that the defrosting mode should be ended, the utilization-side controller
(86) transmits the defrosting end signal to the main controller (81). Next, the process
proceeds to step (ST11).
<Refrigerant Flow in Cooling Mode>
[0094] Next, how a refrigerant flows in the refrigerant circuit (15) during the cooling
mode will be described with reference to FIG. 3. In the cooling mode, the four-way
valve (22) is placed in the first state, in which the discharge ports of the first
and second compressors (21a, 21b) communicate with the gas end of the heat-source-side
heat exchanger (23), and the suction ports of the first and second compressors (21a,
21b) communicate with the gas interconnecting pipe (14).
[0095] A refrigerant discharged from the first and second compressors (21a, 21b) passes
through the first and second oil separators (OSa, OSb) and the first and second discharge
check valves (CVa, CVb) in the discharge refrigerant pipe (41), then flows through
the four-way valve (22) into the heat-source-side heat exchanger (23), dissipates
heat to the heat-source-side air (i.e., outside air) in the heat-source-side heat
exchanger (23), and condenses. The refrigerant (high-pressure refrigerant) that has
flowed out of the heat-source-side heat exchanger (23) passes through the first check
valve (CV1) in the first heat-source-side liquid pipe (43a), then passes through the
receiver (35) and the second heat-source-side liquid pipe (43b) in this order, flows
into the first channels (24a) of the supercooling heat exchanger (24), and is supercooled
by having its heat absorbed by a refrigerant (intermediate-pressure refrigerant) flowing
through the second channels (24b) of the supercooling heat exchanger (24). The refrigerant
that has flowed out of the first channels (24a) of the supercooling heat exchanger
(24) flows into the third heat-source-side liquid pipe (43c). Then, part of the refrigerant
flows into the first main injection pipe (44m). The remaining part passes through
the second check valve (CV2) in the third heat-source-side liquid pipe (43c), and
then flows through the liquid stop valve (VI) into the liquid interconnecting pipe
(13).
[0096] The refrigerant that has flowed into the first main injection pipe (44m) is decompressed
in the supercooling expansion valve (31), flows into the second channels (24b) of
the supercooling heat exchanger (24), and absorbs heat from the refrigerant (high-pressure
refrigerant) flowing through the first channels (24a) of the supercooling heat exchanger
(24). The refrigerant that has flowed out of the second channels (24b) of the supercooling
heat exchanger (24) passes through the second main injection pipe (44n). Then, part
of the refrigerant flows into the first injection branch pipe (44a). The remaining
part flows into the second injection branch pipe (44b). The refrigerant that has flowed
into the first injection branch pipe (44a) is decompressed in the intermediate expansion
valve (32), and flows into the intermediate port of the first compressor (21a). The
refrigerant that has flowed into the second injection branch pipe (44b) passes through
the intermediate open/close valve (33) and the intermediate check valve (34) in this
order, and then flows into the intermediate port of the second compressor (21b). The
refrigerant that has flowed through the intermediate ports into the first and second
compressors (21a, 21b) is mixed with a refrigerant in the first and second compressors
(21a, 21b) (specifically, a refrigerant in the compression chamber). That is to say,
the refrigerant in the first and second compressors (21a, 21b) is compressed while
being cooled.
[0097] On the other hand, the refrigerant that has flowed into the liquid interconnecting
pipe (13) passes through the open utilization-side open/close valve (52) in the utilization-side
liquid refrigerant pipe (61) of the utilization-side unit (12), and is then decompressed
in the utilization-side expansion valve (53). The decompressed refrigerant flows into
the utilization-side heat exchanger (51), and absorbs heat from the utilization-side
air (i.e., inside air) in the utilization-side heat exchanger (51) to evaporate. Thus,
the utilization-side air is cooled. The refrigerant that has flowed out of the utilization-side
heat exchanger (51) passes through the utilization-side gaseous refrigerant pipe (62),
the gas interconnecting pipe (14), and the gas stop valve (V2), the four-way valve
(22), and the suction refrigerant pipe (42) of the heat-source-side unit (11) in this
order, and is sucked into the suction ports of the first and second compressors (21a,
21b).
