TECHNICAL FIELD
[0001] The present invention relates to a refrigeration apparatus.
BACKGROUND ART
[0002] A refrigeration apparatus that has been proposed in the related art includes an oil
separator and an oil return pipe for a compressor in order to prevent exhaustion of
a refrigerating machine oil as a lubricant in the compressor.
[0003] For example, Patent Literature 1 (
JP 2011a-208860 A) discloses a refrigeration apparatus that includes an oil separator disposed on a
discharge side of a compressor and configured to separate a refrigerating machine
oil from a refrigerant, and an oil return circuit configured to return the refrigerating
machine oil separated by the oil separator to an upstream side of a gas-liquid separator
disposed on a suction side of the compressor. The refrigeration apparatus also includes
an electronic expansion valve whose throttle opening degree is controllable, the electronic
expansion valve being disposed at some midpoint to the oil return circuit. The opening
degree of the electronic expansion valve is controlled in accordance with an operating
frequency of the compressor and a difference in pressure between the suction side
and discharge side of the compressor. The refrigerating machine oil is thus returned
in appropriate amounts to the compressor.
SUMMARY OF THE INVENTION
<Technical Problem>
[0004] However, Patent Literature 1 discloses only the refrigeration apparatus configured
to control the opening degree of the electronic expansion valve for the oil return
circuit in accordance with the operating frequency of the compressor and the difference
in pressure between the suction side and discharge side of the compressor, but gives
no considerations on other control methods.
[0005] In addition, if the oil separator does not separate the refrigerating machine oil
so much, the refrigerating machine oil flows in considerably small amounts through
the oil return circuit. Consequently, only a discharge gas refrigerant from the compressor
may substantially flow through the oil return circuit. If only the discharge gas refrigerant
flows through the oil return circuit, such a situation may lower the coefficient of
performance of the refrigeration apparatus.
[0006] In view of the respects described above, the present invention provides a refrigeration
apparatus that is capable of implementing a novel control method capable of suppressing
occurrence of a situation in which a refrigerating machine oil from an oil separator
is unsatisfactorily returned to a compressor and a discharge gas refrigerant is mostly
returned to the compressor.
<Solutions to Problem>
[0007] According to a first aspect, a refrigeration apparatus includes a compressor, an
oil separator, a refrigerant supply pipe, an oil return pipe, a flow rate adjusting
mechanism, and a control unit. The oil separator is disposed on a discharge side of
the compressor. The refrigerant supply pipe leads supply of a refrigerant to the compressor.
The oil return pipe connects the oil separator to the refrigerant supply pipe. The
flow rate adjusting mechanism is disposed on the oil return pipe. The control unit
is configured to control the flow rate adjusting mechanism to reduce a flow rate when
a temperature of the refrigerant discharged from the compressor or a pressure of the
refrigerant flowing through the refrigerant supply pipe satisfies a predetermined
condition.
[0008] The refrigerant supply pipe may be a pipe for supplying the refrigerant to a suction
side of the compressor or may be a pipe for supplying the refrigerant to a middle
of a compression process in the compressor.
[0009] Examples of the predetermined condition may include, but not limited to, a case where
a discharge temperature rise rate at the compressor is more than a predetermined value
(i.e., a case where a discharge temperature rise speed is more than a predetermined
rise speed) and a case where a refrigerant pressure drop rate at the refrigerant supply
pipe is more than a predetermined value (i.e., a case where a refrigerant pressure
drop speed at the refrigerant supply pipe is more than a predetermined drop speed).
[0010] In the refrigeration apparatus, the control unit causes the flow rate adjusting mechanism
to reduce the flow rate of a fluid (the refrigerant and/or a refrigerating machine
oil) passing through the flow rate adjusting mechanism, when the temperature of the
refrigerant discharged from the compressor or the pressure of the refrigerant flowing
through the refrigerant supply pipe satisfies the predetermined condition.
[0011] In this case, the fluid flowing through the oil return pipe includes a small amount
of refrigerating machine oil, and the fluid flowing through the oil return pipe includes
a large amount of discharge gas refrigerant. If the discharge gas refrigerant is mostly
returned to the compressor, the temperature of the refrigerant discharged from the
compressor rises by repetition of gas refrigerant compressing operation by the compressor.
[0012] In a situation in which the refrigerating machine oil passes in large amounts through
the flow rate adjusting mechanism on the oil return pipe, the refrigerating machine
oil remains in a liquid state without phase change before flowing into the flow rate
adjusting mechanism and after flown out of the flow rate adjusting mechanism. Since
the refrigerating machine oil is higher in viscosity than the discharge gas refrigerant,
the flow velocity of the refrigerating machine oil is less prone to increase at the
time when the refrigerating machine oil passes through the flow rate adjusting mechanism.
Consequently, in the situation in which the refrigerating machine oil passes in large
amounts through the flow rate adjusting mechanism on the oil return pipe, the refrigerating
machine oil passes with smaller resistance; therefore, the flow rate adjusting mechanism
is less prone to cause considerable decompression.
[0013] In contrast to this, the discharge gas refrigerant is lower in viscosity than the
refrigerating machine oil. Therefore, in a situation in which the refrigerating machine
oil passes in small amounts through the flow rate adjusting mechanism on the oil return
pipe and the discharge gas refrigerant passes in large amounts through the flow rate
adjusting mechanism on the oil return pipe, the flow velocity of the discharge gas
refrigerant is apt to increase at the time when the discharge gas refrigerant passes
through the flow rate adjusting mechanism. Consequently, in the situation in which
the discharge gas refrigerant passes in large amounts through the flow rate adjusting
mechanism on the oil return pipe, the discharge gas refrigerant passes with higher
resistance, so that the flow rate adjusting mechanism is apt to cause decompression.
A change from the situation in which the refrigerating machine oil passes in large
amounts through the flow rate adjusting mechanism on the oil return pipe to the situation
in which the gas refrigerant passes in large amount though the flow rate adjusting
mechanism on the oil return pipe causes a reduction in pressure of the refrigerant
flowing through the refrigerant supply pipe to which the oil return pipe is connected.
[0014] Hence, detecting a discharge refrigerant temperature rise at the compressor or a
refrigerant pressure drop at the refrigerant supply pipe enables a grasp of a situation
in which the gas refrigerant rather than the refrigerating machine oil is mostly returned
to the compressor.
[0015] Consequently, for example, in the case where the discharge temperature rise rate
at the compressor is more than the predetermined value (i.e., in the case where the
discharge temperature rise speed is more than the predetermined rise speed) or in
the case where the refrigerant pressure drop rate at the refrigerant supply pipe is
more than the predetermined value (i.e., in the case where the refrigerant pressure
drop speed at the refrigerant supply pipe is more than the predetermined drop speed),
reducing the flow rate of the fluid passing through the flow rate adjusting mechanism
prevents return of the gas refrigerant rather than the refrigerating machine oil at
the oil return pipe. This configuration therefore suppresses occurrence of a situation
in which the refrigerating machine oil from the oil separator is unsatisfactorily
returned to the compressor and the discharge gas refrigerant is mostly returned to
the compressor.
[0016] According to a second aspect, in the refrigeration apparatus according to the first
aspect, the control unit performs normal control to control the flow rate adjusting
mechanism, based on an amount of oil loss in the compressor, the amount of oil loss
being obtained by multiplying a circulation amount of refrigerant in the compressor
by a rate of oil loss in the compressor. When the predetermined condition is satisfied
in the normal control, the control unit controls the flow rate adjusting mechanism
to further reduce the flow rate from a state of the flow rate adjusting mechanism
in the normal control.
[0017] The circulation amount of refrigerant may be expressed in terms of mass or may be
expressed in terms of volume. Preferably, the circulation amount of refrigerant is
expressed in terms of mass.
[0018] The rate of oil loss refers to an amount of refrigerating machine oil contained per
unit circulation amount of the refrigerant discharged from the compressor. For example,
the rate of oil loss may be calculated based on a driving frequency of the compressor
as well as a high pressure, an intermediate pressure, and a low pressure in a refrigeration
cycle. The rate of oil loss may also be calculated in additional consideration of
the degree of superheating of the refrigerant to be sucked into the compressor. However,
the calculation method is not limited thereto.
[0019] In the refrigeration apparatus, when the predetermined condition is satisfied in
the normal control, the control unit causes the flow rate adjusting mechanism to further
reduce the flow rate from the state of the flow rate adjusting mechanism in the normal
control. As described above, the refrigeration apparatus enables the control to reduce
the flow rate in addition to the normal control. Therefore, even in the situation
in which the discharge gas refrigerant is mostly returned to the compressor because
of continuation of the normal control, the reduction in flow rate by the flow rate
adjusting mechanism suppresses occurrence of the situation in which the refrigerating
machine oil from the oil separator is unsatisfactorily returned to the compressor
and the discharge gas refrigerant is mostly returned to the compressor.
[0020] According to a third aspect, the refrigeration apparatus according to the first or
second aspect further includes a heat source-side heat exchanger and an intermediate
expansion valve. The heat source-side heat exchanger is configured to condense the
refrigerant discharged from the compressor. The refrigerant supply pipe is an injection
pipe through which a part of the refrigerant condensed by the heat source-side heat
exchanger is guided to a middle of a compression process in the compressor. The intermediate
expansion valve is disposed at a middle of the injection pipe.
[0021] In the refrigeration apparatus, the oil return pipe leads, for example, the refrigerating
machine oil separated by the oil separator to be guided to the middle of the compression
process in the compressor, via the injection pipe. As described above, a part of the
high-temperature fluid discharged from the compressor toward the oil separator is
guided to the middle of the compression process in the compressor, rather than the
suction side of the compressor. This configuration therefore suppresses occurrence
of a situation in which heat energy of a part of the high-temperature fluid discharged
from the compressor is used for raising a suction refrigerant temperature at the compressor.
