U.S. patent number RE43,998 [Application Number 12/654,828] was granted by the patent office on 2013-02-19 for refrigeration/air conditioning equipment.
This patent grant is currently assigned to Mitsubishi Electric Corporation. The grantee listed for this patent is Masanori Aoki, Tetsuji Saikusa, Makoto Saitou, Fumitake Unezaki, Masato Yosomiya. Invention is credited to Masanori Aoki, Tetsuji Saikusa, Makoto Saitou, Fumitake Unezaki, Masato Yosomiya.
United States Patent |
RE43,998 |
Aoki , et al. |
February 19, 2013 |
Refrigeration/air conditioning equipment
Abstract
Refrigeration/air conditioning equipment includes a first
internal heat exchanger for exchanging heat between a refrigerant
to be sucked in a compressor and a high-pressure liquid
refrigerant, an injection circuit for evaporating a bypassed
high-pressure liquid at intermediate pressure and injecting the
vaporized refrigerant into the compressor, a second internal heat
exchanger for exchanging heat between the high-pressure liquid
refrigerant and the refrigerant to be injected, and a heat source
for heating the refrigerant to be injected.
Inventors: |
Aoki; Masanori (Tokyo,
JP), Yosomiya; Masato (Tokyo, JP), Unezaki;
Fumitake (Tokyo, JP), Saitou; Makoto (Tokyo,
JP), Saikusa; Tetsuji (Tokyo, JP) |
Applicant: |
Name |
City |
State |
Country |
Type |
Aoki; Masanori
Yosomiya; Masato
Unezaki; Fumitake
Saitou; Makoto
Saikusa; Tetsuji |
Tokyo
Tokyo
Tokyo
Tokyo
Tokyo |
N/A
N/A
N/A
N/A
N/A |
JP
JP
JP
JP
JP |
|
|
Assignee: |
Mitsubishi Electric Corporation
(Chiyoda-Ku, Tokyo, JP)
|
Family
ID: |
35788032 |
Appl.
No.: |
12/654,828 |
Filed: |
January 5, 2010 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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Reissue of: |
11251788 |
Oct 18, 2005 |
7316120 |
Jan 8, 2008 |
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Foreign Application Priority Data
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Oct 18, 2004 [JP] |
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2004-303077 |
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Current U.S.
Class: |
62/324.4; 62/504;
62/513 |
Current CPC
Class: |
F25B
13/00 (20130101); F25B 40/00 (20130101); F25B
41/35 (20210101); F25B 2600/2513 (20130101); F25B
2313/008 (20130101); F25B 2400/054 (20130101); F25B
1/10 (20130101); F25B 2700/2117 (20130101); F25B
2400/053 (20130101); F25B 2600/0271 (20130101); F25B
41/39 (20210101); F25B 2500/31 (20130101); Y02B
30/70 (20130101); F25B 2700/21151 (20130101); F25B
2400/16 (20130101); F25B 2700/21152 (20130101); F25B
2400/13 (20130101); F25B 2600/2509 (20130101); F25B
41/385 (20210101) |
Current International
Class: |
F25B
13/00 (20060101) |
Field of
Search: |
;62/513,126,504,324.1,324.4,160,225,237.7,238.7 |
References Cited
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Primary Examiner: Ali; Mohammad
Attorney, Agent or Firm: Buchanan Ingersoll & Rooney
PC
Claims
What is claimed is:
1. Refrigeration/air conditioning equipment comprising: a
compressor; a four-way valve; an indoor heat exchanger; a first
decompressor; and an outdoor heat exchanger, wherein these
components are coupled circularly, and heat is supplied from the
indoor heat exchanger, the refrigeration/air conditioning equipment
further comprising: an intermediate-pressure receiver disposed
between the indoor heat exchanger and the first decompressor; a
first internal heat exchanger that exchanges heat between a
refrigerant in the intermediate-pressure receiver and a refrigerant
in a suction pipe of the compressor; and an injection circuit in
which part of a refrigerant between the indoor heat exchanger and
the first decompressor is bypassed and is injected into a
compression chamber in the compressor, the injection circuit
comprising: a second decompressor; a second internal heat exchanger
that exchanges heat between a refrigerant having a pressure reduced
by the second decompressor and the refrigerant between the indoor
heat exchanger and the first decompressor; and a heat source for
heating a refrigerant, disposed between the second internal heat
exchanger and the compressor.