[0098] The first and second oil separators (OSa, OSb) separate refrigerating machine oil
from the refrigerant (i.e., the refrigerant discharged from the first and second compressors
(21a, 21b)), and store therein the refrigerating machine oil. The refrigerating machine
oil stored in the first oil separator (OSa) passes through the first capillary tube
(CTa) in the first oil return sub-pipe (47a), and then flows into the main oil return
pipe (47c). The refrigerating machine oil stored in the second oil separator (OSb)
passes through the oil return check valve (CVc) and the second capillary tube (CTb)
in this order in the second oil return sub-pipe (47b), and then flows into the main
oil return pipe (47c). The refrigerating machine oil that has flowed into the main
oil return pipe (47c) flows into the second main injection pipe (44n) to join with
a refrigerant flowing through the second main injection pipe (44n).
<Refrigerant Flow in Defrosting Mode>
[0099] Next, how a refrigerant flows through the refrigerant circuit (15) during the defrosting
mode will be described with reference to FIG. 4. In the defrosting mode, the four-way
valve (22) is placed in the second state, in which the discharge ports of the first
and second compressors (21a, 21b) communicate with the gas interconnecting pipe (14),
and the suction ports of the first and second compressors (21a, 21b) communicate with
the gas end of the heat-source-side heat exchanger (23).
[0100] The refrigerant discharged from the first and second compressors (21a, 21b) passes
through the first and second oil separators (OSa, OSb) and the first and second discharge
check valves (CVa, CVb) in the discharge refrigerant pipe (41), then passes through
the four-way valve (22) and the gas stop valve (V2) in this order, and flows into
the gas interconnecting pipe (14). The refrigerant that has flowed into the gas interconnecting
pipe (14) passes through the utilization-side gaseous refrigerant pipe (62) of the
utilization-side unit (12), flows into the utilization-side heat exchanger (51), and
dissipates heat in the utilization-side heat exchanger (51) to condense. Thus, frost
formed on the utilization-side heat exchanger (51) is heated to melt. Part of the
refrigerant that has flowed out of the utilization-side heat exchanger (51) passes
through the open utilization-side expansion valve (53) and the open utilization-side
open/close valve (52) in this order in the utilization-side liquid refrigerant pipe
(61). The remaining part passes through the utilization-side check valve (54) in the
bypass pipe (63). The refrigerant that has passed through the open utilization-side
open/close valve (52) in the utilization-side liquid refrigerant pipe (61) joins with
the refrigerant that has passed through the utilization-side check valve (54) in the
bypass pipe (63), and flows into the liquid interconnecting pipe (13).
[0101] The refrigerant that has passed through the liquid interconnecting pipe (13) passes
through the liquid stop valve (VI) of the heat-source-side unit (11), and flows into
the third heat-source-side liquid pipe (43c). The refrigerant that has flowed into
the third heat-source-side liquid pipe (43c) flows into the first connection pipe
(45) at the second intermediate portion (Q2), passes through the third check valve
(CV3) in the first connection pipe (45), and flows into the intermediate portion (third
intermediate portion (Q3)) of the first heat-source-side liquid pipe (43a). The refrigerant
that has flowed into the intermediate portion of the first heat-source-side liquid
pipe (43a) passes through the receiver (35), the second heat-source-side liquid pipe
(43b), the first channels (24a) of the supercooling heat exchanger (24) in this order,
and flows into the third heat-source-side liquid pipe (43c). The refrigerant that
has flowed into the third heat-source-side liquid pipe (43c) flows into the second
connection pipe (46) at the fourth intermediate portion (Q4), is decompressed in the
heat-source-side expansion valve (36), and flows into the intermediate portion (fifth
intermediate portion (Q5)) of the first heat-source-side liquid pipe (43a). The refrigerant
that has flowed into the intermediate portion of the first heat-source-side liquid
pipe (43a) flows into the heat-source-side heat exchanger (23), and absorbs heat from
the heat-source-side air (i.e., outside air) in the heat-source-side heat exchanger
(23) to evaporate. The refrigerant that has flowed out of the heat-source-side heat
exchanger (23) passes through the four-way valve (22) and the suction refrigerant
pipe (42) in this order, and is sucked into the suction ports of the first and second
compressors (21a, 21b).