[0022] According to a fourth aspect, in the refrigeration apparatus according to any of
the first to third aspects, the control unit controls the flow rate adjusting mechanism
to a state that blocks passage of the refrigerant through the flow rate adjusting
mechanism upon activation of the compressor.
[0023] Causing the flow rate adjusting mechanism to block the passage of the refrigerant
through the flow rate adjusting mechanism upon activation of the compressor may be
effected in at least a part of a period in which the frequency of the compressor increases.
Such control is not necessarily effected over the entire period in which the frequency
of the compressor increases. For example, the control used herein involves a case
where the flow rate adjusting mechanism permits the passage of the refrigerant at
the time when the frequency of the compressor starts to increase, and then blocks
the passage of the refrigerant at the time when the frequency of the compressor further
increases.
[0024] In the refrigeration apparatus, the flow rate adjusting mechanism blocks the passage
of the refrigerant when the frequency of the compressor, which has been stopped, increases
upon activation of the compressor. This configuration therefore efficiently increases
a difference between a pressure at the discharge side of the compressor and a pressure
at the side, to which the refrigerant supply pipe is connected, of the compressor
in such a manner that the flow rate adjusting mechanism blocks the passage of the
refrigerant upon activation of the compressor.
[0025] According to a fifth aspect, in the refrigeration apparatus according to any of the
first to fourth aspects, the control unit controls the flow rate adjusting mechanism
to a state that permits passage of the refrigerant through the flow rate adjusting
mechanism before activation of the compressor.
[0026] In the refrigeration apparatus, the flow rate adjusting mechanism permits the passage
of the refrigerant before activation of the compressor. This configuration therefore
achieves pressure equalization by reducing the difference between the pressure at
the discharge side of the compressor and the pressure at the side, to which the refrigerant
supply pipe is connected, of the compressor. This configuration also allows the refrigerating
machine oil in the oil separator to be dissolved into the refrigerant in the compressor
via the oil return pipe and the refrigerant supply pipe. This configuration thus enables
more reliable activation of the compressor.
<Advantageous Effects of Invention>
[0027] The refrigeration apparatus according to the first aspect suppresses occurrence of
the situation in which the refrigerating machine oil from the oil separator is unsatisfactorily
returned to the compressor and the discharge gas refrigerant is mostly returned to
the compressor.
[0028] The refrigeration apparatus according to the second aspect suppresses occurrence
of the situation in which the refrigerating machine oil from the oil separator is
unsatisfactorily returned to the compressor and the discharge gas refrigerant is mostly
returned to the compressor, by the reduction in flow rate by the flow rate adjusting
mechanism, even in the situation in which the discharge gas refrigerant is mostly
returned to the compressor because of continuation of the normal control.
[0029] The refrigeration apparatus according to the third aspect suppresses the situation
in which heat energy of a part of the high-temperature fluid discharged from the compressor
is used for raising the suction refrigerant temperature at the compressor.
[0030] The refrigeration apparatus according to the fourth aspect efficiently increases
the difference between the pressure at the discharge side of the compressor and the
pressure at the side, to which the refrigerant supply pipe is connected, of the compressor
in such a manner that the flow rate adjusting mechanism blocks the passage of the
refrigerant upon activation of the compressor.
[0031] The refrigeration apparatus according to the fifth aspect activates the compressor
more reliably.
BRIEF DESCRIPTION OF THE DRAWINGS
[0032]
FIG. 1 is a general configuration diagram of a refrigeration apparatus according to
an embodiment of the present invention.
FIG. 2 is a schematic block diagram of a schematic configuration of a controller and
components connected to the controller.
FIG. 3 is a flowchart of exemplary processing to be performed by the controller in
performing normal control and hot gas bypass suppression control on an oil return
valve.
FIG. 4 is a general configuration diagram of a refrigeration apparatus including a
refrigerant circuit according to Modification A.
FIG. 5 is a general configuration diagram of a refrigeration apparatus including a
refrigerant circuit according to Modification B.
FIG. 6 is a general configuration diagram of a refrigeration apparatus including a
refrigerant circuit according to Modification C.
DESCRIPTION OF EMBODIMENTS
[0033] A refrigeration apparatus 100 according to an embodiment of the present invention
will be described below with reference to the drawings. It should be noted that the
following embodiments are merely specific examples of the present invention, do not
intend to limit the technical scope of the present invention, and may be appropriately
modified without departing from the gist of the present invention.
(1) Refrigeration Apparatus 100
[0034] FIG. 1 is a schematic configuration diagram of a refrigeration apparatus 100 according
to an embodiment of the present invention. The refrigeration apparatus 100 employs
a vapor compression refrigeration cycle to cool a usage-side space such as the interior
of a cold storage warehouse or the interior of a showcase in a store.
[0035] The refrigeration apparatus 100 mainly includes: a heat source unit 2; a plurality
of (two in this embodiment) usage units, that is, a first usage unit 50 and a second
usage unit 60; a liquid-side-refrigerant connection pipe 6 and a gas-side-refrigerant
connection pipe 7 each connecting the heat source unit 2 to the first usage unit 50
and the second usage unit 60; a plurality of remote controllers, that is, a first
remote controller 50a and a second remote controller 60a each serving as an input
device and a display device; and a controller 70 configured to control operation of
the refrigeration apparatus 100.
[0036] In the refrigeration apparatus 100, the heat source unit 2 as well as the first usage
unit 50 and the second usage unit 60 connected to the heat source unit 2 in parallel
via the liquid-side-refrigerant connection pipe 6 and the gas-side-refrigerant connection
pipe 7 constitute a refrigerant circuit 10. The refrigeration apparatus 100 performs
a refrigeration cycle to compress, cool or condense, decompress, heat or evaporate,
and then compress again a sealed-in refrigerant in the refrigerant circuit 10. In
this embodiment, the refrigerant circuit 10 is filled with R32 as a refrigerant for
a vapor compression refrigeration cycle; however, the refrigerant is not limited to
R32.
(1-1) Heat Source Unit 2
[0037] The heat source unit 2, to which the first usage unit 50 and the second usage unit
60 are connected in parallel via the liquid-side-refrigerant connection pipe 6 and
the gas-side-refrigerant connection pipe 7, constitutes a part of the refrigerant
circuit 10. The heat source unit 2 mainly includes a compressor 21, an oil separator
23, a four-way switching valve 24, a heat source-side heat exchanger 25, a heat source-side
fan 45, a receiver 27, a subcooler 31, a heat source-side expansion valve 28, an injection
pipe 30, a subcooling expansion valve 32, an injection valve 33, an oil return pipe
38, an oil return valve 39, a first branch pipe 34, a second branch pipe 36, a liquid-side
shutoff valve 48, and a gas-side shutoff valve 49.
[0038] The heat source unit 2 also includes a discharge-side pipe 41, a suction-side pipe
42, a first heat source liquid-side pipe 43, and a second heat source liquid-side
pipe 44. The discharge-side pipe 41 connects a discharge side of the compressor 21
to one of connection ports of the four-way switching valve 24, and the oil separator
23 is disposed at a middle of the discharge-side pipe 41. The suction-side pipe 42
connects a suction side of the compressor 21 to one of the connection ports of the
four-way switching valve 24. The first heat source liquid-side pipe 43 connects a
liquid side of the heat source-side heat exchanger 25 to the receiver 27. The second
heat source liquid-side pipe 44 connects the liquid-side shutoff valve 48 to an end
of the receiver 27, the end being opposite to an end connected to the heat source-side
heat exchanger 25.
[0039] The compressor 21 is a device configured to change by compression a low-pressure
refrigerant to a high-pressure refrigerant in the refrigeration cycle. The compressor
21 according to this embodiment includes a first compressor 21a, a second compressor
21b, and a third compressor 21c that are connected in parallel; however, the configuration
of the compressor 21 is not limited thereto. In this embodiment, each of the first
compressor 21a, the second compressor 21b, and the third compressor 21c is a fully
hermetic high pressure dome-type scroll compressor. The first compressor 21a is a
variable displacement compressor whose number of rotations is variable. The first
compressor 21a includes an inverter. Each of the second compressor 21b and the third
compressor 21c is a fixed displacement compressor whose number of rotations is fixed.
Each of the second compressor 21b and the third compressor 21c does not include an
inverter.
[0040] The first compressor 21a, the second compressor 21b, and the third compressor 21c
have suction sides to which individual suction pipes are respectively connected. The
individual suction pipes are merged into one at their most upstream sides. The suction-side
pipe 42 connects the most upstream-side merged portion of the individual suction pipes
to the four-way switching valve 24.
[0041] The first compressor 21a, the second compressor 21b, and the third compressor 21c
also have discharge sides to which individual discharge pipes are respectively connected.
The individual discharge pipes are merged into one at their most downstream sides.
The discharge-side pipe 41 connects the most downstream-side merged portion of the
individual discharge pipes to the four-way switching valve 24. A check valve 22a is
disposed on the discharge side of the first compressor 21a to permit only a discharge
flow. Likewise, a check valve 22b is disposed on the discharge side of the second
compressor 21b to permit only a discharge flow, and a check valve 22c is disposed
on the discharge side of the third compressor 21c to permit only a discharge flow.
[0042] The oil separator 23 is a container configured to mainly separate a refrigerating
machine oil from the refrigerant discharged from the compressor 21, and is disposed
at a middle of the discharge-side pipe 41. The oil separator 23 allows a collective
inflow of fluids (including the refrigerant and the refrigerating machine oil) discharged
from the plurality of compressors, that is, the first compressor 21a, the second compressor
21b, and the third compressor 21c constituting the compressor 21, and mainly separates
the refrigerating machine oil (into which a gas refrigerant is mixed to some extent
depending on an operating condition) from the fluid. For this reason, the oil separator
23 according to this embodiment is larger in capacity than, for example, oil separators
to be respectively disposed on the discharge sides of the first compressor 21a, second
compressor 21b, and third compressor 21c in one-to-one correspondence.