2. The refrigeration/air conditioning equipment according to claim
1, wherein a third decompressor is provided between the indoor heat
exchanger and the intermediate-pressure receiver.
3. The refrigeration/air conditioning equipment according to claim
1, further comprising a controller for controlling the degree of
superheat of a refrigerant sucked into the compressor or the degree
of superheat of a refrigerant at the outlet of the outdoor hear
exchanger to a predetermined value by adjusting the first
decompressor.
4. The refrigeration/air conditioning equipment according to claim
1, further comprising a controller for controlling the discharge
temperature or the degree of superheat of a refrigerant at the
outlet of the compressor to a predetermined value by adjusting the
second decompressor.
5. The refrigeration/air conditioning equipment according to claim
2, further comprising a controller for controlling the degree of
supercooling of a refrigerant at the outlet of the indoor heat
exchanger to a predetermined value by adjusting the third
decompressor.
6. The refrigeration/air conditioning equipment according to claim
2, further comprising a controller for controlling the degree of
superheat of a refrigerant sucked into the compressor or the degree
of superheat of a refrigerant at the outlet of the outdoor hear
exchanger to a predetermined value by adjusting the first
decompressor.
7. The refrigeration/air conditioning equipment according to claim
2, further comprising a controller for controlling the discharge
temperature or the degree of superheat of a refrigerant at the
outlet of the compressor to a predetermined value by adjusting the
second decompressor.
.Iadd.8. Heating equipment, comprising: a first heat exchanger that
makes a refrigerant absorb heat of air; a compressor that sucks the
refrigerant from the first heat exchanger; a second heat exchanger
that provides a load side medium with heat of the refrigerant
discharged from the compressor; a first expansion valve that
decompresses the refrigerant flowing from the second heat exchanger
to the first heat exchanger, the first heat exchanger, compressor,
second heat exchanger and first expansion valve being connected so
as to circulate the refrigerant; a third heat exchanger that
exchanges heat between the refrigerant flowing from an outlet of
the second heat exchanger to an inlet of the first heat exchanger
and the refrigerant flowing from the first heat exchanger toward a
suction inlet of the compressor; an injection circuit that merges
part of the refrigerant flowing from the second heat exchanger to
the first heat exchanger with the refrigerant that is sucked by the
compressor via the first heat exchanger to be compressed to an
intermediate pressure; a second expansion valve that is installed
in the injection circuit and decompresses the refrigerant flowing
in the injection circuit; a fourth heat exchanger that is installed
in the injection circuit to supply heat of the refrigerant flowing
from the second heat exchanger toward the first heat exchanger to
the refrigerant flowing toward an injection inlet of the compressor
in the injection circuit; and a controller that controls an opening
degree of the first and the second expansion valves..Iaddend.
.Iadd.9. The heating equipment of claim 8, wherein the controller
controls the second expansion valve so that the refrigerant flowing
in the injection circuit becomes a gas-liquid two phase
state..Iaddend.
.Iadd.10. The heating equipment of claim 8, wherein the injection
circuit branches from between the second heat exchanger and the
first expansion valve..Iaddend.
.Iadd.11. The heating equipment of claim 10, wherein the injection
circuit branches from between the third heat exchanger and the
fourth heat exchanger..Iaddend.
.Iadd.12. The heating equipment of claim 8 comprising: a third
expansion valve provided between the second heat exchanger and the
third heat exchanger to be controlled by the
controller..Iaddend.
.Iadd.13. The heating equipment of claim 12, wherein the third heat
exchanger has a receiver provided with a function to store part of
the refrigerant flowing from the second heat exchanger to the first
heat exchanger, and exchanges heat between the refrigerant stored
within the receiver and the refrigerant flowing from the first heat
exchanger to the compressor..Iaddend.
.Iadd.14. The heating equipment of claim 13, wherein the third
expansion valve decompresses the refrigerant flowing from the
second heat exchanger to the receiver..Iaddend.
.Iadd.15. The heating equipment of claim 8, wherein the second heat
exchanger is a condenser..Iaddend.
.Iadd.16. The heating equipment of claim 8, wherein the load side
medium that exchanges heat with the refrigerant discharged from the
compressor in the second heat exchanger is air..Iaddend.
