U.S. patent application number 12/922810 was filed with the patent office on 2011-01-20 for refrigeration apparatus.
Invention is credited to Shinichi Kasahara.
Application Number | 20110011125 12/922810 |
Document ID | / |
Family ID | 41113237 |
Filed Date | 2011-01-20 |
United States Patent
Application |
20110011125 |
Kind Code |
A1 |
Kasahara; Shinichi |
January 20, 2011 |
REFRIGERATION APPARATUS
Abstract
An air conditioner (10) comprised of a refrigeration apparatus
includes a main controller (60), and a sub-controller (70a, 70b). A
compressor control section of the main controller (60) adjusts
operational capacity of the compressor (31), and stops the
compressor (31) when capability of the air conditioner (10) is
excessive relative to a load. When a frequency at which the
compressor (31) is started and stopped by the compressor control
section is increased, a target superheat degree changing section of
the main controller (60) forcibly increases a target degree of
superheat. Then, in air cooling operation, the sub-controller (70a,
70b) adjusts the degree of opening of an indoor expansion valve
(42, 47) based on the increased target degree of superheat. In air
heating operation, the main controller (60) adjusts the degree of
opening of an outdoor expansion valve (34) based on the increased
target degree of superheat.
Inventors: |
Kasahara; Shinichi; (Osaka,
JP) |
Correspondence
Address: |
BIRCH STEWART KOLASCH & BIRCH
PO BOX 747
FALLS CHURCH
VA
22040-0747
US
|
Family ID: |
41113237 |
Appl. No.: |
12/922810 |
Filed: |
March 11, 2009 |
PCT Filed: |
March 11, 2009 |
PCT NO: |
PCT/JP2009/001097 |
371 Date: |
September 15, 2010 |
Current U.S.
Class: |
62/498 ;
62/513 |
Current CPC
Class: |
F25B 43/006 20130101;
F25B 49/02 20130101; F25B 2600/025 20130101; F25B 13/00 20130101;
F25B 2313/02741 20130101; F25B 2700/1931 20130101; F25B 2700/21174
20130101; F25B 2700/1933 20130101; F25B 2313/006 20130101; F25B
2313/0233 20130101; F25B 2313/005 20130101; F25B 2700/21175
20130101; F25B 2500/15 20130101; F25B 2600/2513 20130101 |
Class at
Publication: |
62/498 ;
62/513 |
International
Class: |
F25B 1/00 20060101
F25B001/00; F25B 41/00 20060101 F25B041/00 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 24, 2008 |
JP |
2008-076250 |
Claims
1. A refrigeration apparatus comprising: a refrigerant circuit (20)
which includes a compressor (31), an expansion mechanism (34, 42,
47), a heat source-side heat exchanger (33), and a utilization-side
heat exchanger (41, 46) connected thereto, and performs a
refrigeration cycle in which high pressure is set higher than
critical pressure of a refrigerant; and a control means (80) which
controls the compressor (31) and the expansion mechanism (34, 42,
47), wherein the control means (80) is configured to perform
capacity control operation of adjusting capacity of the compressor
(31) in such a manner that a physical value representing an
operating state of the refrigeration cycle performed by the
refrigerant circuit (20) reaches a target control value, flow rate
control operation of adjusting a flow rate of the refrigerant
passing through the expansion mechanism (34, 42, 47) in such a
manner that a degree of superheat of the refrigerant flowing from
one of the heat source-side heat exchanger (33) and the
utilization-side heat exchanger (41, 46) which functions as an
evaporator to the compressor (31) reaches a target degree of
superheat, and a target superheat degree changing operation of
forcibly increasing the target degree of superheat when the
compressor (13) is stopped by the capacity control operation.
2. The refrigeration apparatus comprising: a refrigerant circuit
(20) which includes a compressor (31), an expansion mechanism (34,
42, 47), a heat source-side heat exchanger (33), and a
utilization-side heat exchanger (41, 46) connected thereto, and
performs a refrigeration cycle in which high pressure is set higher
than critical pressure of a refrigerant; and a control means (80)
which controls the compressor (31), the refrigeration apparatus
performing at least cooling operation in which the heat source-side
heat exchanger (33) functions as a gas cooler, and the
utilization-side heat exchanger (41, 46) functions as an
evaporator, wherein the control means (80) is configured to perform
capacity control operation of adjusting capacity of the compressor
(31) in such a manner that a control parameter, which is
evaporating temperature of the refrigerant in the utilization-side
heat exchanger (41, 46), or low pressure of the refrigeration cycle
performed by the refrigerant circuit (20), reaches a target control
value, and target control value changing operation of gradually
reducing the target control value after the compressor (31) is
started in such a manner that the target control value reaches a
predetermined standard target value after a predetermined period of
time from the start of the compressor (31).
3. The refrigeration apparatus comprising: a refrigerant circuit
(20) which includes a compressor (31), an expansion mechanism (34,
42, 47), a heat source-side heat exchanger (33), and a
utilization-side heat exchanger (41, 46) connected thereto, and
performs a refrigeration cycle in which high pressure is set higher
than critical pressure of a refrigerant; and a control means (80)
which controls the compressor (31), the refrigeration apparatus
performing at least heating operation in which the utilization-side
heat exchanger (41, 46) functions as a gas cooler, and the heat
source-side heat exchanger (33) functions as an evaporator, wherein
the control means (80) is configured to perform capacity control
operation of adjusting capacity of the compressor (31) in such a
manner that a control parameter, which is high pressure of the
refrigeration cycle performed by the refrigerant circuit (20),
reaches a target control value, and target control value changing
operation of gradually increasing the target control value after
the compressor (31) is started in such a manner that the target
control value reaches a predetermined standard target value after a
predetermined period of time from the start of the compressor
(31).
4. The refrigeration apparatus comprising: a refrigerant circuit
(20) which includes a compressor (31), an expansion mechanism (34,
42, 47), a heat source-side heat exchanger (33), and a
utilization-side heat exchanger (41, 46) connected thereto, and
performs a refrigeration cycle in which high pressure is set higher
than critical pressure of a refrigerant; and a control means (80)
which controls the compressor (31), wherein the control means (80)
is configured to perform capacity control operation of adjusting
capacity of the compressor (31) based on a command value calculated
using a physical value representing an operating state of the
refrigeration cycle performed by the refrigerant circuit (20), and
a control gain in such a manner that the physical value reaches a
target control value, and gain adjustment operation of reducing the
control gain as a load of the refrigeration apparatus is reduced.
Description
TECHNICAL FIELD
[0001] The present invention relates to refrigeration apparatuses
which perform a refrigeration cycle in which high pressure is set
higher than critical pressure of a refrigerant.
BACKGROUND ART
[0002] Refrigeration apparatuses which perform a refrigeration
cycle by circulating a refrigerant in a refrigerant circuit have
been known. In a refrigeration apparatus disclosed by Patent
Document 1, high pressure of the refrigeration cycle performed by
the refrigerant circuit is set higher than critical pressure of the
refrigerant. That is, the refrigerant circuit of the refrigeration
apparatus performs a so-called supercritical cycle.
[0003] In an air conditioner disclosed by Patent Document 2, a
general refrigeration cycle is performed in which the high pressure
is set lower than the critical pressure of the refrigerant.
According to Patent Document 2, a target value for controlling the
operation of the air conditioner is adjusted to reduce a frequency
of starts and stops of a compressor in the air conditioner.
Citation List
[0004] Patent Document 1: Japanese Patent Publication No.
2001-116376
[0005] Patent Document 2: Japanese Patent Publication No.
2002-061925
SUMMARY OF THE INVENTION
Technical Problem
[0006] In a refrigeration apparatus which performs the so-called
supercritical cycle, the compressor may be started/stopped to
adjust capability of the refrigeration apparatus. For example, even
when a variable capacity compressor is used, and the capacity of
the compressor is set to the lowest, the capability of the
refrigeration apparatus may be too high relative to a load. In such
a state, the compressor is stopped.
[0007] In the supercritical cycle, the high pressure is higher than
that in the general refrigeration cycle. Therefore, as compared
with the general refrigeration cycle in which the high pressure is
lower than the critical pressure of the refrigerant, the
supercritical cycle consumes higher energy until the high pressure
and the low pressure of the refrigeration cycle reach appropriate
values after the compressor is started. Nevertheless, effective
measures have not been taken so far to reduce the frequency of
starts and stops of the compressor in the refrigeration apparatus
which performs the supercritical cycle.