[0043] The oil return pipe 38 extends from and branches off the oil separator 23 disposed
at the middle of the discharge-side pipe 41. The oil return pipe 38 has a second end
that is connected to a middle of the injection pipe 30 (to be described later) at
a position between the subcooler 31 and first, second, and third injection shunt pipes
33x, 33y, and 33z. The oil return valve 39 is disposed at a middle of the oil return
pipe 38. The oil return valve 39 includes an electronic expansion valve whose valve
opening degree is controllable.
[0044] The four-way switching valve 24 is connected to a downstream-side end of the discharge-side
pipe 41. The four-way switching valve 24 switches a connection state, thereby switching
between a cooling operation state in which the discharge side of the compressor 21
is connected to the heat source-side heat exchanger 25 and the gas-side shutoff valve
49 is connected to the suction side of the compressor 21, and a heating operation
state in which the discharge side of the compressor 21 is connected to the gas-side
shutoff valve 49 and the heat source-side heat exchanger 25 is connected to the suction
side of the compressor 21.
[0045] The heat source-side heat exchanger 25 functions as a radiator for the high-pressure
refrigerant in the refrigeration cycle, and also functions as an evaporator for the
low-pressure refrigerant in the refrigeration cycle. The heat source-side heat exchanger
25 has a first end connected to a refrigerant pipe extending from the four-way switching
valve 24, and a second end connected to the first heat source liquid-side pipe 43.
[0046] The heat source-side fan 45 sucks outside air (heat source-side air) into the heat
source unit 2, causes the heat source-side air to exchange heat with the refrigerant
in the heat source-side heat exchanger 25, and then forms an air flow for discharging
the heat source-side air. The heat source-side fan 45 is driven to rotate by a heat
source-side fan motor M45. The heat source-side fan 45 has an airflow volume controlled
by adjusting the number of rotations of the heat source-side fan motor M45.
[0047] A first heat source liquid-side check valve 26 is disposed at a middle of the first
heat source liquid-side pipe 43. The first heat source liquid-side check valve 26
permits only a flow of the refrigerant from the heat source-side heat exchanger 25
toward the receiver 27.
[0048] The receiver 27 is a container temporarily stores therein the refrigerant. The receiver
27 is disposed on the first heat source liquid-side pipe 43 on a side opposite to
the heat source-side heat exchanger 25. The first heat source liquid-side pipe 43
is connected to an upper gas-phase portion of the receiver 27.
[0049] The heat source-side expansion valve 28 is an electric expansion valve whose valve
opening degree is controllable. The heat source-side expansion valve 28 is disposed
on the second heat source liquid-side pipe 44. More specifically, the heat source-side
expansion valve 28 is disposed downstream of the subcooler 31.
[0050] The subcooler 31 is a heat exchanger for further cooling the refrigerant temporarily
stored in the receiver 27 before the refrigerant is supplied to the first and second
usage units 50 and 60. The subcooler 31 is disposed on the second heat source liquid-side
pipe 44 at a position between the receiver 27 and the heat source-side expansion valve
28.
[0051] The injection pipe 30 extends from the second heat source liquid-side pipe 44 so
as to branch off a portion between the subcooler 31 and the heat source-side expansion
valve 28. The injection pipe 30 is connected to a middle of a compression process
in the compressor 21.
[0052] The subcooling expansion valve 32 is an electric expansion valve whose valve opening
degree is controllable. The subcooling expansion valve 32 is disposed upstream of
the subcooler 31 at a middle of the injection pipe 30. The subcooler 31 causes the
refrigerant that flows out of the receiver 27 and flows through the second heat source
liquid-side pipe 44 to exchange heat with the refrigerant that flows through the injection
pipe 30 and is decompressed by the subcooling expansion valve 32. The refrigerant
flowing through the second heat source liquid-side pipe 44 is thus subcooled, and
then flows toward the heat source-side expansion valve 28. In the injection pipe 30,
the refrigerant passes through the subcooler 31, and then flows toward the downstream
side of the injection pipe 30.
[0053] In the injection pipe 30, a portion downstream of a merged portion with the oil return
pipe 38 (i.e., a portion closer to the compressor 21 than the merged portion is) extends
to the compressor 21 via the first, second, and third injection shunt pipes 33x, 33y,
and 33z. Specifically, the portion downstream of the merged portion with the oil return
pipe 38 (i.e., the portion closer to the compressor 21 than the merged portion is)
in the injection pipe 30 is separated into the first injection shunt pipe 33x through
which the refrigerant flows into the middle of the compression process in the first
compressor 21a, the second injection shunt pipe 33y through which the refrigerant
flows into the middle of the compression process in the second compressor 21b, and
the third injection shunt pipe 33z through which the refrigerant flows into the middle
of the compression process in the third compressor 21c.
[0054] The injection valve 33 is an electric expansion valve whose valve opening degree
is controllable. The injection valve 33 includes first, second, and third injection
valves 33a, 33b, and 33c respectively disposed at middles of the first, second, and
third injection shunt pipes 33x, 33y, and 33z of the injection pipe 30. Specifically,
the first injection valve 33a is disposed at the middle of the first injection shunt
pipe 33x, the second injection valve 33b is disposed at the middle of the second injection
shunt pipe 33y, and the third injection valve 33c is disposed at the middle of the
third injection shunt pipe 33z.
[0055] A second heat source liquid-side check valve 29 is disposed on the second heat source
liquid-side pipe 44 at a position between the heat source-side expansion valve 28
and the liquid-side shutoff valve 48. The second heat source liquid-side check valve
29 permits only a flow of the refrigerant from the heat source-side expansion valve
28 toward the liquid-side shutoff valve 48.
[0056] The first branch pipe 34 is a refrigerant pipe that branches off a portion between
the second heat source liquid-side check valve 29 and the liquid-side shutoff valve
48 at a middle of the second heat source liquid-side pipe 44 and merges with a portion
between the first heat source liquid-side check valve 26 and the receiver 27 at a
middle of the first heat source liquid-side pipe 43. A first branch check valve 35
is disposed at a middle of the first branch pipe 34. The first branch check valve
35 permits only a flow of the refrigerant from the second heat source liquid-side
pipe 44 toward the first heat source liquid-side pipe 43.
[0057] The second branch pipe 36 is a refrigerant pipe that branches off a portion between
the heat source-side expansion valve 28 and the second heat source liquid-side check
valve 29 at a middle of the second heat source liquid-side pipe 44 and merges with
a portion between the heat source-side heat exchanger 25 and the first heat source
liquid-side check valve 26 at a middle of the first heat source liquid-side pipe 43.
A second branch check valve 37 is disposed at a middle of the second branch pipe 36.
The second branch check valve 37 permits only a flow of the refrigerant from the second
heat source liquid-side pipe 44 toward the first heat source liquid-side pipe 43.
[0058] The liquid-side shutoff valve 48 is a manual valve disposed at a joint between the
second heat source liquid-side pipe 44 and the liquid-side-refrigerant connection
pipe 6.
[0059] The gas-side shutoff valve 49 is a manual valve disposed at a joint between a pipe
extending from the four-way switching valve 24 and the gas-side-refrigerant connection
pipe 7.
[0060] The heat source unit 2 includes various sensors. Specifically, a low-pressure sensor
40a is disposed on the suction-side pipe 42. The low-pressure sensor 40a is configured
to detect a suction pressure that is a pressure of the refrigerant at the suction
side of the compressor 21. A high-pressure sensor 40c is disposed at a middle of the
individual discharge pipe for the first compressor 21a. The high-pressure sensor 40c
is configured to detect a discharge pressure that is a pressure of the refrigerant
at the discharge side of the compressor 21. An intermediate-pressure sensor 40b is
disposed between a merged portion of the injection pipe 30 with the oil return pipe
38 and the subcooler 31 at a middle of the injection pipe 30. The intermediate-pressure
sensor 40b is configured to detect an intermediate pressure in the refrigeration cycle.
A heat source-side air temperature sensor 46 is disposed around the heat source-side
heat exchanger 25 or the heat source-side fan 45. The heat source-side air temperature
sensor 46 is configured to detect a temperature of heat source-side air to be sucked
into the heat source unit 2. A discharge temperature sensor 47 is disposed at a middle
of the discharge-side pipe 41. In this embodiment, the discharge temperature sensor
47 is disposed upstream of the oil separator 23 at a position where the discharge
refrigerants from the first compressor 21a, second compressor 21b, and third compressor
21c are merged. The discharge temperature sensor 47 is configured to detect a temperature
of the refrigerant discharged from the compressor 21.
[0061] The heat source unit 2 also includes a heat source unit control unit 20 configured
to control operations of the respective components constituting the heat source unit
2. The heat source unit control unit 20 includes a microcomputer including, for example,
a central processing unit (CPU) and a memory. The heat source unit control unit 20
is connected to usage unit control units 57 and 67 of each usage unit 50, 60 via communication
lines to exchange, for example, a control signal with the usage unit control units
57 and 67.
(1-2) First Usage Unit 50
[0062] The first usage unit 50 is connected to the heat source unit 2 via the liquid-side-refrigerant
connection pipe 6 and the gas-side-refrigerant connection pipe 7, and constitutes
a part of the refrigerant circuit 10.
[0063] The first usage unit 50 includes a first usage-side expansion valve 54 and a first
usage-side heat exchanger 52. The first usage unit 50 also includes: a first usage-side
liquid refrigerant pipe 59 connecting a liquid-side end of the first usage-side heat
exchanger 52 to the liquid-side-refrigerant connection pipe 6; and a first usage-side
gas refrigerant pipe 58 connecting a gas-side end of the first usage-side heat exchanger
52 to the gas-side-refrigerant connection pipe 7.