.Iadd.17. The heating equipment of claim 8, wherein the load side
medium that exchanges heat with the refrigerant discharged from the
compressor in the second heat exchanger is water..Iaddend.
.Iadd.18. The heating equipment of claim 8 comprising a temperature
sensor that detects a discharge temperature of the refrigerant
discharged from the compressor, wherein the controller controls an
opening degree of the second expansion valve to be large so as to
decrease enthalpy of the refrigerant when the discharge temperature
detected by the temperature sensor is higher than a target value,
and controls the opening degree of the second expansion valve to be
small so as to increase enthalpy of the refrigerant when the
discharge temperature is lower than the target value..Iaddend.
.Iadd.19. An outdoor unit of heating equipment including a first
heat exchanger that makes a refrigerant absorb heat of air, a
compressor that sucks the refrigerant from the first heat exchanger
and discharges the refrigerant to a second heat exchanger that is
externally installed, and a first expansion valve that decompresses
the refrigerant flowing toward the first heat exchanger after
providing a load side medium with heat in the second heat
exchanger, comprising a third heat exchanger that exchanges heat
between the refrigerant flowing from an outlet of the second heat
exchanger toward an inlet of the first heat exchanger and the
refrigerant flowing from the first heat exchanger toward a suction
inlet the compressor; an injection circuit that merges part of the
refrigerant flowing from the second heat exchanger toward the first
heat exchanger with the refrigerant that is sucked by the
compressor via the first heat exchanger to be compressed to an
intermediate pressure; a second expansion valve that is installed
in the injection circuit and decompresses the refrigerant flowing
in the injection circuit; a fourth heat exchanger that is installed
in the injection circuit to supply heat of the refrigerant flowing
from the second heat exchanger toward the first heat exchanger to
the refrigerant flowing toward an injection inlet of the compressor
in the injection circuit; and a controller that controls an opening
degree of the first and the second expansion valves..Iaddend.
.Iadd.20. The outdoor unit of heating equipment of claim 19,
wherein the controller controls the second expansion valve so that
the refrigerant flowing in the injection circuit becomes a
gas-liquid two phase state..Iaddend.
.Iadd.21. The outdoor unit of heating equipment of claim 19,
wherein the injection circuit branches from between the second heat
exchanger and the first expansion valve..Iaddend.
.Iadd.22. The outdoor unit of heating equipment of claim 21,
wherein the injection circuit branches from between the third heat
exchanger and the fourth heat exchanger..Iaddend.
.Iadd.23. The outdoor unit of heating equipment of claim 19
comprising: a third expansion valve provided between the second
heat exchanger and the third heat exchanger to be controlled by the
controller..Iaddend.
.Iadd.24. The outdoor unit of heating equipment of claim 23,
wherein the third heat exchanger has a receiver having a function
to store part of a refrigerant flowing from the second heat
exchanger to the first heat exchanger, and exchanges heat between
the refrigerant stored in the receiver and the refrigerant flowing
from the first heat exchanger to the compressor..Iaddend.
.Iadd.25. The outdoor unit of heating equipment of claim 24,
wherein the third expansion valve decompresses the refrigerant
flowing from the second heat exchanger to the
receiver..Iaddend.
.Iadd.26. The outdoor unit of heating equipment of claim 19,
wherein the second heat exchanger is a condenser..Iaddend.
.Iadd.27. The outdoor unit of heating equipment of claim 19,
wherein the load side medium that exchanges heat with the
refrigerant discharged from the compressor in the second heat
exchanger is air..Iaddend.
.Iadd.28. The outdoor unit of heating equipment of claim 19,
wherein the load side medium that exchanges heat with the
refrigerant discharged from the compressor in the second heat
exchanger is water..Iaddend.
.Iadd.29. The outdoor unit of heating equipment of claim 19
including a temperature sensor that detects a discharge temperature
of the refrigerant discharged from the compressor, wherein the
controller controls an opening degree of the second expansion valve
to be large so as to decrease enthalpy of the refrigerant when the
discharge temperature detected by the temperature sensor is higher
than a target value and controls the opening degree of the second
expansion valve to be small so as to increase enthalpy of the
refrigerant when the discharge temperature is lower than the target
value..Iaddend.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to refrigeration/air conditioning
equipment, and particularly to refrigeration/air conditioning
equipment in which the heating capacity at low outdoor temperature
is improved by gas injection, and a defrosting operation is
performed efficiently.