[0008] In view of the foregoing, the present invention has been
achieved. An object of the invention is to reduce the number of
times the compressor is started and stopped in the refrigeration
apparatus which performs the so-called supercritical cycle, thereby
improving operation efficiency of the refrigeration apparatus.
Solution to the Problem
[0009] A first aspect of the invention is directed to a
refrigeration apparatus including: a refrigerant circuit (20) which
includes a compressor (31), an expansion mechanism (34, 42, 47), a
heat source-side heat exchanger (33), and a utilization-side heat
exchanger (41, 46) connected thereto, and performs a refrigeration
cycle in which high pressure is set higher than critical pressure
of a refrigerant; and a control means (80) which controls the
compressor (31) and the expansion mechanism (34, 42, 47). The
control means (80) is configured to perform capacity control
operation of adjusting capacity of the compressor (31) in such a
manner that a physical value representing an operating state of the
refrigeration cycle performed by the refrigerant circuit (20)
reaches a target control value, flow rate control operation of
adjusting a flow rate of the refrigerant passing through the
expansion mechanism (34, 42, 47) in such a manner that a degree of
superheat of the refrigerant flowing from one of the heat
source-side heat exchanger (33) and the utilization-side heat
exchanger (41, 46) which functions as an evaporator to the
compressor (31) reaches a target degree of superheat, and a target
superheat degree changing operation of forcibly increasing the
target degree of superheat when the compressor (13) is stopped by
the capacity control operation.
[0010] A second aspect of the invention is directed to a
refrigeration apparatus including: a refrigerant circuit (20) which
includes a compressor (31), an expansion mechanism (34, 42, 47), a
heat source-side heat exchanger (33), and a utilization-side heat
exchanger (41, 46) connected thereto, and performs a refrigeration
cycle in which high pressure is set higher than critical pressure
of a refrigerant; a control means (80) which controls the
compressor (31), the refrigeration apparatus performing at least
cooling operation in which the heat source-side heat exchanger (33)
functions as a gas cooler, and the utilization-side heat exchanger
(41, 46) functions as an evaporator. The control means (80) is
configured to perform capacity control operation of adjusting
capacity of the compressor (31) in such a manner that a control
parameter, which is evaporating temperature of the refrigerant in
the utilization-side heat exchanger (41, 46), or low pressure of
the refrigeration cycle performed by the refrigerant circuit (20),
reaches a target control value, and target control value changing
operation of gradually reducing the target control value after the
compressor (31) is started in such a manner that the target control
value reaches a predetermined standard target value after a
predetermined period of time from the start of the compressor
(31).
[0011] A third aspect of the invention is directed to a
refrigeration apparatus including: a refrigerant circuit (20) which
includes a compressor (31), an expansion mechanism (34, 42, 47), a
heat source-side heat exchanger (33), and a utilization-side heat
exchanger (41, 46) connected thereto, and performs a refrigeration
cycle in which high pressure is set higher than critical pressure
of a refrigerant; and a control means (80) which controls the
compressor (31), the refrigeration apparatus performing at least
heating operation in which the utilization-side heat exchanger (41,
46) functions as a gas cooler, and the heat source-side heat
exchanger (33) functions as an evaporator. The control means (80)
is configured to perform capacity control operation of adjusting
capacity of the compressor (31) in such a manner that a control
parameter, which is high pressure of the refrigeration cycle
performed by the refrigerant circuit (20), reaches a target control
value, and target control value changing operation of gradually
increasing the target control value after the compressor (31) is
started in such a manner that the target control value reaches a
predetermined standard target value after a predetermined period of
time from the start of the compressor (31).
[0012] A fourth aspect of the invention is directed to a
refrigeration apparatus including: a refrigerant circuit (20) which
includes a compressor (31), an expansion mechanism (34, 42, 47), a
heat source-side heat exchanger (33), and a utilization-side heat
exchanger (41, 46) connected thereto, and performs a refrigeration
cycle in which high pressure is set higher than critical pressure
of a refrigerant; and a control means (80) which controls the
compressor (31). The control means (80) is configured to perform
capacity control operation of adjusting capacity of the compressor
(31) based on a command value calculated using a physical value
representing an operating state of the refrigeration cycle
performed by the refrigerant circuit (20), and a control gain in
such a manner that the physical value reaches a target control
value, and gain adjustment operation of reducing the control gain
as a load of the refrigeration apparatus is reduced.
[0013] According to the first to fourth aspects of the invention,
the refrigeration cycle is performed by circulating the refrigerant
in the refrigerant circuit (20). In this case, the pressure of the
refrigerant discharged from the compressor (31) is higher than the
critical pressure of the refrigerant. In the refrigerant circuit
(20), one of the heat source-side heat exchanger (33) and the
utilization-side heat exchanger (41, 46) functions as a gas cooler,
and the other functions as an evaporator.
[0014] According to the first aspect of the invention, the control
means (80) performs the capacity control operation. In the capacity
control operation, capacity of the compressor (31) is adjusted in
such a manner that a predetermined physical value reaches a target
control value. The control means (80) stops the compressor (31)
when the capacity of the compressor (31) cannot be reduced anymore
although the predetermined physical value is deviated from the
target control value. When the compressor (31) is stopped by the
capacity control operation, the control means (80) performs the
target superheat degree changing operation to forcibly increase the
target degree of superheat. Then, after the compressor (31) is
restarted, the control means (80) performs the flow rate control
operation using the target degree of superheat increased by the
target superheat degree changing operation. Specifically, the
control means (80) adjusts the flow rate of the refrigerant passing
through the expansion mechanism (34, 42, 47) in such a manner that
the degree of superheat of the refrigerant flowing from the heat
exchanger (33, 41, 46) which functions as an evaporator to the
compressor (31) reaches the increased target degree of
superheat.
[0015] According to the first aspect of the invention, the
expansion mechanism (34, 42, 47) is brought into the state where
the flow rate of the refrigerant passing through the expansion
mechanism is reduced as the target degree of superheat is
increased. With the capacity of the compressor (31) kept constant,
the amount of the refrigerant circulating in the refrigerant
circuit (20) is reduced as the target degree of superheat is
increased, thereby reducing the capability of the refrigeration
apparatus (10). That is, a lower limit value of the capability of
the refrigeration apparatus (10) is reduced as the target degree of
superheat is increased. Thus, the compressor (31), which would have
to be stopped by the control means (80) before the target degree of
superheat is increased, is more likely to be continuously operated
after the target degree of superheat is increased.
[0016] According to the second aspect of the invention, the control
means (80) performs the capacity control operation, and the target
control value changing operation in the cooling operation. In the
capacity control operation, the control means (80) adjusts the
capacity of the compressor (31) in such a manner that a control
parameter, which is evaporating temperature of the refrigerant in
the utilization-side heat exchanger (41, 46), or the low pressure
of the refrigeration cycle performed by the refrigerant circuit
(20), reaches a target control value. The control means (80) stops
the compressor (31) when the capacity of the compressor (31) cannot
be reduced anymore although the control parameter is deviated from
the target control value. Then, after the compressor (31) is
restarted, the control means (80) performs the target control value
changing operation. In the target control value changing operation,
the control means (80) sets the target control value at a point of
time when the compressor (31) is restarted higher than a standard
target value, and then gradually reduces the target control value
to be close to the standard target value in a predetermined period
of time from the point of time. During this period, in the capacity
control operation, the capacity of the compressor (31) is adjusted
using the target control value adjusted by the target control value
changing operation.
[0017] Immediately after the start of the compressor (31), there is
a big difference between the control parameter, which is the
evaporating temperature of the refrigerant, or an actual
measurement of the low pressure of the refrigeration cycle, and the
standard target value. Thus, when the target control value is not
changed from the standard target value immediately after the start
of the compressor (31), the capacity of the compressor (31) is
abruptly increased to bring the control parameter close to the
standard target value as soon as possible. When the cooling
capability of the refrigeration apparatus (10) is abruptly
increased due to the abrupt increase in capacity of the compressor
(31), the cooling capability becomes excessive in a relatively
short time after the start of the compressor (31), and the
compressor (31) has to be stopped again.