[0064] The first usage-side expansion valve 54 is an electric expansion valve whose valve
opening degree is controllable. The first usage-side expansion valve 54 is disposed
at a middle of the first usage-side liquid refrigerant pipe 59.
[0065] The first usage-side heat exchanger 52 functions as an evaporator for the low-pressure
refrigerant in a cooling operation in the refrigeration cycle to cool inside air (usage-side
air), and also functions as a radiator for the refrigerant in a heating operation
such as a defrosting operation.
[0066] The first usage unit 50 includes a first usage-side fan 53 for sucking usage-side
air into the first usage unit 50, causing the usage-side air to exchange heat with
the refrigerant in the first usage-side heat exchanger 52, and then supplying the
usage-side air to the usage-side space. The first usage-side fan 53 is configured
to supply to the first usage-side heat exchanger 52 the usage-side air for heating
the refrigerant flowing through the first usage-side heat exchanger 52. The first
usage-side fan 53 is driven to rotate by a first usage-side fan motor M53.
[0067] The first usage unit 50 also includes a first usage unit control unit 57 configured
to control operations of the respective components constituting the first usage unit
50. The first usage unit control unit 57 includes a microcomputer including, for example,
a CPU and a memory. The first usage unit control unit 57 is connected to the heat
source unit control unit 20 via the communication line to exchange, for example, a
control signal with the heat source unit control unit 20.
(1-3) Second Usage Unit 60
[0068] The second usage unit 60 is similar in configuration to the first usage unit 50.
The second usage unit 60 is also connected to the heat source unit 2 via the liquid-side-refrigerant
connection pipe 6 and the gas-side-refrigerant connection pipe 7, and constitutes
a part of the refrigerant circuit 10. The second usage unit 60 and the first usage
unit 50 are connected in parallel.
[0069] The second usage unit 60 includes a second usage-side expansion valve 64 and a second
usage-side heat exchanger 62. The second usage unit 60 also includes: a second usage-side
liquid refrigerant pipe 69 connecting a liquid-side end of the second usage-side heat
exchanger 62 to the liquid-side-refrigerant connection pipe 6; and a second usage-side
gas refrigerant pipe 68 connecting a gas-side end of the second usage-side heat exchanger
62 to the gas-side-refrigerant connection pipe 7.
[0070] The second usage-side expansion valve 64 is an electric expansion valve whose valve
opening degree is controllable. The second usage-side expansion valve 64 is disposed
at a middle of the second usage-side liquid refrigerant pipe 69.
[0071] The second usage-side heat exchanger 62 functions as an evaporator for the low-pressure
refrigerant in the cooling operation in the refrigeration cycle to cool inside air
(usage-side air), and also functions as a radiator for the refrigerant in the heating
operation such as the defrosting operation.
[0072] As in the first usage unit 50, the second usage unit 60 also includes a second usage-side
fan 63 to be driven to rotate by a second usage-side fan motor M63.
[0073] The second usage unit 60 also includes a second usage unit control unit 67 configured
to control operations of the respective components constituting the second usage unit
60. The second usage unit control unit 67 includes a microcomputer including, for
example, a CPU and a memory. The second usage unit control unit 67 is connected to
the heat source unit control unit 20 via the communication line to exchange, for example,
a control signal with the heat source unit control unit 20.
(1-4) First Remote Controller 50a, Second Remote Controller 60a
[0074] The first remote controller 50a is an input device that causes a user of the first
usage unit 50 to input various instructions for switching an operating state of the
refrigeration apparatus 100. The first remote controller 50a also functions as a display
device for displaying the operating state of the refrigeration apparatus 100 and predetermined
notification information. The first remote controller 50a is connected to the first
usage unit control unit 57 via a communication line to exchange signals with the first
usage unit control unit 57.
[0075] As in the first remote controller 50a, the second remote controller 60a is an input
device that causes a user of the second usage unit 60 to input various instructions
for switching an operating state of the refrigeration apparatus 100, and a display
device for displaying the operating state of the refrigeration apparatus 100 and predetermined
notification information. The second remote controller 60a is connected to the second
usage unit control unit 67 via a communication line to exchange signals with the second
usage unit control unit 67.
(2) Details of Controller 70
[0076] In the refrigeration apparatus 100, the heat source unit control unit 20, the first
usage unit control unit 57, and the second usage unit control unit 67 are connected
via the communication lines to constitute the controller 70 for controlling operation
of the refrigeration apparatus 100.
[0077] FIG. 2 is a schematic block diagram of a schematic configuration of the controller
70 and the components connected to the controller 70.
[0078] The controller 70 has a plurality of control modes, and controls the operation of
the refrigeration apparatus 100 in accordance with a control mode in which the controller
70 is to be placed. Examples of the control modes of the controller 70 include: a
cooling operating mode in which the controller 70 is placed in a normal situation;
and a heating operating mode in which the controller 70 is placed in reverse cycle
defrosting. The controller 70 selectively performs normal control on the oil return
valve 39 and hot gas bypass suppression control on the oil return valve 39 in both
the cooling operating mode and the heating operating mode. The controller 70 performs
the normal control on the oil return valve 39 to return an appropriate amount of refrigerating
machine oil to the compressor 21 in accordance with operating conditions of the refrigeration
cycle. The controller 70 performs the hot gas bypass suppression control on the oil
return valve 39 to suppress passage of a large amount of hot gas through the oil return
valve 39 although the oil return valve 39 cannot allow passage of a satisfactory amount
of refrigerating machine oil.
[0079] The controller 70 is electrically connected to the actuators (i.e., the compressor
21, the four-way switching valve 24, the heat source-side expansion valve 28, the
subcooling expansion valve 32, the injection valve 33, the oil return valve 39, and
the heat source-side fan 45 (the heat source-side fan motor M45)) and the various
sensors (i.e., the low-pressure sensor 40a, the intermediate-pressure sensor 40b,
the high-pressure sensor 40c, the heat source-side air temperature sensor 46, the
discharge temperature sensor 47, and the like) in the heat source unit 2. The controller
70 is also electrically connected to the actuators (i.e., the first usage-side fan
53 (the first usage-side fan motor M53) and the first usage-side expansion valve 54)
in the first usage unit 50. The controller 70 is also electrically connected to the
actuators (i.e., the second usage-side fan 63 (the second usage-side fan motor M63)
and the second usage-side expansion valve 64) in the second usage unit 60. The controller
70 is also electrically connected to the first remote controller 50a and the second
remote controller 60a.
[0080] The controller 70 mainly includes a storage unit 71, a communication unit 72, a mode
control unit 73, an actuator control unit 74, and a display control unit 75. These
units in the controller 70 are implemented in such a manner that the components in
the heat source unit control unit 20 and/or each usage unit control unit 57, 67 integrally
function.
(2-1) Storage Unit 71
[0081] The storage unit 71 includes, for example, a read only memory (ROM), a random access
memory (RAM), and a flash memory. The storage unit 71 has a volatile storage region
and a nonvolatile storage region. The storage unit 71 stores therein a control program
that defines processing to be performed by each unit of the controller 70. Also in
the storage unit 71, the respective units of the controller 70 appropriately store
predetermined information (e.g., values detected by the respective sensors, commands
input to the first remote controller 50a, commands input to the second remote controller
60a) in a predetermined storage region.
(2-2) Communication Unit 72
[0082] The communication unit 72 is a functional unit that plays a role as a communication
interface for exchanging signals with the respective components connected to the controller
70. The communication unit 72 receives a request from the actuator control unit 74,
and transmits a predetermined signal to a designated one of the actuators. The communication
unit 72 also receives signals from the various sensors, the first remote controller
50a, and the second remote controller 60a, and stores the received signals in the
predetermined storage region of the storage unit 71.
(2-3) Mode Control Unit 73
[0083] The mode control unit 73 is a functional unit that switches a control mode, for example.
The mode control unit 73 places the controller 70 in the cooling operating mode when
the refrigeration apparatus 100 that does not satisfy a predetermined defrosting condition
is operated. The predetermined defrosting condition concerns frost forming on the
first and second usage-side heat exchangers 52 and 62. When the predetermined defrosting
condition is satisfied in the cooling operating mode, the mode control unit 73 switches
the control mode to the heating operating mode. The mode control unit 73 basically
performs the normal control on the oil return valve 39 in both the cooling operating
mode and the heating operating mode. When a rise speed of a temperature of the refrigerant
discharged from the compressor 21 (i.e., a temperature detected by the discharge temperature
sensor 47) is more than a predetermined rise speed, the mode control unit 73 switches
the normal control for the oil return valve 39 to the hot gas bypass suppression control
for the oil return valve 39. (2-4) Actuator Control Unit 74
[0084] The actuator control unit 74 controls, based on the control program, the operations
of the respective actuators (e.g., the compressor 21) in the refrigeration apparatus
100, in accordance with a situation.
[0085] In the cooling operating mode, the actuator control unit 74 connects the discharge
side of the compressor 21 to the heat source-side heat exchanger 25 via the four-way
switching valve 24, and also connects the suction side of the compressor 21 to the
gas-side shutoff valve 49 via the four-way switching valve 24. In this connection
state, the actuator control unit 74 brings the heat source-side expansion valve 28
into a fully open state. In addition, the actuator control unit 74 controls, for example,
the number of rotations of the compressor 21, the number of rotations of the heat
source-side fan 45, the opening degree of the subcooling expansion valve 32, the opening
degree of the oil return valve 39, the valve opening degrees of the first, second,
and third injection valves 33a, 33b, and 33c, the opening degrees of the usage-side
expansion valves 54 and 64, and the numbers of rotations of the usage-side fans 53
and 63 in real time, in accordance with, for example, set temperatures and values
detected by the various sensors. In the cooling operating mode, each of the first,
second, and third injection valves 33a, 33b, and 33c is brought into a state other
than the fully closed state.