<Operation of Target Temperature Setting Section in Cooling Mode>
[0102] Next, how the target temperature setting section (84) operates in the cooling mode
will be described with reference to FIG. 5.
<<Step (ST21)>>
[0103] First, the target temperature setting section (84) determines whether or not the
utilization-side unit (12) is in a suspended state. In this example, if the utilization-side
unit (12) shifts from the cooling state to the suspended state in the cooling mode,
the pressure of the refrigerant sucked into the first and second compressors (21a,
21b) (i.e., the suction pressure) decreases to below the low pressure range. If the
utilization-side unit (12) shifts from the suspended state to the cooling state in
the cooling mode, the suction pressure increases to above the low pressure range.
Specifically, a lower limit of the low pressure range is set to be equal to the suction
pressure obtained when the utilization-side unit (12) is considered to have shifted
from the cooling state to the suspended state, and an upper limit thereof is set to
be equal to the suction pressure obtained when the utilization-side unit (12) is considered
to have shifted from the suspended state to the cooling state. If the suction pressure
is above the low pressure range, the target temperature setting section (84) determines
that the utilization-side unit (12) is in the cooling state. If the suction pressure
is below the low pressure range, the target temperature setting section (84) determines
that the utilization-side unit (12) is in the suspended state. Specifically, if the
suction pressure decreases to below the low pressure range, the target temperature
setting section (84) determines that the utilization-side unit (12) has shifted from
the cooling state to the suspended state. If the suction pressure increases to above
the low pressure range, the target temperature setting section (84) determines that
the utilization-side unit (12) has shifted from the suspended state to the cooling
state. If a determination is made that the utilization-side unit (12) is in the suspended
state, the process proceeds to step (ST23). If not, the process proceeds to step (ST22).
<<Step (ST22)>>
[0104] If, in step (ST21), a determination is not made that the utilization-side unit (12)
is in the suspended state (i.e., if the utilization-side unit (12) is in the cooling
state), the target temperature setting section (84) determines whether or not a predetermined
period of time (T1) has elapsed since the start of the cooling mode. Note that the
predetermined period of time (T1) is set to be equal to a period of time that it is
estimated to take from the start of the cooling mode to a time when the internal temperature
(Tr) decreases to a temperature near the set internal temperature (Tset) (e.g., 24
hours). If a determination is made that the predetermined period of time (T1) has
elapsed, the process proceeds to step (ST23). If not, the process proceeds to step
(ST21).
[0105] As can be seen, the target temperature setting section (84) determines, in steps
(ST21, ST22), whether or not a period of time required to reduce the internal temperature
(Tr) (hereinafter referred to as the "pull-down period (PD)") has elapsed since the
start of the cooling mode. Specifically, in this example, the pull-down period (PD)
corresponds to a shorter one of a period of time from a time when the cooling mode
is started to a time when the utilization-side unit (12) has shifted from the cooling
state to the suspended state or a period of time from the time when the cooling mode
is started to a time when the predetermined period of time (T1) has elapsed since
the start of the cooling mode. If a determination is made that the pull-down period
(PD) has elapsed since the start of the cooling mode, the process proceeds to step
(ST23).
<<Step (ST23)>>
[0106] Next, the target temperature setting section (84) determines whether or not the utilization-side
unit (12) is in the cooling state. In this example, if the suction pressure is above
the low pressure range, the target temperature setting section (84) determines that
the utilization-side unit (12) is in the cooling state. If the suction pressure is
below the low pressure range, the target temperature setting section (84) determines
that the utilization-side unit (12) is in the suspended state. Specifically, if the
suction pressure decreases to below the low pressure range, the target temperature
setting section (84) determines that the utilization-side unit (12) has shifted from
the cooling state to the suspended state. If the suction pressure increases to above
the low pressure range, the target temperature setting section (84) determines that
the utilization-side unit (12) has shifted from the suspended state to the cooling
state. If a determination is made that the utilization-side unit (12) is in the cooling
state, the process proceeds to step (ST24).