[0018] In contrast, according to the control means (80) of the
second aspect of the invention, the target control value is set
higher than the standard target value for some time after the start
of the compressor (31). Thus, even immediately after the start of
the compressor (31), the difference between the control parameter,
which is the evaporating temperature of the refrigerant or the
actual measurement of the low pressure of the refrigeration cycle,
and the target control value is smaller than the difference in the
case where the target control value is not changed from the
standard target value. This alleviates the abrupt increase in
capacity of the compressor (31) after the start of the compressor
(31), thereby gently changing the cooling capability of the
refrigeration apparatus (10). Thus, with the target control value
set higher than the standard target value by the control means (80)
of the present invention, the compressor (31), which would have to
be stopped by the control means (80) when the target control value
is not changed from the standard target value, is more likely to be
continuously operated.
[0019] According to the third aspect of the invention, the control
means (80) performs the capacity control operation, and the target
control value changing operation in the heating operation. In the
capacity control operation, the control means (80) adjusts the
capacity of the compressor (31) in such a manner that the control
parameter, which is the high pressure of the refrigeration cycle
performed by the refrigerant circuit (20), reaches the target
control value. The control means (80) stops the compressor (31)
when the capacity of the compressor (31) cannot be reduced anymore
although the control parameter is deviated from the target control
value. Then, after the compressor (31) is restarted, the control
means (80) performs the target control value changing operation. In
the target control value changing operation, the control means (80)
sets the target control value at a point of time when the
compressor (31) is restarted lower than the standard target value,
and then gradually increases the target control value to be close
to the standard target value in a predetermined period of time from
the point of time. During this period, in the capacity control
operation, the capacity of the compressor (31) is adjusted using
the target control value adjusted by the target control value
changing operation.
[0020] Immediately after the start of the compressor (31), there is
a big difference between the control parameter, which is the actual
measurement of the high pressure of the refrigeration cycle, and
the standard target value. Thus, when the target control value is
not changed from the standard target value immediately after the
start of the compressor (31), the capacity of the compressor (31)
is abruptly increased to bring the control parameter close to the
standard target value as soon as possible. When the heating
capability of the refrigeration apparatus (10) is abruptly
increased due to the abrupt increase in capacity of the compressor
(31), the heating capability becomes excessive in a relatively
short time after the start of the compressor (31), and the
compressor (31) has to be stopped again.
[0021] In contrast, according to the control means (80) of the
third aspect of the invention, the target control value is set
lower than the standard target value for some time after the start
of the compressor (31). Thus, even immediately after the start of
the compressor (31), the difference between the actual measurement
of the high pressure of the refrigeration cycle as the control
parameter, and the target control value is smaller than the
difference in the case where the target control value is not
changed from the standard target value. This alleviates the abrupt
increase in capacity of the compressor (31) after the start of the
compressor (31), thereby gently changing the heating capability of
the refrigeration apparatus (10). Thus, with the target control
value set lower than the standard target value by the control means
(80) of the present invention, the compressor (31), which would
have to be stopped by the control means (80) when the target
control value is not changed from the standard target value, is
more likely to be continuously operated.
[0022] According to the fourth aspect of the invention, the control
means (80) performs the capacity control operation, and the target
control value changing operation. In the capacity control
operation, the capacity of the compressor (31) is adjusted in such
a manner that a predetermined physical value reaches a target
control value. The control means (80) stops the compressor (31)
when the capacity of the compressor (31) cannot be reduced anymore
although the predetermined physical value is deviated from the
target control value. Further, the control means (80) performs the
gain adjustment operation of reducing the control gain used in the
capacity control operation as the load of the refrigeration
apparatus (10) is reduced.
[0023] When the control gain is kept high although the load of the
refrigeration apparatus (10) is reduced, the amount of change in
capacity of the compressor (31) determined based on a deviation
between the predetermined physical value and the target control
value is increased. As a result, the capability of the
refrigeration apparatus (10) becomes excessive relative to the
load, and the compressor (31) is more likely to be stopped.
[0024] In contrast, according to the control means (80) of the
fourth aspect of the invention, the control gain is reduced as the
load of the refrigeration apparatus (10) is reduced. Thus, the
command value calculated using the predetermined physical value and
the control gain is reduced as compared with the case where the
control gain is constant. With the control gain reduced by the
control means (80) according to the invention, the compressor (31),
which would have to be stopped by the control means (80) when the
control gain is constant, is more likely to be continuously
operated.
Advantages of the Invention
[0025] As described above, according to the first aspect of the
invention, the target degree of superheat is increased to reduce
the lower limit value of the capability of the refrigeration
apparatus (10), thereby reducing the possibility that the
compressor (31) is stopped due to excessive capability of the
refrigeration apparatus (10) relative to the load. According to the
second aspect of the invention, the control parameter in the
cooling operation is set higher immediately after the start of the
compressor (31), thereby reducing the possibility that the
compressor (31) is stopped due to excessive cooling capability of
the refrigeration apparatus (10) relative to the load. According to
the third aspect of the invention, the control parameter in the
heating operation is set lower immediately after the start of the
compressor (31), thereby reducing the possibility that the
compressor (31) is stopped due to excessive heating capability of
the refrigeration apparatus (10) relative to the load. According to
the fourth aspect of the invention, the control gain is set lower
when the load of the refrigeration apparatus (10) is small, thereby
reducing the possibility that the compressor (31) is stopped due to
excessive capability of the refrigeration apparatus (10) relative
to the load.
[0026] Thus, according to the invention, in the refrigeration
apparatus (10) which performs the so-called supercritical cycle,
the possibility that the compressor (31) is stopped due to the
excessive capability of the refrigeration apparatus (10) relative
to the load can be reduced. Specifically, in the refrigeration
apparatus (10) which performs the supercritical cycle in which
"high energy is consumed until the high pressure and the low
pressure of the refrigeration cycle reach the appropriate values
after the compressor (31) is started," the number of times the
compressor (31) is started and stopped for capability adjustment
can be reduced. Thus, according to the invention, the number of
times the compressor (31) is started and stopped for capability
adjustment can be reduced, thereby reducing the power consumed
while the refrigeration apparatus (10) is operated, and improving
operation efficiency of the refrigeration apparatus (10).
BRIEF DESCRIPTION OF THE DRAWINGS
[0027] FIG. 1 is a refrigerant circuit diagram illustrating the
schematic structure of an air conditioner of a first
embodiment.
[0028] FIG. 2 is a block diagram illustrating the structure of a
main controller and sub-controllers of the first embodiment.
[0029] FIG. 3 is a block diagram illustrating the structure of a
main controller of a second embodiment.
[0030] FIG. 4 is a block diagram illustrating the structure of a
main controller of a third embodiment.
DESCRIPTION OF REFERENCE CHARACTERS
[0031] 10 Air conditioner (refrigeration apparatus) [0032] 20
Refrigeration circuit [0033] 31 Compressor [0034] 33 Outdoor heat
exchanger (heat source-side heat exchanger) [0035] 34 Outdoor
expansion valve (expansion mechanism) [0036] 41 Indoor heat
exchanger (utilization-side heat exchanger) [0037] 42 Indoor
expansion valve (expansion mechanism) [0038] 46 Indoor heat
exchanger (utilization-side heat exchanger) [0039] 47 Indoor
expansion valve (expansion mechanism) [0040] 60 Main controller
[0041] 70a Sub-controller [0042] 70b Sub-controller [0043] 80
Control means
DESCRIPTION OF EMBODIMENTS
[0044] Embodiments of the present invention will be described in
detail with reference to the drawings. The embodiments described
below are directed to an air conditioner (10) comprised of a
refrigeration apparatus.
First Embodiment of the Invention
[0045] As shown in FIG. 1, the air conditioner (10) of the present
embodiment includes a single outdoor unit (11), and two indoor
units (12, 13). The outdoor unit (11) is placed outside. The indoor
units (12, 13) are placed inside. The number of the outdoor unit
(11) and the number of the indoor units (12, 13) are merely
described as examples. The air conditioner (10) includes a main
controller (60), and sub-controllers (70a, 70b). The main
controller (60) and the sub-controllers (70a, 70b) constitute a
control means (80).