[0086] In the heating operating mode, the actuator control unit 74 connects the discharge
side of the compressor 21 to the gas-side shutoff valve 49 via the four-way switching
valve 24, and also connects the suction side of the compressor 21 to the heat source-side
heat exchanger 25 via the four-way switching valve 24. In this connection state, the
actuator control unit 74 brings the subcooling expansion valve 32 into a fully closed
state, brings the usage-side expansion valves 54 and 64 into the fully open state,
and stops the usage-side fans 53 and 63. In addition, the actuator control unit 74
controls, for example, the number of rotations of the compressor 21, the number of
rotations of the heat source-side fan 45, the opening degree of the heat source-side
expansion valve 28, the opening degree of the oil return valve 39, and the valve opening
degrees of the first, second, and third injection valves 33a, 33b, and 33c in real
time, in accordance with, for example, values detected by the various sensors. Also
in the heating operating mode, each of the first, second, and third injection valves
33a, 33b, and 33c is brought into a state other than the fully closed state.
[0087] In the cooling operating mode and the heating operating mode, the controller 70 selectively
performs the normal control on the oil return valve 39 and the hot gas bypass suppression
control on the oil return valve 39.
-- Normal control for oil return valve 39 --
[0088] In the normal control for the oil return valve 39 (i.e., control other than the hot
gas bypass suppression control), the actuator control unit 74 controls the opening
degree of the oil return valve 39 such that a passage and circulation amount becomes
equal to an amount of oil loss in the compressor 21. In other words, the actuator
control unit 74 controls the valve opening degree of the oil return valve 39 such
that "an amount of oil loss in the compressor 21" becomes equal to "a passage and
circulation amount in the oil return valve 39".
[0089] A relation of "an amount of oil loss in a compressor" = "a circulation amount of
refrigerant in the compressor" × "a rate of oil loss in the compressor" is satisfied.
In a case where the plurality of compressors, that is, the first compressor 21a, the
second compressor 21b, and the third compressor 21c, constituting the compressor 21
are respectively driven, "the amount of oil loss in the compressor" is calculated
from "the circulation amount of refrigerant in the compressor" and "the rate of oil
loss in the compressor" as to each of the compressors driven. By summing the results,
"the amount of oil loss in the compressor 21" is calculated.
[0090] For example, "the circulation amount in the compressor" may be calculated based on,
but not limited to, a piston displacement of the compressor, a driving frequency of
the compressor, and a suction refrigerant density of the compressor. Alternatively,
"the circulation amount in the compressor" may be calculated by dividing electric
power input to the compressor 21 by a difference in enthalpy between the outlet and
inlet of the compressor 21.
[0091] In addition, "the rate of oil loss in the compressor" may be calculated for each
compressor driven, based on the driving frequency of the compressor, a high pressure,
an intermediate pressure, and a low pressure in a refrigeration cycle, and the degree
of superheating of a refrigerant to be sucked by the compressor if necessary.
[0092] In addition, "the passage and circulation amount in the oil return valve 39" may
be calculated using the valve opening degree of the oil return valve 39, the difference
in pressure between the refrigerant before flowing into the oil return valve 39 and
the refrigerant that has flown out of the oil return valve 39 (i.e., the high pressure
- the intermediate pressure), and predetermined relation value table data stored in
the storage unit 71 in advance. The predetermined relation value table data is obtained
in advance, based on such a relation that a passage and circulation amount increases
as the valve opening degree of the oil return valve 39 is larger and also increases
as the difference in pressure between the refrigerant before flowing into the oil
return valve 39 and the refrigerant that has flown out of the oil return valve 39
is larger.
[0093] As described above, the valve opening degree of the oil return valve 39 is substantially
controlled in accordance with "the amount of oil loss in the compressor 21" and "the
difference in pressure between the refrigerant before flowing into the oil return
valve 39 and the refrigerant that has flown out of the oil return valve 39 (i.e.,
the high pressure - the intermediate pressure)".
-- Hot gas bypass suppression control for oil return valve 39 --
[0094] In the hot gas bypass suppression control for the oil return valve 39, the actuator
control unit 74 lowers the opening degree of the oil return valve 39 below the valve
opening degree of the oil return valve 39 subjected to the normal control in the preceding
cooling operating mode or heating operating mode. For example, the actuator control
unit 74 may lower the opening degree of the oil return valve 39 to a half of the valve
opening degree of the oil return valve 39 subjected to the normal control in the preceding
cooling operating mode or heating operating mode. Alternatively, the actuator control
unit 74 may lower the opening degree of the oil return valve 39 so as to bring the
oil return valve 39 into the fully closed state. However, the degree of lowering the
opening degree of the oil return valve 39 is not limited thereto. Lowering the valve
opening degree of the oil return valve 39 enables suppression of degradation in performance
to be caused because hot gas is returned in large amounts to the suction side of the
compressor 21 via the oil return pipe 38.
[0095] In lowering the opening degree of the oil return valve 39, the valve opening degrees
of the first, second, and third injection valves 33a, 33b, and 33c are not particularly
changed and are maintained at the same control state.
(2-5) Display Control Unit 75
[0096] The display control unit 75 is a functional unit that controls operations of the
first remote controller 50a and second remote controller 60a each serving as the display
device.
[0097] The display control unit 75 causes each of the first remote controller 50a and the
second remote controller 60a to output predetermined information in order that information
on an operating state or situation is displayed for an administrator.
[0098] For example, the display control unit 75 causes each of the first remote controller
50a and the second remote controller 60a to display thereon various kinds of information,
such as set temperatures, during the cooling operation.
[0099] In the hot gas bypass suppression control, the display control unit 75 causes each
of the first remote controller 50a and the second remote controller 60a to display
thereon information indicating that the refrigeration apparatus 100 is in the hot
gas bypass suppression control mode.
(3) Flow of Refrigerant in Cooling Operating Mode
[0100] Next, a description will be given of the flow of the refrigerant in the refrigerant
circuit 10 in the cooling operating mode.
[0101] During the operation, the refrigeration apparatus 100 performs the cooling operation
(a refrigeration cycle operation) causing the refrigerant in the refrigerant circuit
10 to mainly circulate through the compressor 21, the heat source-side heat exchanger
25, the receiver 27, the subcooler 31, the heat source-side expansion valve 28, the
usage-side expansion valves 54, 64, and the usage-side heat exchangers 52, 62 in this
order.
[0102] When the cooling operation is started, the refrigerant is sucked into and compressed
by the compressor 21, and then is discharged from the compressor 21, in the refrigerant
circuit 10. In the cooling operation, the low pressure in the refrigeration cycle
corresponds to the suction pressure to be detected by the low-pressure sensor 40a,
the high pressure in the refrigeration cycle corresponds to the discharge pressure
to be detected by the high-pressure sensor 40c, and the intermediate pressure in the
refrigeration cycle corresponds to the discharge pressure to be detected by the intermediate-pressure
sensor 40b.
[0103] The compressor 21 is subjected to capacity control according to a cooling load to
be required for each of the first usage unit 50 and the second usage unit 60. Specifically,
the operating frequency of the compressor 21 is controlled such that the suction pressure
takes a target value set in accordance with the cooling load to be required for each
of the first usage unit 50 and the second usage unit 60.
[0104] The gas refrigerant discharged from the compressor 21 flows into the heat source-side
heat exchanger 25 through the gas-side end of the heat source-side heat exchanger
25, via the discharge-side pipe 41. The oil separator 23 disposed at the middle of
the discharge-side pipe 41 separates the refrigerating machine oil from the refrigerant
discharged from the compressor 21, and guides the refrigerating machine oil to the
oil return pipe 38. In the cooling operating mode, the oil return valve 39 is subjected
to the normal control or the hot gas bypass suppression control.
[0105] When the gas refrigerant flows into the heat source-side heat exchanger 25 through
the gas-side end of the heat source-side heat exchanger 25, the heat source-side heat
exchanger 25 causes the gas refrigerant to radiate heat by heat exchange with the
heat source-side air supplied by the heat source-side fan 45, and then condenses the
gas refrigerant to turn the gas refrigerant into the liquid refrigerant. The liquid
refrigerant flows out of the heat source-side heat exchanger 25 through the liquid-side
end of the heat source-side heat exchanger 25.
[0106] When the liquid refrigerant flows out of the heat source-side heat exchanger 25 through
the liquid-side end of the heat source-side heat exchanger 25, then the liquid refrigerant
passes through the first heat source liquid-side pipe 43 and the first heat source
liquid-side check valve 26 without being shunted to the second branch pipe 36, and
flows into the receiver 27 through the inlet of the receiver 27. When the liquid refrigerant
flows into the receiver 27, the receiver 27 temporarily stores therein the liquid
refrigerant in a saturated state. Thereafter, the liquid refrigerant flows out of
the receiver 27 through the outlet of the receiver 27.
[0107] When the liquid refrigerant flows out of the receiver 27 through the outlet of the
receiver 27, then the liquid refrigerant flows into the subcooler 31 through the second
heat source liquid-side pipe 44.
[0108] When the liquid refrigerant flows into the subcooler 31, the subcooler 31 further
cools the liquid refrigerant by heat exchange with the refrigerant flowing through
the injection pipe 30, thereby bringing the liquid refrigerant into a subcooled state.
The resultant liquid refrigerant flows out of the subcooler 31 through the outlet,
coupled to the heat source-side expansion valve 28, of the subcooler 31. The controller
70 controls the valve opening degree of the subcooling expansion valve 32 such that
the refrigerant flowing from the subcooler 31 toward the heat source-side expansion
valve 28 has a predetermined positive degree of subcooling and a value detected by
the intermediate-pressure sensor satisfies a predetermined intermediate pressure condition.