2. Description of the Related Art
Japanese Unexamined Patent Application Publication No. 2001-304714
discloses refrigeration/air conditioning equipment including a
gas-liquid separator in an intermediate-pressure portion between a
condenser and an evaporator. A gas refrigerant separated by the
gas-liquid separator is injected into an intermediate-pressure
portion of a compressor to increase the heating capacity.
Japanese Unexamined Patent Application Publication No. 2000-274859
discloses another conventional refrigeration/air conditioning
equipment without a gas-liquid separator. In this equipment, part
of a high-pressure liquid refrigerant is bypassed, is decompressed,
is vaporized through heat exchange with the high-pressure liquid
refrigerant. The vaporized refrigerant is injected into a
compressor to increase the heating capacity.
Japanese Unexamined Patent Application Publication No. 2001-263882
discloses still another conventional refrigeration/air conditioning
equipment, in which a heater for heating a refrigerant is provided
to improve the efficiency in a defrosting operation.
However, these pieces of conventional refrigeration/air
conditioning equipment have the following problems.
First, as described in the Japanese Unexamined Patent Application
Publication No. 2001-304714, when the injection is performed with
the gas-liquid separator, the fluid volume in the gas-liquid
separator varies with the amount of the injection. This variation
causes fluctuations in the distribution of a liquid refrigerant
level in a refrigeration cycle and makes the operation
unstable.
When the flow rate of a gas refrigerant to be injected is
substantially equal to the flow rate of a gas refrigerant in a
two-phase refrigerant flowing into the gas-liquid separator, only
the liquid refrigerant flows out to an evaporator and therefore the
liquid refrigerant level in the gas-liquid separator is
substantially constant. However, when the flow rate of the gas
refrigerant to be injected is smaller than that of the gas
refrigerant flowing into the gas-liquid separator, the gas
refrigerant also flows out to the evaporator from the bottom of the
gas-liquid separator. Thus, most of the liquid refrigerant in the
gas-liquid separator flows out. Conversely, when the flow rate of
the refrigerant to be injected increases and the gas refrigerant
becomes deficient, the liquid refrigerant is also injected into the
compressor. Thus, the liquid refrigerant flows out from the top of
the gas-liquid separator, and the gas-liquid separator is almost
filled with the liquid refrigerant.
The injection flow rate tends to vary, for example, with the
pressure of the refrigeration cycle, the pressure of the gas-liquid
separator, or the operation capacity of the compressor. Thus, the
injection flow rate hardly balances with the flow rate of the gas
refrigerant flowing into the gas-liquid separator. Actually, the
liquid refrigerant level in the gas-liquid separator tends to vary
with the operation and be almost zero or full. This variation often
causes fluctuations in the distribution of the refrigerant in the
refrigeration cycle, making the operation unstable. Furthermore,
the heater as in the Japanese Unexamined Patent Application
Publication No. 2001-263882 is only used in a defrosting operation
and does not contribute significantly to the increase in the
capacity during a heating operation.
SUMMARY OF THE INVENTION
In view of these problems, it is an object of the present invention
to provide refrigeration/air conditioning equipment that has a
higher heating capacity than conventional gas injection cycles, and
exhibits a sufficient heating capacity even in a cold district
where the outdoor temperature is -10.degree. C. or lower, and also
to increase the efficiency during the defrosting operation.
Refrigeration/air conditioning equipment according to the present
invention includes:
a compressor;
a four-way valve;
an indoor heat exchanger;
a first decompressor; and
an outdoor heat exchanger,
wherein these components are coupled circularly, and heat is
supplied from the indoor heat exchanger,
and the refrigeration/air conditioning equipment further
includes:
an intermediate-pressure receiver disposed between the indoor heat
exchanger and the first decompressor;
a first internal heat exchanger that exchanges heat between a
refrigerant in the intermediate-pressure receiver and a refrigerant
in a suction pipe of the compressor; and
an injection circuit in which part of a refrigerant between the
indoor heat exchanger and the first decompressor is bypassed and is
injected into a compression chamber in the compressor,
wherein the injection circuit includes: a second decompressor; a
second internal heat exchanger that exchanges heat between a
refrigerant having a pressure reduced by the second decompressor
and the refrigerant between the indoor heat exchanger and the first
decompressor; and a heat source for heating a refrigerant disposed
between the second internal heat exchanger and the compressor.