<<Step (ST24)>>
[0107] Next, the target temperature setting section (84) starts measuring a period of time
(Ton) that has elapsed since the utilization-side unit (12) determined in step (ST23)
that the utilization-side unit (12) was in the cooling state. That is to say, the
target temperature setting section (84) measures the length of time during which the
utilization-side unit (12) is in the cooling state (hereinafter referred to as the
"cooling duration"). In this example, the cooling duration corresponds to a period
of time from a time when the utilization-side unit (12) shifts from the suspended
state to the cooling state to a time when the utilization-side unit (12) subsequently
shifts from the cooling state to the suspended state, or a period of time from a time
when the pull-down period (PD) ends to a time when the utilization-side unit (12)
subsequently shifts from the cooling state to the suspended state.
<<Step (ST25)>>
[0108] Next, the target temperature setting section (84) determines whether or not the utilization-side
unit (12) is in the suspended state. If the utilization-side unit (12) is in the suspended
state, the process proceeds to step (ST26). If not, the process proceeds to step (ST29).
<<Step (ST26)>>
[0109] Next, the target temperature setting section (84) determines whether or not a frequency
index value (FQi) during the cooling duration (i.e., the period of time during which
the utilization-side unit (12) is in the cooling state) is above a predetermined reference
value (FQref).
[0110] Note that the frequency index value (FQi) depends on the operation frequency (FQ)
of the first compressor (21a) during the cooling duration. For example, as shown in
FIG. 6, the frequency index value (FQi) may correspond to the average (FQave) of the
operation frequencies (FQ) of the first compressor (21a) during the cooling duration.
Alternatively, the frequency index value (FQi) may correspond to the operation frequency
(FQ) of the first compressor (21a) obtained when the utilization-side unit (12) shifts
from the cooling state to the suspended state.
[0111] The reference value (FQref) is a value based on which a determination is made whether
or not the operation frequency of the first compressor (21a) is relatively high. For
example, the reference value (FQref) is set to correspond to 60% of a maximum value
(FQmax) of the operation frequency (FQ) of the first compressor (21a).
[0112] If a determination is made that the frequency index value (FQi) is above the reference
value (FQref), the process proceeds to step (ST27). If not, the process proceeds to
step (ST23).
<<Step (ST27)>>
[0113] Next, the target temperature setting section (84) determines whether or not the present
target evaporation temperature (Te) is equal to a predetermined upper-limit temperature
(Temax). In this example, the upper-limit temperature (Temax) is set to be equal to
the target evaporation temperature (Te) at which the utilization-side unit (12) may
be considered to have cooling capability high enough to appropriately cool inside
air in the cooling mode. Specifically, the upper-limit temperature (Temax) is set
to be equal to a temperature obtained by adding a predetermined temperature (e.g.,
3°C) to the reference temperature (Teref). If a determination is made that the present
target evaporation temperature (Te) is equal to the upper-limit temperature (Temax),
the process proceeds to step (ST23). If not, the process proceeds to step (ST28).
<<Step (ST28)>>
[0114] Next, the target temperature setting section (84) corrects the target evaporation
temperature (Te) so that the target evaporation temperature (Te) increases. Specifically,
the target temperature setting section (84) increases the target evaporation temperature
(Te) by a predetermined temperature (e.g., 1°C). Next, the process proceeds to step
(ST23).
<<Step (ST29)>>
[0115] On the other hand, if a determination is not made, in step (ST25), that the utilization-side
unit (12) is in the suspended state (i.e., if the utilization-side unit (12) in the
cooling state), the target temperature setting section (84) determines whether or
not the period of time (Ton) is above a predetermined duration threshold (Tth). In
this example, the duration threshold (Tth) is set to be equal to a period of time
(e.g., one hour) corresponding to a cooling duration (the length of time during which
the utilization-side unit (12) is in the cooling state) required when the internal
cooling load may be considered to have increased after the pull-down period (PD) has
elapsed. If the period of time (Ton) is above the duration threshold (Tth), the process
proceeds to step (ST30). If not, the process proceeds to step (ST25).