[0109] When the liquid refrigerant flows out of the subcooler 31 through the outlet, coupled
to the heat source-side expansion valve 28, of the subcooler 31, then the liquid refrigerant
flows into the heat source-side expansion valve 28 via a portion, between the subcooler
31 and the heat source-side expansion valve 28, of the second heat source liquid-side
pipe 44. At this time, the liquid refrigerant, which has flown out of the subcooler
31 through the outlet, coupled to the heat source-side expansion valve 28, of the
subcooler 31, partly flows toward the injection pipe 30 branching off the portion,
between the subcooler 31 and the heat source-side expansion valve 28, of the second
heat source liquid-side pipe 44.
[0110] The refrigerant flowing through the injection pipe 30 is decompressed by the subcooling
expansion valve 32 to have the intermediate pressure in the refrigeration cycle. The
refrigerant decompressed by the subcooling expansion valve 32 flows through the injection
pipe 30, and then flows into the subcooler 31 through the inlet, connected to the
injection pipe 30, of the subcooler 31. When the refrigerant flows into the subcooler
31 through the inlet, connected to the injection pipe 30, of the subcooler 31, the
subcooler 31 causes the refrigerant to exchange heat with the refrigerant flowing
through the second heat source liquid-side pipe 44, and then heats the refrigerant
to turn the refrigerant into the gas refrigerant. The refrigerant heated by the subcooler
31 flows toward the downstream side of the injection pipe 30, and is mixed with the
refrigerating machine oil from the oil return pipe 38. The resultant refrigerant is
then shunted to each of the first, second, and third injection shunt pipes 33x, 33y,
and 33z, and the shunted refrigerants respectively flow into the middles of the compression
processes in the first, second, and third compressors 21a, 21b, and 21c. The amounts
of the refrigerants flowing through the first, second, and third injection shunt pipes
33x, 33y, and 33z are respectively adjusted by the valve opening degrees of the first,
second, and third injection valves 33a, 33b, and 33c.
[0111] The heat source-side expansion valve 28 is brought into the fully open state in the
cooling operating mode. The liquid refrigerant, which has flown into the heat source-side
expansion valve 28 via the second heat source liquid-side pipe 44, therefore passes
through the heat source-side expansion valve 28 without being decompressed, and flows
into each of the first usage unit 50 and the second usage unit 60 that are currently
operated, via the liquid-side shutoff valve 48 and the liquid-side-refrigerant connection
pipe 6.
[0112] When the refrigerant flows into the first usage unit 50, then the refrigerant flows
into the first usage-side expansion valve 54 via a part of the first usage-side liquid
refrigerant pipe 59. When the refrigerant flows into the first usage-side expansion
valve 54, then the refrigerant is decompressed by the first usage-side expansion valve
54 to have the low pressure in the refrigeration cycle. Thereafter, the refrigerant
flows into the first usage-side heat exchanger 52 through the liquid-side end of the
first usage-side heat exchanger 52 via the first usage-side liquid refrigerant pipe
59. When the refrigerant flows into the first usage-side heat exchanger 52 through
the liquid-side end of the first usage-side heat exchanger 52, the first usage-side
heat exchanger 52 evaporates the refrigerant by heat exchange with the usage-side
air supplied by the first usage-side fan 53, thereby turning the refrigerant into
the gas refrigerant. The resultant gas refrigerant flows out of the first usage-side
heat exchanger 52 through the gas-side end of the first usage-side heat exchanger
52. When the gas refrigerant flows out of the first usage-side heat exchanger 52 through
the gas-side end of the first usage-side heat exchanger 52, then the gas refrigerant
flows to the gas-side-refrigerant connection pipe 7 via the first usage-side gas refrigerant
pipe 58.
[0113] As in the first usage unit 50, when the refrigerant flows into the second usage unit
60, then the refrigerant flows into the second usage-side expansion valve 64 via a
part of the second usage-side liquid refrigerant pipe 69. When the refrigerant flows
into the second usage-side expansion valve 64, then the refrigerant is decompressed
by the second usage-side expansion valve 64 to have the low pressure in the refrigeration
cycle. Thereafter, the refrigerant flows into the second usage-side heat exchanger
62 through the liquid-side end of the second usage-side heat exchanger 62 via the
second usage-side liquid refrigerant pipe 69. When the refrigerant flows into the
second usage-side heat exchanger 62 through the liquid-side end of the second usage-side
heat exchanger 62, the second usage-side heat exchanger 62 evaporates the refrigerant
by heat exchange with the usage-side air supplied by the second usage-side fan 63,
thereby turning the refrigerant into the gas refrigerant. The resultant gas refrigerant
flows out of the second usage-side heat exchanger 62 through the gas-side end of the
second usage-side heat exchanger 62. When the gas refrigerant flows out of the second
usage-side heat exchanger 62 through the gas-side end of the second usage-side heat
exchanger 62, then the gas refrigerant flows to the gas-side-refrigerant connection
pipe 7 via the second usage-side gas refrigerant pipe 68.
[0114] The refrigerant, which has flown out of the first usage unit 50, and the refrigerant,
which has flown out of the second usage unit 60, merge with each other at the gas-side-refrigerant
connection pipe 7, and then are sucked into the compressor 21 again, via the gas-side
shutoff valve 49, the four-way switching valve 24, and the suction-side pipe 42.
(4) Flow of Refrigerant in Heating Operating Mode
[0115] Next, a description will be given of the flow of the refrigerant in the refrigerant
circuit 10 in the heating operating mode, which is performed, for example, for removing
frost from the usage-side heat exchangers 52 and 62.
[0116] The heating operation is started when the controller 70 determines that a predetermined
heating operation start condition is satisfied in the cooling operation (e.g., when
the cooling operation is performed for a predetermined time or when a temperature
of a heat exchanger to be subjected to defrosting is equal to or less than a predetermined
temperature).
[0117] During the heating operation, the refrigeration apparatus 100 performs the heating
operation (a refrigeration cycle operation) causing the refrigerant in the refrigerant
circuit 10 to mainly circulate through the compressor 21, the usage-side heat exchangers
52 and 62, the usage-side expansion valves 54 and 64, the receiver 27, the heat source-side
expansion valve 28, and the heat source-side heat exchanger 25 in this order.
[0118] When the heating operation is started, the refrigerant is sucked into and compressed
by the compressor 21, and then is discharged from the compressor 21, in the refrigerant
circuit 10.
[0119] The compressor 21 is controlled at, for example, the maximum frequency; however,
the control of the compressor 21 is not limited thereto.
[0120] The gas refrigerant discharged from the compressor 21 flows into each of the usage-side
heat exchangers 52 and 62 through each of the gas-side ends of the usage-side heat
exchangers 52 and 62, via the discharge-side pipe 41. As in the cooling operation,
the oil return valve 39 is subjected to the normal control or the hot gas bypass suppression
control.
[0121] When the gas refrigerants respectively flow into the usage-side heat exchangers 52
and 62 through the gas-side ends of the usage-side heat exchangers 52 and 62, then
the gas refrigerants condense by radiating heat and melt frost on the usage-side heat
exchangers 52 and 62. At this time, the usage-side fans 53 and 63 each come to a stop.
[0122] The refrigerants condensed by melting frost on the usage-side heat exchangers 52
and 62 respectively pass through the usage-side expansion valves 54 and 64 controlled
in the fully open state, and then flow into the heat source unit 2 through the liquid
side of the heat source unit 2 via the liquid-side-refrigerant connection pipe 6.
[0123] When the refrigerant passes through the liquid-side shutoff valve 48 of the heat
source unit 2, then the refrigerant passes through the first branch check valve 35
on the first branch pipe 34, and flows into the receiver 27. However, the refrigerant
does not flow toward the second heat source liquid-side pipe 44 since the second heat
source liquid-side check valve 29 is disposed on the second heat source liquid-side
pipe 44. When the refrigerant flows into the receiver 27, then the refrigerant flows
through the second heat source liquid-side pipe 44, and passes through the subcooler
31. Thereafter, the refrigerant is decompressed by the heat source-side expansion
valve 28 to have the low pressure in the refrigeration cycle, and then passes through
the second branch check valve 37 on the second branch pipe 36. In the heating operation,
since the subcooling expansion valve 32 is controlled in the fully closed state, the
refrigerant does not flow toward the upstream side of the injection pipe 30. Also
in the heating operation, since the opening degree of the oil return valve 39 is controlled,
the refrigerating machine oil passes through the oil return pipe 38, and then is supplied
to each of the first, second, and third compressors 21a, 21b, and 21c via the downstream
portion of the injection pipe 30.
[0124] When the refrigerant passes through the second branch check valve 37 on the second
branch pipe 36, then the refrigerant flows into the heat source-side heat exchanger
25 via the first heat source liquid-side pipe 43. When the refrigerant flows into
the heat source-side heat exchanger 25 through the liquid-side end of the heat source-side
heat exchanger 25, the heat source-side heat exchanger 25 evaporates the refrigerant
by heat exchange with the heat source-side air supplied by the heat source-side fan
45, thereby turning the refrigerant into the gas refrigerant. The gas refrigerant
flows out of the heat source-side heat exchanger 25 through the gas-side end of the
heat source-side heat exchanger 25.
[0125] When the gas refrigerant flows out of the heat source-side heat exchanger 25, then
the gas refrigerant is sucked into the compressor 21 again via the four-way switching
valve 24 and the suction-side pipe 42.
[0126] The heating operation terminates when the controller 70 determines that a predetermined
heating operation termination condition is satisfied from the start of the heating
operation (e.g., when a predetermined time is elapsed or when the temperature of the
heat exchanger to be subjected to defrosting is equal to or more than the predetermined
temperature). The normal cooling operation is then resumed.