[0046] In the air conditioner (10) of this embodiment, an outdoor
circuit (30) of the outdoor unit (11) and indoor circuits (40, 45)
of the indoor units (12, 13) are connected through a liquid flow
pipe (21) and a gas flow pipe (22) to form a refrigerant circuit
(20). The refrigerant circuit (20) is filled with carbon dioxide
(CO.sub.2) as a refrigerant. The refrigerant circuit (20) performs
a refrigeration cycle in which high pressure is set higher than
critical pressure of carbon dioxide as the refrigerant.
[0047] The outdoor unit (11) contains a single outdoor circuit
(30). The outdoor circuit (30) includes the compressor (31), a
four-way switching valve (32), an outdoor heat exchanger (33) as a
heat source-side heat exchanger, an outdoor expansion valve (34) as
an expansion mechanism, a receiver (35), a liquid stop valve (36),
and a gas stop valve (37). The outdoor unit (11) is provided with
an outdoor fan (16) for sending outdoor air to the outdoor heat
exchanger (33).
[0048] In the outdoor circuit (30), the compressor (31) is
connected to a first port of the four-way switching valve (32)
through a discharge side thereof, and is connected to a second port
of the four-way switching valve (32) through a suction side
thereof. The outdoor heat exchanger (33) is connected to a third
port of the four-way switching valve through a gas end thereof, and
is connected to an end of the outdoor expansion valve (34) through
a liquid end thereof. The other end of the outdoor expansion valve
(34) is connected to the liquid stop valve (36) through the
receiver (35). A fourth port of the four-way switching valve (32)
is connected to the gas stop valve (37).
[0049] The indoor units (12, 13) contain indoor circuits (40, 45),
respectively. Each of the indoor circuits (40, 45) includes an
indoor heat exchanger (41, 46) as a utilization-side heat
exchanger, and an indoor expansion valve (42, 47) as an expansion
mechanism. The indoor heat exchanger (41, 46) and the indoor
expansion valve (42, 47) in each of the indoor circuits (40, 45)
are connected in series. Each of the indoor units (12, 13) contains
an indoor fan (17, 18) for sending room air to the indoor heat
exchanger (41, 46).
[0050] In the refrigerant circuit (20), an end of the liquid flow
pipe (21) is connected to the liquid stop valve (36). The other end
of the liquid flow pipe (21) is branched in two, and the branched
ends are connected to the ends of the indoor units (40, 45) near
the indoor expansion valves (42, 47), respectively. An end of the
gas flow pipe (22) is connected to the gas stop valve (37). The
other end of the gas flow pipe (22) is branched in two, and the
branched ends are connected to the ends of the indoor units (40,
45) near the indoor heat exchangers (41, 46), respectively.
Specifically, the two indoor units (40, 45) are parallel-connected
to the single outdoor circuit (30) in the refrigerant circuit
(20).
[0051] The compressor (31) is a hermetic compressor including a
compression mechanism and a motor in a single casing. The outdoor
heat exchanger (33), and the indoor heat exchangers (41, 46) are
fin-and-tube air heat exchangers which are configured to exchange
heat between the refrigerant and the air. The outdoor expansion
valve (34), and the indoor expansion valves (42, 47) are
motor-operated expansion valves capable of changing the degree of
opening. The four-way switching valve (32) is configured to be able
to switch between a first state where the first and third ports
communicate with each other, and the second and fourth ports
communicate with each other (a state indicated by a solid line in
FIG. 1), and a second state where the first and fourth ports
communicate with each other, and the second and third ports
communicate with each other (a state indicated by a broken line in
FIG. 1).
[0052] The outdoor unit (11) includes a high pressure sensor (51),
a low pressure sensor (52), a suction temperature sensor (53), an
outdoor gas temperature sensor (54), and an outdoor air temperature
sensor (58). The high pressure sensor (51) is connected to the
refrigerant circuit (20) between the discharge side of the
compressor (31) and the first port of the four-way switching valve
(32) to measure the pressure of the refrigerant discharged from the
compressor (31). The low pressure sensor (52) is connected to the
refrigerant circuit (20) between the suction side of the compressor
(31) and the second port of the four-way switching valve (32) to
measure the pressure of the refrigerant sucked into the compressor
(31). The suction temperature sensor (53) is attached to the
refrigerant circuit (20) between the suction side of the compressor
(31) and the second port of the four-way switching valve (32) to
measure the temperature of the refrigerant sucked into the
compressor (31). The outdoor gas temperature sensor (54) is
arranged near the gas end of the outdoor heat exchanger (33) in the
outdoor circuit (30) to measure the temperature of the refrigerant
passing through the gas end. The outdoor air temperature sensor
(58) measures the temperature of outdoor air before passing through
the outdoor heat exchanger (33).
[0053] The indoor units (12, 13) include room air temperature
sensors (55a, 55b), indoor gas temperature sensors (56, 56b), and
indoor liquid temperature sensors (57, 57b), respectively. The room
air temperature sensor (55a, 55b) measures the temperature of the
room air before passing through the indoor heat exchanger (41, 46).
The indoor gas temperature sensor (56, 56b) is arranged near an end
of indoor heat exchanger (41, 46) opposite the indoor expansion
valve (42, 47) in the corresponding indoor circuit (40, 45) to
measure the temperature of the refrigerant passing through the end.
The indoor liquid temperature sensor (57, 57b) is arranged near an
end of the indoor heat exchanger (41, 46) close to the indoor
expansion valve (42, 47) in the corresponding indoor circuit (40,
45) to measure the temperature of the refrigerant passing through
the end.
[0054] The main controller (60) is arranged in the outdoor unit
(11). As shown in FIG. 2, the main controller (60) includes a
target low pressure determining section (61), a target high
pressure determining section (62), a compressor control section
(63), an outdoor expansion valve control section (64), and a target
superheat degree changing section (65). The main controller (60)
receives measurements of the high pressure sensor (51), the low
pressure sensor (52), the suction temperature sensor (53), the
outdoor gas temperature sensor (54), the room air temperature
sensors (55a, 55b), and the outdoor air temperature sensor
(58).
[0055] The sub-controllers (70a, 70b) are arranged in the indoor
units (12, 13), respectively. As shown in FIG. 2, the
sub-controllers (70a, 70b) include indoor expansion valve control
sections (71a, 71b), respectively. Each of the sub-controllers
(70a, 70b) receives a measurement of the low pressure sensor (52).
Each of the sub-controllers (70a, 70b) receives measurements of the
indoor gas temperature sensor (56, 56b) and the indoor liquid
temperature sensor (57, 57b) arranged in the same indoor unit (12,
13).
[0056] The main controller (60) and the sub-controllers (70a, 70b)
control the operation of the air conditioner (10) using the
measurements input from the sensors. Details of the control
operation performed by the main controller (60) and the
sub-controllers (70a, 70b) will be described in detail below.
--Operation Mechanism of Air Conditioner--
[0057] The air conditioner (10) of the present embodiment
selectively performs air cooling operation as cooling operation,
and air heating operation as heating operation. Switching between
the air cooling operation and the air heating operation is
performed by switching the four-way switching valve (32).
<Air Cooling Operation>
[0058] Operation of the air conditioner (10) in the air cooling
operation will be described. In the air cooling operation, the
four-way switching valve (32) is set to the first state (the state
indicated by a solid line in FIG. 1). In the air cooling operation,
the outdoor expansion valve (34) is fully opened, and the degrees
of opening of the indoor expansion valves (42, 47) are suitably
adjusted.
[0059] The refrigerant circuit (20) performs a refrigeration cycle
by circulating the refrigerant. In the refrigerant circuit (20)
performing the air cooling operation, the outdoor heat exchanger
(33) functions as a gas cooler, and each of the indoor heat
exchangers (41, 46) functions as an evaporator.
[0060] Specifically, the supercritical refrigerant discharged from
the compressor (31) passes through the four-way switching valve
(32) to enter the outdoor heat exchanger (33), and dissipates heat
to the outdoor air. The refrigerant flowing out of the outdoor heat
exchanger (33) passes through the outdoor expansion valve (34) and
the receiver (35), flows into the liquid flow pipe (21), and is
distributed to the indoor circuits (40, 45).