<<Step (ST30)>>
[0116] Next, the target temperature setting section (84) determines whether or not the target
evaporation temperature (Te) is equal to the reference temperature (Teref). If a determination
is made that the target evaporation temperature (Te) is equal to the reference temperature
(Teref), the process proceeds to step (ST24). If not, the process proceeds to step
(ST31).
<<Step (ST31)>>
[0117] Next, the target temperature setting section (84) corrects the target evaporation
temperature (Te) so that the target evaporation temperature (Te) decreases to be closer
to, or equal to, the reference temperature (Teref). Specifically, the target temperature
setting section (84) reduces the target evaporation temperature (Te) by a predetermined
temperature (e.g., 1°C). Next, the process proceeds to step (ST24). In other words,
the period of time (Ton) is set to be zero, and measurement of the period of time
(Ton) is restarted.
<Change in Internal Temperature>
[0118] Next, how the internal temperature (Tr) changes will be described with reference
to FIG. 7.
[0119] At a time (t0), the refrigeration device (10) starts operating to start operating
in the cooling mode. Thus, the utilization-side unit (12) is in the cooling state.
This allows the cooling of inside air to start. Thus, the internal temperature (Tr)
gradually decreases.
[0120] At a time (t1), the internal temperature (Tr) is below the set internal temperature
range, and the utilization-side unit (12) shifts form the cooling state to the suspended
state. That is to say, the utilization-side unit (12) performs a thermo-off operation.
This allows the pull-down period (PD) to end. Specifically, in the example shown in
FIG. 7, the pull-down period (PD) is a period of time from a time when the cooling
mode starts to a time when the utilization-side unit (12) shifts from the cooling
state to the suspended state. When the utilization-side unit (12) shifts from the
cooling state to the suspended state, the cooling of the inside air is suspended.
Thus, the internal temperature (Tr) gradually increases.
[0121] At a time (t2), the internal temperature (Tr) is above the set internal temperature
range, and the utilization-side unit (12) shifts from the suspended state to the cooling
state. That is to say, the utilization-side unit (12) performs a thermo-on operation.
This allows the cooling of the inside air to restart. Thus, the internal temperature
(Tr) gradually decreases.
[0122] At a time (t3), the internal temperature (Tr) is below the set internal temperature
range, and the utilization-side unit (12) shifts from the cooling state to the suspended
state. This allows the cooling of the inside air to be suspended. Thus, the internal
temperature (Tr) gradually increases.
[0123] The utilization-side unit (12) alternately and repeatedly performs the thermo-off
operation (an operation to shift from the cooling state to the suspended state) and
the thermo-on operation (an operation to shift from the suspended state to the cooling
state) during a period of time from the time (t3) to the time (t4). This can stabilize
the internal temperature (Tr) near the set internal temperature (Tset).
[0124] At a time (t4), the cooling mode ends, and the defrosting mode is started. Thus,
the utilization-side unit (12) enters into the heat dissipation state. Thus, the defrosting
of the utilization-side heat exchanger (51) is started. The heat dissipation of the
utilization-side heat exchanger (51) causes the internal temperature (Tr) to gradually
increase.
[0125] At a time (t5), the defrosting mode ends, and the cooling mode is restarted. Thus,
the utilization-side unit (12) enters into the cooling state. This allows the cooling
of the inside air to restart. Thus, the internal temperature (Tr) gradually decreases.
[0126] As can be seen, upon the start of the cooling mode, the utilization-side unit (12)
enters into the cooling state. Thus, the internal temperature (Tr) gradually decreases.