(5) Processing by Controller 70 in Performing Normal Control and Hot Gas Bypass Suppression
Control on Oil Return Valve 39
[0127] With reference to a flowchart of FIG. 3, next, a description will be given of exemplary
processing to be performed by the controller 70 in performing the normal control and
the hot gas bypass suppression control on the oil return valve 39.
[0128] In both the cooling operating mode and the heating operating mode, the normal control
and the hot gas bypass suppression control are selectively performed on the oil return
valve 39. Therefore, the following description involves a case where the compressor
21 that is stopping is activated in, for example, the cooling operating mode.
[0129] In step S11, the controller 70 controls the valve opening degree of the oil return
valve 39 to temporarily bring the oil return valve 39 into the fully open state for
a predetermined time before activation of the compressor 21 for starting the cooling
operating mode from the state in which the compressor 21 stops. This configuration
enables equalization of the pressure on the discharge side of the compressor 21 and
the pressure on the side, to which the injection pipe 30 is connected, of the compressor
21, and also enables more reliable activation of the compressor 21.
[0130] In step S12, the controller 70 controls the valve opening degree of the oil return
valve 39 to bring the oil return valve 39 into the fully closed state. This configuration
easily brings about a difference in pressure between the refrigerant on the discharge
side of the compressor 21 and the refrigerant on the side, to which the injection
pipe 30 is connected, of the compressor 21 at the time when the compressor 21 is driven.
[0131] In step S13, the controller 70 activates the compressor 21, and increases the frequency
of the compressor 21. Since the oil return valve 39 is brought into the fully closed
state in step S11, the refrigerant discharged from the compressor 21 and the refrigerating
machine oil do not flow toward the joint to the injection pipe 30 in the compressor
21 via the oil return pipe 38. The difference in pressure is therefore secured with
ease.
[0132] In step S14, the controller 70 determines whether the frequency of the compressor
21 increases to exceed the predetermined frequency. When the frequency is more than
the predetermined frequency, the processing proceeds to step S15. When the frequency
is less than the predetermined frequency, the processing returns to step S13 in which
the controller 70 keeps the frequency increasing. When the frequency of the compressor
21 is more than the predetermined frequency, the controller 70 is maintained at the
cooling operating mode described above.
[0133] In step S15, the controller 70 performs the normal control on the oil return valve
39 in order to return an appropriate amount of refrigerating machine oil from the
oil separator 23 to the compressor 21 in accordance with an operating condition. Specifically,
as described above, the controller 70 controls the valve opening degree of the oil
return valve 39 such that "the amount of oil loss in the compressor 21" becomes equal
to "the passage and circulation amount in the oil return valve 39".
[0134] In step S16, the controller 70 determines whether a rise speed of the temperature
of the refrigerant discharged from the compressor 21 (i.e., the temperature detected
by the discharge temperature sensor 47) is more than the predetermined rise speed.
When the discharge refrigerant temperature rise speed at the compressor 21 is more
than the predetermined rise speed, the hot gas passes in large amounts through the
oil return valve 39, so that the hot gas flows in large amounts into the compressor
21 via the oil return pipe 38 and the injection pipe 30. It is therefore estimated
that the discharge refrigerant temperature rapidly rises. In view of this, the processing
proceeds to step S17 in order to reduce the amount of hot gas passing through the
oil return valve 39. On the other hand, when the discharge refrigerant temperature
rise speed is less than the predetermined rise speed, the processing returns to step
S15 in which the controller 70 performs the normal control on the oil return valve
39 again.
[0135] In step S17, the controller 70 performs the hot gas bypass suppression control on
the oil return valve 39 to reduce the amount of hot gas passing through the oil return
valve 39. Specifically, in step S16, the controller 70 controls the valve opening
degree of the oil return valve 39 so as to lower the opening degree of the oil return
valve 39 below the valve opening degree at the time when it is determined that the
discharge refrigerant temperature rise speed at the compressor 21 is more than the
predetermined rise speed. More specifically, in step S16, the controller 70 controls
the valve opening degree of the oil return valve 39 so as to lower the opening degree
of the oil return valve 39 to, for example, a half of the valve opening degree at
the time when it is determined that the discharge refrigerant temperature rise speed
at the compressor 21 is more than the predetermined rise speed.
[0136] In step S18, the controller 70 determines whether the state in which the discharge
refrigerant temperature at the compressor 21 (i.e., the temperature detected by the
discharge temperature sensor 47) is equal to or less than a predetermined temperature
continues for a predetermined time with the oil return valve 39 subjected to the hot
gas bypass suppression control. In other words, the controller 70 determines whether
the discharge refrigerant temperature is maintained to be low by the hot gas bypass
suppression control on the oil return valve 39. When the state in which the discharge
refrigerant temperature is equal to or less than the predetermined temperature continues
for the predetermined time, the controller 70 terminates the hot gas bypass suppression
control of the oil return valve 39. The processing then returns to step S15. On the
other hand, when the state in which the discharge refrigerant temperature is equal
to or less than the predetermined temperature does not continue for the predetermined
time, the processing proceeds to step S19.
[0137] In step S19, the controller 70 continuously performs the hot gas bypass suppression
control with the valve opening degree of the oil return valve 39 further lowered.
The processing then proceeds to step S18.
[0138] The controller 70 controls the oil return valve 39 in the cooling operating mode
as described above until the cooling operating mode terminates. The normal control
and the hot gas bypass suppression control for the oil return valve 39 are also performed
in the heating operating mode.
[0139] When the operation of the refrigeration apparatus 100 is stopped after the termination
of the cooling operating mode, the controller 70 controls the valve opening degree
of the oil return valve 39 to bring the oil return valve 39 into the fully open state
rather than the fully closed state. With this configuration, during the stop of the
operation, the refrigerating machine oil in the oil separator 23 can be dissolved
into the refrigerant in the compressor 21 via the oil return pipe 38 and the injection
pipe 30. This configuration therefore enables the next activation of the compressor
21 more reliably.
(6) Features of Refrigeration Apparatus 100
(6-1)
[0140] In the refrigeration apparatus 100 according to this embodiment, the oil return valve
39 is subjected to the normal control in the cooling operating mode and the heating
operating mode, so that the refrigerating machine oil can be returned to the compressor
21 in appropriate amounts according to the circulation amount of the refrigerant in
the compressor 21 and the rate of oil loss in the compressor 21, that is, according
to the situations of the refrigeration cycle, such as the frequency of the compressor
21 as well as the high pressure, intermediate pressure, and low pressure in the refrigeration
cycle. The reliability of the compressor 21 can be thus enhanced.
[0141] In the refrigeration apparatus 100 according to this embodiment, moreover, if the
discharge refrigerant temperature at the compressor 21 rapidly rises (if the discharge
refrigerant temperature rise speed is more than the predetermined rise speed) owing
to, for example, a transitional change in operating condition, even in the normal
control for the oil return valve 39, it is assumed that the high-temperature hot gas
is supplied in large amounts to the compressor 21 since the hot gas refrigerant discharged
from the compressor 21 passes in large amounts through the oil return valve 39, in
addition to the refrigerating machine oil. Based on this assumption, the control for
the oil return valve 39 is switched from the normal control to the hot gas bypass
suppression control to lower the valve opening degree. This configuration thus reduces
the amount of hot gas passing through the oil return valve 39. This configuration
also can reduces such a factor of degradation in performance that the hot gas discharged
from the compressor 21 is immediately sucked into the compressor 21, as small as possible.
[0142] In the refrigeration apparatus 100 according to this embodiment, moreover, one oil
separator 23 is provided for the plurality of compressors, that is, the first compressor
21a, the second compressor 21b, and the third compressor 21c. The oil separator 23
of the refrigeration apparatus 100 according to this embodiment is therefore larger
in capacity than oil separators to be provided for a plurality of compressors in one-to-one
correspondence. If one oil separator 23 having a larger capacity is provided for the
plurality of compressors as described above, the oil separator 23 retains not only
the refrigerating machine oil, but also the hot gas refrigerant in large amounts.
In addition, one oil return pipe 38 that extends from the oil separator 23 is provided
without being branched in correspondence with the number of compressors. For this
reason, the oil return pipe 38 is larger in inner diameter than an oil return pipe
to be provided for each compressor. In the refrigeration apparatus 100 according to
this embodiment, the oil separator 23 retains the hot gas in large amounts, so that
the hot gas refrigerant easily passes in large amounts through the oil return pipe
38. With this configuration, however, even when the oil return valve 39 is subjected
to the normal control, it easily occurs that the hot gas refrigerant passes in large
amounts through the oil return pipe 38 owing to, for example, a transitional change
in operating condition. Even with the configuration, in the refrigeration apparatus
100 according this embodiment, the hot gas bypass suppression control for the oil
return valve 39 suppresses degradation in performance of the refrigeration apparatus
100.
(6-2)
[0143] In the refrigeration apparatus 100 according to this embodiment, the oil return pipe
38 is disposed to merge with the injection pipe 30 that is not connected to the suction
side of the compressor 21, but is connected to the middle of the compression process
in the compressor 21. This configuration thus can suppress a situation in which heat
energy of a part of the high-temperature fluid (the refrigerant and the refrigerating
machine oil) discharged from the compressor 21 is used for raising the suction refrigerant
temperature at the compressor 21.
(6-3)
[0144] In the refrigeration apparatus 100 according to this embodiment, the oil return valve
39 is controlled to be closed in performing the control to increase the frequency
of the compressor 21 upon activation of the compressor 21. This configuration therefore
efficiently can increase the difference between the pressure at the discharge side
of the compressor 21 and the pressure at the side, to which the injection pipe 30
is connected, of the compressor 21 upon activation of the compressor 21.