[0061] Each of the refrigerant streams that entered the
corresponding indoor circuit (40, 45) is reduced in pressure as it
passes through the indoor expansion valve (42, 47) to reach a
gas-liquid two phase state, and absorbs heat from the room air in
the indoor heat exchanger (41, 46) to evaporate. Each of the indoor
units (12, 13) feeds the room air cooled in the indoor heat
exchanger (41, 46) to the inside of a room. The refrigerant streams
that passed through the indoor heat exchangers (41, 46),
respectively, flow into the gas flow pipe (22) to merge with each
other, and the merged stream is sucked into the compressor (31)
after passing through the four-way switching valve (32). The
compressor (31) compresses the sucked refrigerant, and discharges
the compressed refrigerant.
<Air Heating Operation>
[0062] Operation of the air conditioner (10) in the air heating
operation will be described. In the air heating operation, the
four-way switching valve (32) is set to the second state (the state
indicated by a broken line in FIG. 1). In the air heating
operation, the degrees of opening of the outdoor expansion valve
(34) and the indoor expansion valves (42, 47) are suitably
adjusted.
[0063] The refrigerant circuit (20) performs a refrigeration cycle
by circulating the refrigerant. In refrigerant circuit (20)
performing the air heating operation, each of the indoor heat
exchangers (41, 46) functions as a gas cooler, and the outdoor heat
exchanger (33) functions as an evaporator.
[0064] Specifically, the supercritical refrigerant discharged from
the compressor (31) passes through the four-way switching valve
(32) to enter the gas flow pipe (22), and is distributed to the
indoor circuits (40, 45). Each of the refrigerant streams that
entered the corresponding indoor circuit (40, 45) dissipates heat
to the room air in the indoor heat exchanger (41, 46). Each of the
indoor units (12, 13) feeds the room air heated in the indoor heat
exchanger (41, 46) to the inside of the room. The refrigerant
flowing out of the indoor heat exchanger (41, 46) flows into the
liquid flow pipe (21) after passing through the indoor expansion
valve (42, 47), and then flows into the outdoor circuit (30).
[0065] The refrigerant that entered the outdoor circuit (30) is
sent to the outdoor expansion valve (34) after passing through the
receiver (35), and is reduced in pressure as it passes through the
outdoor expansion valve (34) to reach a gas-liquid two phase state.
The refrigerant that passed through the outdoor expansion valve
(34) is sent to the outdoor heat exchanger (33), and absorbs heat
from the outdoor air to evaporate. The refrigerant flowing out of
the outdoor heat exchanger (33) passes through the four-way
switching valve (32), and is sucked into the compressor (31). The
compressor (31) compresses the sucked refrigerant, and discharges
the compressed refrigerant.
--Operation of Main Controller and Sub-Controller--
[0066] As described above, the main controller (60) and the
sub-controllers (70a, 70b) control the operation of the air
conditioner (10) based on the measurements input from the
sensors.
<Air Cooling Operation>
[0067] Operation of the main controller (60) and the
sub-controllers (70a, 70b) in the air cooling operation will be
described. In the air cooling operation, the target low pressure
determining section (61), the compressor control section (63), and
the target superheat degree changing section (65) of the main
controller (60) are operated. In the main controller (60), the
outdoor expansion valve control section (64) performs only
operation of keeping the outdoor expansion valve (34) fully opened,
and the target high pressure determining section (62) is suspended.
In each of the sub-controllers (70a, 70b), the indoor expansion
valve control section (71a, 71b) is operated.
[0068] The indoor expansion valve control section (71a, 71b) of
each of the sub-controllers (70a, 70b) adjusts the degree of
opening of the indoor expansion valve (42, 47) arranged in the
corresponding indoor unit (12, 13). Specifically, in a first indoor
unit (12), the indoor expansion valve control section (71a) of the
sub-controller (70a) adjusts the degree of opening of a first
expansion valve (42) in such a manner that the degree of superheat
of the refrigerant at the exit of a first indoor heat exchanger
(41) reaches the predetermined target degree of superheat. In a
second indoor unit (13), the indoor expansion valve control section
(71b) of the sub-controller (70b) adjusts the degree of opening of
a second indoor expansion valve (47) in such a manner that the
degree of superheat of the refrigerant at the exit of a second
indoor heat exchanger (46) reaches the predetermined target degree
of superheat.
[0069] The control operation performed by each of the indoor
expansion valve control sections (71a, 71b) will be described in
detail below. The indoor expansion valve control section (71a, 71b)
calculates the degree of superheat of the refrigerant at the exit
of the indoor heat exchanger (41, 46) in the corresponding indoor
unit (12, 13) by subtracting saturation temperature of the
refrigerant associated with a detected value of the low pressure
sensor (52) from a detected value of the indoor gas temperature
sensor (56, 56b) in the corresponding indoor unit (12, 13). Then,
the degree of opening of the indoor expansion valve (42, 47) in the
corresponding indoor unit (12, 13) is adjusted in such a manner
that the calculated degree of superheat reaches the target degree
of superheat. The control of the degree of opening of the indoor
expansion valve (42, 47) by the indoor expansion valve control
section (71a, 71b) is performed by general feedback control, such
as PID control etc.
[0070] Specifically, when the calculated degree of superheat is
lower than the target degree of superheat, the indoor expansion
valve control section (71a, 71b) reduces the degree of opening of
the indoor expansion valve (42, 47) to reduce the flow rate of the
refrigerant passing through the indoor heat exchanger (41, 46),
thereby increasing the degree of superheat of the refrigerant at
the exit of the indoor heat exchanger (41, 46). When the calculated
degree of superheat is higher than the target degree of superheat,
the indoor expansion valve control section (71a, 71b) increases the
degree of opening of the indoor expansion valve (42, 47) to
increase the flow rate of the refrigerant passing through the
indoor heat exchanger (41, 46), thereby reducing the degree of
superheat of the refrigerant at the exit of the indoor heat
exchanger (41, 46). In the indoor expansion valve control section
(71a, 71b), the target degree of superheat is set at a certain
standard value (e.g., 5.degree. C.) except for the case where the
target degree of superheat is changed by the target superheat
degree changing section (65).
[0071] The target low pressure determining section (61) is
configured to perform target low pressure determining operation. In
the target low pressure determining operation, the target low
pressure, which is a target value of the low pressure of the
refrigeration cycle, is determined to correspond to a cooling load
of the indoor unit (12, 13) in the air cooling operation.
[0072] Specifically, the target low pressure determining section
(61) determines whether air cooling capability of the indoor unit
(12, 13) is sufficient or not based on the measurements of the room
air temperature sensors (55a, 55b), set room temperature for
cooling the room, etc. Then, when the target low pressure
determining section (61) has made a determination that the air
cooling capability of the indoor unit (12, 13) is insufficient, the
target low pressure is reduced to increase the air cooling
capability. When the target low pressure determining section (61)
has made a determination that the air cooling capability of the
indoor unit (12, 13) is excessive, the target low pressure is
increased to reduce the air cooling capability.
[0073] The compressor control section (63) is configured to perform
capacity control operation. In the capacity control operation,
operational capacity of the compressor (31) is adjusted in such a
manner that the measurement of the low pressure sensor (52) (i.e.,
an actual measurement of the low pressure of the refrigeration
cycle) reaches the target low pressure. Specifically, the
compressor control section (63) adjusts the operational capacity of
the compressor (31) using the low pressure of the refrigeration
cycle as a control parameter in such a manner that the control
parameter reaches the target low pressure.
[0074] Specifically, the compressor control section (63) changes a
frequency of alternating current fed to a motor of the compressor
(31) to change rotation speed of the compression mechanism driven
by the motor, thereby changing the operational capacity of the
compressor (31). When the measurement of the low pressure sensor
(52) is higher than the target low pressure, the compressor control
section (63) increases the rotation speed of the motor of the
compressor (31) to increase the operational capacity of the
compressor (31), thereby reducing the low pressure of the
refrigeration cycle. When the measurement of the low pressure
sensor (52) is lower than the target low pressure, the compressor
control section (63) reduces the rotation speed of the motor of the
compressor (31) to reduce the operational capacity of the
compressor (31), thereby increasing the low pressure of the
refrigeration cycle.