If the pull-down period (PD) has elapsed since the start of the cooling mode, the
internal temperature (Tr) becomes close to the set internal temperature (Tset). Thus,
the internal cooling load decreases. That is to say, after the pull-down period (PD)
has elapsed since the start of the cooling mode (during the period of time from the
time (t1) to the time (t4) in FIG. 7), the internal temperature (Tr) is stable near
the set internal temperature (Tset). Thus, the internal cooling load is considered
to be relatively low. The period during which the internal temperature (Tr) is stable
near the set internal temperature (Tset) and the internal cooling load is relatively
low is hereinafter referred to as the "low internal load period."
<Change in Operation Frequency of Compressor>
[0127] Next, how the operation frequency (FQ) of the first compressor (21a) changes during
the period of time during which an operation is performed in the cooling mode will
be described with reference to FIGS. 8 and 9. FIG. 8 shows how the internal temperature
(Tr) and the operation frequency (FQ) change if the target evaporation temperature
(Te) is always the reference temperature (Teref) during the period of time during
which the operation is performed in the cooling mode (i.e., in a comparative example
of the refrigeration device (10)). FIG. 9 shows how the internal temperature (Tr)
and the operation frequency (FQ) change if the target evaporation temperature (Te)
is corrected in accordance with the frequency index value (FQi) during the period
of time during which the operation is performed in the cooling mode (i.e., in the
refrigeration device (10) according to this embodiment).
[0128] In FIGS. 8 and 9, the cooling mode is started at the time (t0), and the cooling mode
ends at the time (t1). For convenience of description, FIGS. 8 and 9 do not show how
the internal temperature (Tr) and the operation frequency (FQ) change during the period
of time (suspension duration) from a time when the utilization-side unit (12) shifts
from the cooling state to the suspended state to a time when the utilization-side
unit (12) subsequently shifts from the suspended state to the cooling state.
<<Change in refrigeration device of Comparative Example>>
[0129] As shown in FIG. 8, in the refrigeration device (10) of a comparative example, the
target evaporation temperature (Te) is a fixed value (the reference temperature (Teref))
during the period of time from the time (t1) to the time (t2). The operation frequency
(FQ) of the first compressor (21a) is close to the maximum value (FQmax) of the operation
frequency (FQ) during the pull-down period (PD), and gradually decreases after the
pull-down period (PD) has elapsed.
<<Change in refrigeration device of Embodiment>>
[0130] On the other hand, as shown in FIG. 9, in the refrigeration device (10) of this embodiment,
the target evaporation temperature (Te) is corrected during the period of time from
the time (t1) to the time (t2). In the example shown in FIG. 9, the reference value
(FQref) is set to correspond to 60% of the maximum value (FQmax) of the operation
frequency (FQ) of the first compressor (21a). The target temperature setting section
(84) is configured to increase the target evaporation temperature (Te) by 1°C if a
determination is made that the frequency index value (FQi) is above the reference
value (FQref).
[0131] Specifically, at a time (t11), the target temperature setting section (84) determines
that the frequency index value (FQi) during the period of time from the time (t1)
to the time (t11) (e.g., the average (FQave) of the operation frequencies (FQi) of
the first compressor (21a) during the period of time from the time (t1) to the time
(t11)) is above the reference value (FQref). Thus, the target temperature setting
section (84) increases the target evaporation temperature (Te) by 1°C. Next, at a
time (t12), the target temperature setting section (84) determines that the frequency
index value (FQi) during the period of time from the time (t11) to the time (t12)
is above the reference value (FQref). Thus, the target temperature setting section
(84) increases the target evaporation temperature (Te) by 1°C. Next, at a time (t13),
the target temperature setting section (84) determines that the frequency index value
(FQi) during the period of time from the time (t12) to the time (t13) is above the
reference value (FQref). Thus, the target temperature setting section (84) increases
the target evaporation temperature (Te) by 1°C.
[0132] In the refrigeration device (10) according to this embodiment, if the target temperature
setting section (84) corrects the target evaporation temperature (Te) so that the
target evaporation temperature (Te) increases, the compressor control section (83)
reduces the operation frequency (FQ) of the first compressor (21a) so that the temperature
of a refrigerant sucked into the first compressor (21a) increases. Specifically, correcting
the target evaporation temperature (Te) at the times (t11, t12, t13) so that the target
evaporation temperature (Te) increases can facilitate reducing the operation frequency
(FQ) of the first compressor (21a) during the low internal load period (the period
of time from the time (t1) to the time (t2) in FIG. 9) in the cooling mode, as compared
with a case where the target evaporation temperature (Te) is a fixed value.