(6-4)
[0145] In the refrigeration apparatus 100 according to this embodiment, the oil return valve
39 is not controlled to be closed (the oil return valve 39 is brought into the fully
open state in this embodiment) before activation of the compressor 21 which has been
stopped. This configuration therefore achieves pressure equalization by reducing the
difference between the pressure at the discharge side of the compressor 21 and the
pressure at the side, to which the injection pipe 30 is connected, of the compressor
21. This configuration also allows the refrigerating machine oil in the oil separator
23 to be dissolved into the refrigerant in the compressor 21 via the oil return pipe
38 and the injection pipe 30. This configuration thus enables more reliable activation
of the compressor 21.
(7) Modifications
[0146] The foregoing embodiment may be appropriately modified as described in the following
modifications. It should be noted that these modifications are applicable in conjunction
with other modifications insofar as there are no consistencies.
(7-1) Modification A
[0147] According to the foregoing embodiment, the oil return pipe 38 is connected to the
middle of the injection pipe 30 at its opposite end to the end connected to the oil
separator 23.
[0148] However, the oil return pipe is not necessarily connected as described above. As
illustrated in FIG. 4, for example, in a refrigeration apparatus 200, an oil return
pipe 38a may be connected to a middle of a suction-side pipe 42 at its opposite end
to an end connected to an oil separator 23.
[0149] In this case, a refrigerating machine oil separated by the oil separator 23 is supplied
to a suction side of a compressor 21. Also in this case, it is considered that a discharge
refrigerant temperature at the compressor 21 rises if a hot gas passes in large amounts
through an oil return valve 39 on the oil return pipe 38a. Therefore, normal control
and hot gas bypass suppression control can be performed on the oil return valve 39
on the oil return pipe 38a in a manner similar to that described in the foregoing
embodiment.
(7-2) Modification B
[0150] According to the foregoing embodiment, the downstream side of the injection pipe
30 merges with the middle of the compression process in the compressor 21.
[0151] As illustrated in FIG. 5, alternatively, in a refrigeration apparatus 300, an injection
pipe 30a may be connected at its downstream side to a suction side of a compressor
21. It should be noted that the injection pipe 30 in the foregoing embodiment is connected
to the middle of the compression process in the compressor 21; therefore, the amount
of refrigerant to be sucked into the compressor 21 is less prone to be reduced because
of the refrigerant flowing through the injection pipe 30.
[0152] In this case, as in Modification A, a refrigerating machine oil separated by an oil
separator 23 is supplied to the suction side of the compressor 21 via the downstream
side of the injection pipe 30a. Also in this case, it is considered that a discharge
refrigerant temperature at the compressor 21 rises if a hot gas passes in large amounts
through an oil return valve 39. Therefore, normal control and hot gas bypass suppression
control can be performed on the oil return valve 39 in a manner similar to that described
in the foregoing embodiment.
(7-3) Modification C
[0153] According to Modification B, the refrigeration apparatus 300 includes the injection
pipe 30a connected at its downstream end to the suction side of the compressor 21.
[0154] As illustrated in FIG. 6, alternatively, a refrigeration apparatus 400 may include
an injection pipe 30a connected at its downstream side to a suction side of a compressor
21. As in Modification A, the refrigeration apparatus 400 may also include an oil
return pipe 38a connected to a middle of a suction-side pipe 42 at its opposite end
to an end connected to an oil separator 23.
(7-4) Modification D
[0155] According to the foregoing embodiment, the refrigeration apparatus 100 switches the
control for the oil return valve 39 from the normal control to the hot gas bypass
suppression control on the condition that the discharge refrigerant temperature rise
speed at the compressor 21 is more than the predetermined rise speed.
[0156] However, the condition to switch the control for the oil return valve 39 from the
normal control to the hot gas bypass suppression control is not limited thereto. For
example, it is considered that the intermediate pressure in the refrigeration cycle
(i.e., the pressure detected by the intermediate-pressure sensor 40b) lowers if the
amount of hot gas passing though the oil return valve 39 increases in the normal control
for the oil return valve 39. Therefore, the control for the oil return valve 39 may
be switched on a condition that an intermediate pressure drop speed is more than a
predetermined pressure drop speed (i.e., the intermediate pressure lowers rapidly).
[0157] In the situation in which the refrigerating machine oil passes in large amounts through
the oil return valve 39, the refrigerating machine oil is maintained at a liquid state
before flowing into the oil return valve 39 and after flown out of the oil return
valve 39. This refrigerating machine oil is higher in viscosity than the gas refrigerant
and is lower in fluidity than the gas refrigerant. Therefore, the flow velocity of
the refrigerating machine oil does not increase so much at the time when the refrigerating
machine oil passes through the oil return valve 39. Consequently, in the situation
in which the refrigerating machine oil passes in large amounts through the oil return
valve 39, the refrigerating machine oil passes through the oil return valve 39 at
a low flow velocity with lower resistance; therefore, the oil return valve 39 is less
prone to cause considerable decompression.
[0158] In contrast to this, the discharge gas refrigerant is lower in viscosity than the
refrigerating machine oil and is higher in fluidity than the refrigerating machine
oil. Therefore, the flow velocity of the gas refrigerant is apt to increase at the
time when the discharge gas refrigerant passes through the oil return valve 39. Consequently,
in the situation in which the refrigerating machine oil passes in small amounts through
the oil return valve 39 and the discharge gas refrigerant passes in large amounts
through the oil return valve 39, the gas refrigerant passes through the oil return
valve 39 at a high flow velocity with higher resistance, so that the oil return valve
39 is apt to cause considerable decompression.
[0159] A change from the situation in which the refrigerating machine oil passes in large
amounts through the oil return valve 39 to the situation in which the gas refrigerant
passes in large amount though the oil return valve 39 causes a reduction in pressure
at the downstream side of the oil return valve 39, and therefore causes a reduction
in pressure of the refrigerant flowing through the injection pipe 30 to which the
oil return pipe 38 is connected.
[0160] As described above, hence, the control for the oil return valve 39 may be switched
from the normal control to the hot gas bypass suppression control when the drop speed
of the intermediate pressure detected by the intermediate-pressure sensor 40b on the
injection pipe 30 is more than the predetermined pressure drop speed.
[0161] In each of the refrigeration apparatus 200 according to Modification A and the refrigeration
apparatus 400 according to Modification C, the oil return pipe 38a is connected to
the suction-side pipe 42. The control for the oil return valve 39 may be switched
from the normal control to the hot gas bypass suppression control on a condition that
a drop speed of the low pressure (pressure detected by the low-pressure sensor 40a)
in the refrigeration cycle is more than a predetermined pressure drop speed.
[0162] Alternatively, the control for the oil return valve 39 may be switched from the normal
control to the hot gas bypass suppression control on conditions that the discharge
refrigerant temperature rise speed at the compressor 21 is more than the predetermined
rise speed and a drop speed of the intermediate pressure or low pressure in the refrigeration
cycle is more than a predetermined pressure drop speed.
[0163] In a case where relational data on a discharge refrigerant temperature appropriate
for the intermediate pressure in the refrigeration cycle is possessed in advance,
the control for the oil return valve 39 may be switched from the normal control to
the hot gas bypass suppression control on a condition that the discharge refrigerant
temperature is more than the discharge refrigerant temperature appropriate for the
intermediate pressure.
(7-5) Modification E
[0164] According to the foregoing embodiment and the respective modifications, the branch
position of the injection pipe 30 is on the side closer to the heat source-side expansion
valve 28 with respect to the subcooler 31.
[0165] Alternatively, the branch position of the injection pipe 30 may be on the side opposite
to the heat source-side expansion valve 28 with respect to the subcooler 31.
(7-6) Modification F
[0166] According to the foregoing embodiment, the refrigeration apparatus 100 is configured
to cool, for example, the interior of a cold storage warehouse or the interior of
a showcase in a store.
[0167] However, the use of the refrigeration apparatus 100 is not limited thereto. For example,
the refrigeration apparatus 100 may be configured to cool the interior of a container
for transportation. Alternatively, the refrigeration apparatus 100 may be an air conditioning
system (an air conditioner) that implements air conditioning by cooling the interior
of a building.
INDUSTRIAL APPLICABILITY
[0168] The present invention is applicable to a refrigeration apparatus.
REFERENCE SIGNS LIST
[0169]
2: heat source unit
6: liquid-side-refrigerant connection pipe
7: gas-side-refrigerant connection pipe
10: refrigerant circuit
20: heat source unit control unit
21: compressor
21a: first compressor
21b: second compressor
21c: third compressor
23: oil separator
25: heat source-side heat exchanger
26: first heat source liquid-side check valve
27: receiver
28: heat source-side expansion valve
29: second heat source liquid-side check valve
30: injection pipe (refrigerant supply pipe, injection pipe)
30a: injection pipe (refrigerant supply pipe)
31: subcooler
32: subcooling expansion valve (intermediate expansion valve)
33: injection valve
33a: first injection valve
33b: second injection valve
33c: third injection valve
34: first bypass pipe
35: first bypass check valve
36: second branch pipe
37: second branch check valve
38: oil return pipe
38a: oil return pipe
39: oil return valve (flow rate adjusting mechanism)
40a: low-pressure sensor
40b: intermediate-pressure sensor
40c: high-pressure sensor
41: discharge-side pipe
42: suction-side pipe (refrigerant supply pipe)
43: first heat source liquid-side pipe
44: second heat source liquid-side pipe
45: heat source-side fan
47: discharge temperature sensor
50: first usage unit
52: first usage-side heat exchanger
54: first usage-side expansion valve
57: first usage unit control unit
58: first usage-side gas refrigerant pipe
59: first usage-side liquid refrigerant pipe
60: second usage unit
62: second usage-side heat exchanger
64: second usage-side expansion valve
67: second usage unit control unit
68: second usage-side gas refrigerant pipe
69: second usage-side liquid refrigerant pipe
70: controller (control unit)
100, 200, 300, 400: refrigeration apparatus
CITATION LIST
PATENT LITERATURE