[0075] In this case, the compressor control section (63) calculates
a command value for changing a frequency of the alternating current
fed to the motor of the compressor (31) using the measurement of
the low pressure sensor (52) and the predetermined control gain.
Specifically, in the compressor control section (63), the command
value for changing the frequency of the alternating current is
increased as a difference between the measurement of the low
pressure sensor (52) and the target low pressure is increased.
Further, the command value for changing the frequency of the
alternating current is reduced as the difference between the
measurement of the low pressure sensor (52) and the target low
pressure is reduced.
[0076] When the measurement of the low pressure sensor (52) remains
lower than the target low pressure for a predetermined period of
time although the frequency of the alternating current fed to the
motor of the compressor (31) has reached the lower limit value, the
compressor control section (63) determines that the air cooling
capability is excessive relative to the cooling load, and stops the
compressor (31). Further, when a difference between the measurement
of the room air temperature sensor (55a, 55b) and the set room
temperature for cooling the room reaches or exceeds a certain
level, the compressor control section (63) determines that the air
inside the room has to be cooled, and starts the compressor
(31).
[0077] The target superheat degree changing section (65) is
configured to perform target superheat degree changing operation.
In the target superheat degree changing operation, the target
superheat degree changing section (65) counts the number of times
the compressor (31) is stopped by the compressor control section
(63). When the number of times the compressor is stopped by the
compressor control section (63) reaches the predetermined number
(e.g., two) within a predetermined period of time (e.g., in 15
minutes), the target superheat degree changing section (65)
forcibly increases the target degree of superheat from a standard
value (e.g., 5.degree. C.). After the target superheat degree
changing section (65) forcibly increased the target degree of
superheat, the indoor expansion valve control section (71a, 71b)
adjusts the degree of opening of the indoor expansion valve (42,
47) using the target degree of superheat increased from the
standard value.
[0078] However, when the degree of superheat of the refrigerant
flowing out of the indoor heat exchanger (41, 46) in the air
cooling operation is too high, the degree of superheat of the
refrigerant sucked into the compressor (31) may be too high, and
the temperature of the refrigerant discharged from the compressor
(31) may be too high. Therefore, the target superheat degree
changing section (65) sets an upper limit value on the increase in
target degree of superheat by the target superheat degree changing
operation to prevent the temperature of the refrigerant discharged
from the compressor (31) from being too high.
<Air Heating Operation>
[0079] Operation of the main controller (60) and the
sub-controllers (70a, 70b) in the air heating operation will be
described below. In the air heating operation, the target high
pressure determining section (62), the compressor control section
(63), the outdoor expansion valve control section (64), and the
target superheat degree changing section (65) of the main
controller (60) are operated, and the target low pressure
determining section (61) is suspended. In each of the
sub-controllers (70a, 70b), the indoor expansion valve control
section (71a, 71b) is operated.
[0080] The indoor expansion valve control section (71a, 71b) of
each of the sub-controllers (70a, 70b) adjusts the degree of
opening of the indoor expansion valve (42, 47) in the corresponding
indoor unit (12, 13). This operation is the same as that in the air
cooling operation. However, in the air heating operation, the
indoor expansion valve control section (71a, 71b) adjusts the
degree of opening of the indoor expansion valve (42, 47) in such a
manner that a detected value of the indoor liquid temperature
sensor (57, 57b) in the corresponding indoor unit (12, 13) reaches
the predetermined target value. Specifically, in the air heating
operation, the indoor expansion valve control section (71a, 71b)
adjusts the degree of opening of the indoor expansion valve (42,
47) in such a manner that the temperature of the refrigerant at the
exit of the indoor heat exchanger (41, 46) which functions as a gas
cooler reaches the predetermined target value. The control of the
degree of opening of the indoor expansion valve (42, 47) by the
indoor expansion valve control section (71a, 71b) is performed by
general feedback control, such as PID control etc.
[0081] Specifically, when the detected value of the indoor liquid
temperature sensor (57, 57b) is higher than the target value, the
indoor expansion valve control section (71a, 71b) reduces the
degree of opening of the indoor expansion valve (42, 47) to reduce
the flow rate of the refrigerant passing through the indoor heat
exchanger (41, 46), thereby reducing the temperature of the
refrigerant at the exit of the indoor heat exchanger (41, 46). When
the detected value of the indoor liquid temperature sensor (57,
57b) is lower than the target value, the indoor expansion valve
control section (71a, 71b) increases the degree of opening of the
indoor expansion valve (42, 47) to increase the flow rate of the
refrigerant passing through the indoor heat exchanger (41, 46),
thereby increasing the temperature of the refrigerant at the exit
of the indoor heat exchanger (41, 46).
[0082] The target high pressure determining section (62) is
configured to perform target high pressure determining operation.
In the target high pressure determining operation, the target high
pressure, which is a target value of the high pressure of the
refrigeration cycle, is determined to correspond to a heating load
of the indoor unit (12, 13) in the air heating operation.
[0083] Specifically, the target high pressure determining section
(62) determines whether the air heating capability of the indoor
unit (12, 13) is sufficient or not based on the measurements of the
room air temperature sensors (55a, 55b), the set room temperature
for heating the room, etc. When the target high pressure
determining section (62) has made a determination that the air
heating capability of the indoor unit (12, 13) is insufficient, the
target high pressure is increased to increase the air heating
capability. When the target high pressure determining section (62)
has made a determination that the air heating capability of the
indoor unit (12, 13) is excessive, the target high pressure is
reduced to reduce the air heating capability.
[0084] The compressor control section (63) is configured to perform
capacity control operation. In the capacity control operation,
operational capacity of the compressor (31) is adjusted in such a
manner that the measurement of the high pressure sensor (51) (i.e.,
an actual measurement of the high pressure of the refrigeration
cycle) reaches the target high pressure. Specifically, the
compressor control section (63) adjusts the operational capacity of
the compressor (31) using the high pressure of the refrigeration
cycle as a control parameter in such a manner that the control
parameter reaches the target high pressure.
[0085] Specifically, the compressor control section (63) changes a
frequency of alternating current fed to a motor of the compressor
(31) to change rotation speed of the compression mechanism driven
by the motor, thereby changing the operational capacity of the
compressor (31). When the measurement of the high pressure sensor
(51) is lower than the target high pressure, the compressor control
section (63) increases the rotation speed of the motor of the
compressor (31) to increase the operational capacity of the
compressor (31), thereby increasing the high pressure of the
refrigeration cycle. When the measurement of the high pressure
sensor (51) is higher than the target high pressure, the compressor
control section (63) reduces the rotation speed of the motor of the
compressor (31) to reduce the operational capacity of the
compressor (31), thereby reducing the high pressure of the
refrigeration cycle.
[0086] In this case, the compressor control section (63) calculates
a command value for changing a frequency of the alternating current
fed to the motor of the compressor (31) using the measurement of
the high pressure sensor (51) and the predetermined control gain.
Specifically, in the compressor control section (63), the command
value for changing the frequency of the alternating current is
increased as a difference between the measurement of the high
pressure sensor (51) and the target high pressure is increased.
Further, the command value for changing the frequency of the
alternating current is reduced as the difference between the
measurement of the high pressure sensor (51) and the target high
pressure is reduced.
[0087] The outdoor expansion valve control section (64) is
configured to perform flow rate control operation. In the flow rate
control operation, the degree of opening of the outdoor expansion
valve (34) is adjusted in such a manner that the degree of
superheat of the refrigerant at the exit of the outdoor heat
exchanger (33) which functions as the evaporator in the air heating
operation reaches the target degree of superheat. Specifically, the
outdoor expansion valve control section (64) adjusts the degree of
opening of the outdoor expansion valve (34) to control the flow
rate of the refrigerant passing through the outdoor expansion valve
(34). The control of the degree of opening of the outdoor expansion
valve (34) by the outdoor expansion valve control section (64) is
performed by general feedback control, such as PID control etc.