[0133] Reducing the operation frequency (FQ) of the first compressor (21a) triggers a reduction
in the cooling capability of the utilization-side unit (12). This increases the period
of time during which the utilization-side unit (12) is in the cooling state (the cooling
duration), and also increases the period of time during which the first compressor
(21a) is placed in the driven state. In general, if a compressor is driven at low
operation frequencies for a long time, the compressor tends to have higher operating
efficiency than if a compressor is driven at high operation frequencies for a short
time. Thus, reducing the operation frequency (FQ) of the first compressor (21a) during
the low internal load period in the cooling mode can improve the operating efficiency
of the first compressor (21a) to increase the coefficient of performance (COP) of
the refrigeration device (10).
<Advantages of Embodiment>
[0134] As can be seen from the foregoing description, the target temperature setting section
(84) sets the target evaporation temperature (Te) to be equal to the reference temperature
(Teref) between the time when the cooling mode starts and the time when the pull-down
period (PD) has elapsed since the start of the cooling mode (step (ST10)). This allows
the utilization-side unit (12) to have sufficiently high cooling capability during
the pull-down period (PD). Thus, the inside air can be appropriately cooled during
the pull-down period (PD).
[0135] If, after the pull-down period (PD) has elapsed, the frequency index value (FQi)
during the cooling duration (the period of time during which the utilization-side
unit (12) is in the cooling state) is above the reference value (FQref), the target
temperature setting section (84) corrects the target evaporation temperature so that
the target evaporation temperature (Te) is higher than the reference temperature (Teref)
(steps (ST21-ST28)). Thus, if the first compressor (21a) is driven at relatively high
operation frequencies during the low internal load period after the pull-down period
(PD) has elapsed, increasing the target evaporation temperature (Te) can facilitate
reducing the operation frequency (FQ) of the first compressor (21a). This can increase
the coefficient of performance (COP) of the refrigeration device (10) during the low
internal load period in the cooling mode.
[0136] An increase in the target evaporation temperature (Te) during the low internal load
period in the cooling mode reduces the cooling capability of the utilization-side
unit (12). This can reduce the amount of frost formed on the utilization-side heat
exchanger (51). This can shorten the defrosting mode period (the period of time during
which an operation is performed in the defrosting mode), and can reduce the power
consumed in the defrosting mode.
[0137] The target temperature setting section (84) corrects the target evaporation temperature
(Te) to prevent the target evaporation temperature (Te) from being above the upper-limit
temperature (Temax) (step (ST27)). An excessively high target evaporation temperature
(Te) may cause the utilization-side unit (12) to have insufficient cooling capability.
This may prevent inside air from being appropriately cooled. Thus, correcting the
target evaporation temperature (Te) to prevent the target evaporation temperature
(Te) from being above the upper-limit temperature (Temax) can prevent the target evaporation
temperature (Te) from becoming too high. This can prevent an increase in the target
evaporation temperature (Te) from causing lack of the cooling capability of the utilization-side
unit (12). Thus, the inside air can be appropriately cooled in the cooling mode.
[0138] If the target evaporation temperature (Te) is higher than the reference temperature
(Teref), and the cooling duration (the period of time during which the utilization-side
unit (12) is in the cooling state) is longer than the duration threshold (Tth), the
target temperature setting section (84) corrects the target evaporation temperature
(Te) so that the target evaporation temperature (Te) decreases to be closer to, or
equal to, the reference temperature (Teref) (steps (ST29-ST31)). During the low internal
load period after a lapse of the pull-down period (PD), the opening/closing of a door
and other factors may cause outside heat to enter the internal space. This may increase
the internal cooling load. An increase in the internal cooling load as above triggers
an increase in the cooling duration (the period of time during which the utilization-side
unit (12) is in the cooling state). Thus, if, when the cooling duration is longer
than the duration threshold (Tth), the target evaporation temperature (Te) is reduced,
the cooling capability of the utilization-side unit (12) can be increased when the
internal cooling load is high during the low internal load period after a lapse of
the pull-down period (PD). This allows the internal temperature (Tr) to be rapidly
closer to the set internal temperature (Tset).