[0088] The outdoor expansion valve control section (64) calculates
the degree of superheat of the refrigerant at the exit of the
outdoor heat exchanger (33) by subtracting saturation temperature
of the refrigerant associated with a detected value of the low
pressure sensor (52) from a detected value of the outdoor gas
temperature sensor (54). Then, the degree of opening of the outdoor
expansion valve (34) is adjusted in such a manner that the
calculated degree of superheat reaches the target degree of
superheat. Specifically, when the calculated degree of superheat is
lower than the target degree of superheat, the outdoor expansion
valve control section (64) reduces the degree of opening of the
outdoor expansion valve (34) to reduce the flow rate of the
refrigerant passing through the outdoor heat exchanger (33),
thereby increasing the degree of superheat of the refrigerant at
the exit of the outdoor heat exchanger (33). When the calculated
degree of superheat is higher than the target degree of superheat,
the outdoor expansion valve control section (64) increases the
degree of opening of the outdoor expansion valve (34) to increase
the flow rate of the refrigerant passing through the outdoor heat
exchanger (33), thereby reducing the degree of superheat of the
refrigerant at the exit of the outdoor heat exchanger (33).
[0089] The target superheat degree changing section (65) is
configured to perform target superheat degree changing operation.
Specifically, like in the air cooling operation, the target
superheat degree changing section (65) forcibly increases the
target degree of superheat from a standard value (e.g., 5.degree.
C.) when the number of times the compressor is stopped by the
compressor control section (63) reaches the predetermined number
within a predetermined period of time. After the target superheat
degree changing section (65) forcibly increased the target degree
of superheat, the outdoor expansion valve control section (64)
adjusts the degree of opening of the outdoor expansion valve (34)
using the target degree of superheat increased from the standard
value.
[0090] However, when the degree of superheat of the refrigerant
flowing out of the outdoor heat exchanger (33) in the air heating
operation is too high, the degree of superheat of the refrigerant
sucked into the compressor (31) may be too high, and the
temperature of the refrigerant discharged from the compressor (31)
may be too high. Therefore, the target superheat degree changing
section (65) sets an upper limit value on the increase in target
degree of superheat by the target superheat degree changing
operation to prevent the temperature of the refrigerant discharged
from the compressor (31) from being too high.
Advantages of First Embodiment
[0091] In this embodiment, the target superheat degree changing
section (65) of the main controller (60) forcibly increases the
target degree of superheat from the standard value when the
capability of the air conditioner (10) is excessive, and a
frequency at which the compressor (31) is stopped by the compressor
control section (63) is increased. In the air cooling operation,
the indoor expansion valve control section (71a, 71b) of the
sub-controller (70a, 70b) adjusts the degree of opening of the
indoor expansion valve (42, 47) in such a manner that the degree of
superheat of the refrigerant flowing from the indoor heat exchanger
(41, 46) to the compressor (31) reaches the increased target degree
of superheat. In the air heating operation, the outdoor expansion
valve control section (64) of the main controller (60) adjusts the
degree of opening of the outdoor expansion valve (34) in such a
manner that the degree of superheat of the refrigerant flowing from
the outdoor heat exchanger (33) to the compressor (31) reaches the
increased target degree of superheat.
[0092] Provided that the temperature and flow rate of the air sent
to the evaporator are constant, the degree of superheat of the
refrigerant at the exit of the evaporator is increased as the flow
rate of the refrigerant passing through the evaporator is reduced.
Thus, the degrees of opening of the indoor expansion valves (42,
47) and the outdoor expansion valve (34) are reduced as the target
degree of superheat is increased. Specifically, the indoor
expansion valves (42, 47) and the outdoor expansion valve (34) are
brought into the state where the flow rate of the refrigerant
passing through them is reduced (i.e., the state where the degrees
of opening are set low). Thus, with the rotation speed of the
compression mechanism of the compressor (31) kept constant, the
amount of the refrigerant circulating in the refrigerant circuit
(20) is reduced as the target degree of superheat is increased,
thereby reducing the capability of the air conditioner (10).
[0093] Specifically, the lower limit value of the capability of the
air conditioner (10) is reduced as the target degree of superheat
is increased. Therefore, the compressor (31), which would have to
be stopped by the compressor control section (63) before the target
degree of superheat is increased, is more likely to be continuously
operated after the target degree of superheat is increased.
[0094] Thus, according to the present embodiment, in the air
conditioner (10) which performs the so-called supercritical cycle,
the possibility that the compressor (31) is stopped due to the
excessive capability of the air conditioner (10) relative to the
load can be reduced. Specifically, in the air conditioner (10)
which performs the supercritical cycle in which "high energy is
consumed until the high pressure and the low pressure of the
refrigeration cycle reach the appropriate values after the
compressor (31) is started," the number of times the compressor
(31) is started and stopped for capability adjustment can be
reduced. Therefore, according to the present embodiment, the number
of times the compressor (31) is started and stopped for capability
adjustment is reduced, thereby reducing the power consumed while
the air conditioner (10) is operated, and improving operation
efficiency of the air conditioner (10).
Second Embodiment of the Invention
[0095] A second embodiment of the invention will be described. This
embodiment is the same as the first embodiment except that the
structure of the main controller (60) of the air conditioner (10)
is changed.
[0096] As shown in FIG. 3, the main controller (60) of the present
embodiment includes a target control value changing section (66) in
place of the target superheat degree changing section (65)
described in the first embodiment. In the main controller (60) of
the present embodiment, the target low pressure determining section
(61), the target high pressure determining section (62), the
compressor control section (63), and the outdoor expansion valve
control section (64) are operated in the same manner as described
in the first embodiment.
[0097] The target control value changing section (66) is configured
to perform target control value changing operation. In the target
control value changing operation, the target control value changing
section (66) counts the number of times the compressor (31) is
stopped by the compressor control section (63). When the number of
times the compressor is stopped by the compressor control section
(63) reaches the predetermined number (e.g., two) within a
predetermined period of time (e.g., 15 minutes), the target control
value changing section (66) forcibly changes a target control value
used in the compressor control section (63).
<Operation Mechanism in Air Cooling Operation>
[0098] In the air cooling operation, the target control value
changing section (66) performs operation of forcibly changing the
target low pressure as the target control value changing operation.
Specifically, when the number of times the compressor is stopped by
the compressor control section (63) reaches the predetermined
number within the predetermined period of time, the target control
value changing section (66) increases the target low pressure used
in the compressor control section (63) from a standard target value
which is determined by the target low pressure determining section
(61). Then, at a point of time when the compressor (31) is started,
the compressor control section (63) adjusts operational capacity of
the compressor (31) using the target low pressure increased by the
target control value changing section (66). Then, the compressor
control section (63) gradually reduces the target low pressure in
such a manner that the target low pressure reaches the standard
target value at a point of time when the predetermined period of
time (e.g., 4 minutes) has passed from the start of the compressor
(31).
[0099] Immediately after the start of the compressor (31), there is
a big difference between the measurement of the low pressure sensor
(52) and the standard target value. Thus, when the target low
pressure is not changed from the standard target value immediately
after the start of the compressor (31), the capacity of the
compressor (31) is abruptly increased to bring the measurement of
the low pressure sensor (52) close to the standard target value as
soon as possible. When the air cooling capability of the air
conditioner (10) is abruptly increased due to the abrupt increase
in capacity of the compressor (31), the room temperature becomes
lower than the set temperature in a relatively short time after the
start of the compressor (31), and the compressor (31) has to be
stopped again.
[0100] In contrast, according to the target control value changing
section (66) of the present embodiment, the target low pressure is
set higher than the standard target value for some time after the
start of the compressor (31). Thus, even immediately after the
start of the compressor (31), a difference between the measurement
of the low pressure sensor (52) and the target low pressure is
smaller than a difference between the measurement and the target
low pressure which is not changed from the standard target value.
This alleviates the abrupt increase in capacity of the compressor
(31) after the start of the compressor (31), thereby gently
changing the air cooling capability of the air conditioner (10).
Thus, with the target low pressure set higher than the standard
target value by the target control value changing section (66)
according to the present embodiment, the compressor (31), which
would have to be stopped by the compressor control section (63)
when the target low pressure is not changed from the standard
target value, is more likely to be continuously operated.
<Operation Mechanism in Air Heating Operation>
[0101] In the air heating operation, the target control value
changing section (66) performs operation of forcibly changing the
target high pressure as the target control value changing
operation. Specifically, when the number of times the compressor is
stopped by the compressor control section (63) reaches the
predetermined number in the predetermined period of time, the
target control value changing section (66) reduces the target high
pressure used in the compressor control section (63) from a
standard target value determined by the target high pressure
determining section (62). Then, at a point of time when the
compressor (31) is started, the compressor control section (63)
adjusts the operational capacity of the compressor (31) using the
target high pressure reduced by the target control value changing
section (66). Then, the compressor control section (63) gradually
increases the target high pressure in such a manner that the target
high pressure reaches the standard target value at a point of time
when a predetermined period of time (e.g., 4 minutes) has passed
from the start of the compressor (31).
[0102] Immediately after the start of the compressor (31), there is
a big difference between the measurement of the high pressure
sensor (51) and the standard target value. Thus, when the target
high pressure is not changed from the standard target value
immediately after the start of the compressor (31), the capacity of
the compressor (31) is abruptly increased to bring the measurement
of the high pressure sensor (51) close to the standard target value
as soon as possible. When the air heating capability of the air
conditioner (10) is abruptly increased due to the abrupt increase
in capacity of the compressor (31), the room temperature exceeds
the set temperature in a relatively short time after the start of
the compressor (31), and the compressor (31) has to be stopped
again.
[0103] In contrast, according to the target control value changing
section (66) of the present embodiment, the target high pressure is
set lower than the standard target value for some period of time
after the start of the compressor (31). Thus, even immediately
after the start of the compressor (31), a difference between the
measurement of the high pressure sensor (51) and the target high
pressure is smaller than a difference between the measurement and
the target high pressure which is not changed from the standard
target value. This alleviates the abrupt increase in capacity of
the compressor (31) after the start of the compressor (31), thereby
gently changing the air heating capability of the air conditioner
(10). Thus, with the target high pressure set lower than the
standard target value by the target control value changing section
(66) according to the present embodiment, the compressor (31),
which would have to be stopped by the compressor control section
(63) when the target high pressure is not changed from the standard
target value, is more likely to be continuously operated.
Advantages of Second Embodiment
[0104] According to the present embodiment, in the air conditioner
(10) which performs the so-called supercritical cycle, the
possibility that the compressor (31) is stopped due to the
excessive capability of the air conditioner (10) relative to the
load can be reduced. Thus, according to the present embodiment,
like in the first embodiment described above, the number of times
the compressor (31) is started and stopped for capability
adjustment is reduced, thereby reducing power consumed while the
air conditioner (10) is operated, and improving the operation
efficiency of the air conditioner (10).
Alternative Example of Second Embodiment
[0105] The compressor control section (63) of the present
embodiment may be configured to use, as a control parameter in the
air cooling operation, evaporating temperature of the refrigerant
in the indoor heat exchanger (41, 46) which functions as an
evaporator. In the main controller (60) of this alternative
example, the target low pressure determining section (61) is
replaced with a target evaporating temperature determining section.
The target evaporating temperature determining section determines
target evaporating temperature of the refrigerant in the indoor
heat exchanger (41, 46) based on the cooling load of the air
conditioner (10). Further, as the target control value changing
operation in the air cooling operation, the target control value
changing section (66) of this alternative example increases the
target evaporating temperature used in the compressor control
section (63) from a standard target value determined by the target
evaporating temperature determining section, and gradually reduces
the target evaporating temperature in such a manner that the target
evaporating temperature reaches the standard target value at a
point of time when a predetermined period of time has passed after
the start of the compressor (31).
Third Embodiment of the Invention
[0106] A third embodiment of the invention will be described. The
present embodiment is the same as the first embodiment except that
the structure of the main controller (60) of the air conditioner
(10) is changed.
[0107] As shown in FIG. 4, the main controller (60) of the present
embodiment includes a gain adjustment section (67) in place of the
target superheat degree changing section (65) of the first
embodiment. In the main controller (60) of the present embodiment,
the target low pressure determining section (61), the target high
pressure determining section (62), the compressor control section
(63), and the outdoor expansion valve control section (64) are
operated in the same manner as described in first embodiment.
[0108] The gain adjustment section (67) is configured to perform
gain adjustment operation. In the gain adjustment operation, the
gain adjustment section (67) adjusts a control gain used in the
compressor control section (63) in accordance with a difference
between the measurement of the outdoor air temperature sensor (58)
(i.e., an actual measurement of outside temperature) and the set
room temperature.
[0109] In the air cooling operation, the gain adjustment section
(67) compares the measurement of the outdoor air temperature sensor
(58) and the set room temperature. In the air cooling operation,
the cooling load for cooling the room is reduced as a value
obtained by subtracting the set room temperature from the
measurement of the outdoor air temperature sensor (58) is reduced.
Therefore, the gain adjustment section (67) sets the control gain
used in the compressor control section (63) smaller as the value
obtained by subtracting the set room temperature from the
measurement of the outdoor air temperature sensor (58) is
smaller.
[0110] In the air cooling operation, the compressor control section
(63) of the present embodiment adjusts the capacity of the
compressor (31) using the small control gain set by the gain
adjustment section (67). Specifically, the compressor control
section (63) calculates a command value for changing a frequency of
alternating current fed to the motor of the compressor (31) using a
difference between the measurement of the low pressure sensor (52)
and the target low pressure, and the control gain. With the
difference between the measurement of the low pressure sensor (52)
and the target low pressure kept constant, the command value for
changing the frequency of the alternating current is reduced as the
control gain is reduced in the compressor control section (63).
[0111] Also in the air heating operation, the gain adjustment
section (67) compares the measurement of the outdoor air
temperature sensor (58) and the set room temperature. In the air
heating operation, the heating load for heating the room is reduced
as the value obtained by subtracting the measurement of the outdoor
air temperature sensor (58) from the set room temperature is
reduced. Thus, the gain adjustment section (67) sets the control
gain used in the compressor control section (63) smaller as the
value obtained by subtracting the measurement of the outdoor air
temperature sensor (58) from the set room temperature is
smaller.
[0112] In the air heating operation, the compressor control section
(63) of the present embodiment adjusts the capacity of the
compressor (31) using the small control gain set by the gain
adjustment section (67). Specifically, the compressor control
section (63) calculates a command value for changing a frequency of
alternating current fed to the motor of the compressor (31) using a
difference between the measurement of the high pressure sensor (51)
and the target high pressure, and the control gain. With the
difference between the measurement of the high pressure sensor (51)
and the target high pressure kept constant, the command value for
changing the frequency of the alternating current is reduced as the
control gain is reduced in the compressor control section (63).
[0113] When the control gain used in the compressor control section
(63) remains high although the load of the air conditioner (10) is
reduced, the command value for changing the frequency of the
alternating current obtained based on the difference between the
measurement of the low pressure sensor (52) and the target low
pressure, or the difference between the measurement of the high
pressure sensor (51) and the target high pressure is increased. As
a result, the capability of the air conditioner (10) becomes
excessive relative to the load, and the compressor (31) is more
likely to be stopped.
[0114] In contrast, the gain adjustment section (67) of the present
embodiment reduces the control gain as the load of the air
conditioner (10) is reduced. Thus, the command value calculated
based on the measurement of the low pressure sensor (52) or the
high pressure sensor (51), and the control gain is reduced as
compared with the case where the control gain is constant.
Therefore, with the control gain reduced by the gain adjustment
section (67) according to the present embodiment, the compressor
(31), which would have to be stopped by the compressor control
section (63) when the control gain is constant, is more likely to
be continuously operated.
Advantages of Third Embodiment
[0115] According to the present embodiment, in the air conditioner
(10) which performs the so-called supercritical cycle, the
compressor (31) is less likely to be stopped due to the excessive
capability of the air conditioner (10) relative to the load. Thus,
according to the present embodiment, like the first embodiment, the
number of times the compressor (31) is started and stopped for
capability adjustment is reduced, thereby reducing power consumed
while the air conditioner (10) is operated, and improving the
operation efficiency of the air conditioner (10).
INDUSTRIAL APPLICABILITY
[0116] As described above, the present invention is useful for a
refrigeration apparatus which performs a refrigeration cycle in
which high pressure is set higher than critical pressure of the
refrigerant.
* * * * *