[0139] The target temperature setting section (84) sets the target evaporation temperature
(Te) at the reference temperature (Teref) after the end of the cooling mode and before
the start of the defrosting mode (step (ST13)). This allows the utilization-side unit
(12) to have sufficiently high heat dissipation capability (specifically, allows the
utilization-side heat exchanger (51) to have sufficiently high heat dissipation capability)
in the defrosting mode. Thus, the utilization-side heat exchanger (51) can be appropriately
defrosted in the defrosting mode.
[0140] The pull-down period (PD) corresponds to a shorter one of a period of time from a
time when the cooling mode starts to a time when the utilization-side unit (12) shifts
from the cooling state to the suspended state or a period of time from the time when
the cooling mode starts to a time when the predetermined period of time (T1) has elapsed
since the start of the cooling mode. Note that if the utilization-side unit (12) shifts
form the cooling state to the suspended state after the start of the cooling mode,
the internal temperature (Tr) can be considered to be close to the set internal temperature
(Tset). In addition, also if a sufficient period of time (i.e., the predetermined
period of time (T1)) has elapsed since the start of the cooling mode, the internal
temperature (Tr) can be considered to be close to the set internal temperature (Tset).
Thus, if a shorter one of the period of time from the time when the cooling mode starts
to the time when the utilization-side unit (12) shifts from the cooling state to the
suspended state or a period of time from the time when the cooling mode starts to
the time when the predetermined period of time (T1) has elapsed since the start of
the cooling mode is defined as the pull-down period (PD), the internal temperature
(Tr) can be reduced to a temperature close to the set internal temperature (Tset)
during the pull-down period (DP).
(Other Embodiments)
[0141] In the foregoing description, a shorter one of the period of time from the time when
the cooling mode starts to the time when the utilization-side unit (12) shifts from
the cooling state to the suspended state and the period of time from the time when
the cooling mode starts to the time when the predetermined period of time (T1) has
elapsed since the start of the cooling mode, for example, is defined as the pull-down
period (PD). However, the pull-down period (PD) may be the period of time from the
time when the cooling mode starts to the time when the utilization-side unit (12)
shifts from the cooling state to the suspended state. In other words, step (ST22)
shown in FIG. 5 may be omitted. Alternatively, the pull-down period (PD) may be the
period of time from the time when the cooling mode starts to the time when the predetermined
period of time (T1) has elapsed since the start of the cooling mode. In other words,
step (ST21) shown in FIG. 5 may be omitted.
[0142] Note that the foregoing description of the embodiment is a merely preferred example
in nature, and is not intended to limit the scope, application, or uses of the present
disclosure.
INDUSTRIAL APPLICABILITY
[0143] As can be seen from the foregoing description, the above-mentioned refrigeration
device is useful as a refrigeration device which cools inside air.
DESCRIPTION OF REFERENCE CHARACTERS
[0144]
- 10
- Refrigeration Device
- 11
- Heat-Source-Side Unit
- 12
- Utilization-Side Unit
- 15
- Refrigerant Circuit
- 21a
- First Compressor (Compressor)
- 21b
- Second Compressor
- 22
- Four-Way Valve
- 23
- Heat-Source-Side Heat Exchanger
- 24
- Supercooling Heat Exchanger
- 51
- Utilization-Side Heat Exchanger
- 52
- Utilization-Side Open/Close valve
- 53
- Utilization-Side Expansion Valve
- 71
- Suction Temperature Sensor
- 72
- Suction Pressure Sensor
- 76
- Internal Temperature Sensor
- 80
- Controller
- 81
- Main Controller
- 82
- Operation Control Section
- 83
- Compressor Control Section
- 84
- Target Temperature Setting Section
- 86
- Utilization-Side Controller