Thus, even when a high flow rate of the gas refrigerant is
injected, sufficient heating capacity can be provided even under
such a condition as the heating capacity tends to decrease owing to
low outdoor temperature or the like, by preventing the reduction in
the discharge temperature of the compressor and allowing the indoor
heat exchanger to exhibit sufficient heat-exchange performance.
According to the present invention, the gas refrigerant to be
injected is supplied not from the gas-liquid separator but through
the gasification of the bypassed refrigerant with the second
internal heat exchanger. Thus, the variation in the fluid volume
caused by the gas-liquid separator can be avoided. Thus, more
stable operation can be achieved. In addition, the gas injection
can be increased while the reduction in the discharge temperature
of the compressor is prevented. Thus, the heating capacity is
further increased, and the efficiency during the defrosting
operation is improved.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a refrigerant circuit diagram of refrigeration/air
conditioning equipment according to Embodiment 1 of the present
invention;
FIG. 2 is a PH diagram showing the heating operation of the
refrigeration/air conditioning equipment according to Embodiment 1
of the present invention;
FIG. 3 is a PH diagram showing the cooling operation of the
refrigeration/air conditioning equipment according to Embodiment 1
of the present invention;
FIG. 4 is a flow chart showing the control action during the
heating operation of the refrigeration/air conditioning equipment
according to Embodiment 1 of the present invention;
FIG. 5 is a flow chart showing the control action during the
cooling operation of the refrigeration/air conditioning equipment
according to Embodiment 1 of the present invention;
FIG. 6 is a PH diagram showing the operation of the
refrigeration/air conditioning equipment according to Embodiment 1
of the present invention in the presence of gas injection;
FIG. 7 is a diagram showing the temperature change of a condenser
in the refrigeration/air conditioning equipment according to
Embodiment 1 of the present invention in the presence of gas
injection;
FIG. 8 is a diagram showing the operation characteristics of the
refrigeration/air conditioning equipment according to Embodiment 1
of the present invention as a function of the gas-injection flow
rate;
FIG. 9 is a diagram showing the operation characteristics of the
refrigeration/air conditioning equipment according to Embodiment 1
of the present invention with or without a first internal heat
exchanger;
FIG. 10 is another diagram showing the operation characteristics of
the refrigeration/air conditioning equipment according to
Embodiment 1 of the present invention as a function of the
gas-injection flow rate;
FIG. 11 is a flow chart showing the control action during the
heating and defrosting operation of the refrigeration/air
conditioning equipment according to Embodiment 1 of the present
invention; .[.and.].
FIG. 12 is a diagram showing the defrosting operation
characteristics of the refrigeration/air conditioning equipment
according to Embodiment 1 of the present invention with or without
a first internal heat exchanger and means for heating a
refrigerant.Iadd.; and.Iaddend.
.Iadd.FIG. 13 is a refrigeration circuit diagram which shows the
load side medium that exchanges heat with the refrigerant
discharged from the compressor in the second heat exchanger being
water.Iaddend..
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Embodiment 1
FIG. 1 is a refrigerant circuit diagram of refrigeration/air
conditioning equipment of Embodiment 1 according to the present
invention. In FIG. 1, an outdoor unit 1 includes a compressor 3, a
four-way valve 4 for switching between heating and cooling, an
outdoor heat exchanger 12, a first expansion valve 11 serving as a
first decompressor, a second internal heat exchanger 10, a third
expansion valve 8 serving as a third decompressor, an injection
circuit 13, a second expansion valve 14 serving as a second
decompressor, an intermediate-pressure receiver 9, and a heat
source 17 for heating a refrigerant. A suction pipe 18 of the
compressor 3 passes through the intermediate-pressure receiver 9.
Thus, a refrigerant in this through-pipe 18a of the suction pipe 18
can exchange heat with a refrigerant 9a in the
intermediate-pressure receiver 9. The heat source 17 heats a
refrigerant circulating through the injection circuit 13.
The capacity of the compressor 3 can be controlled by adjusting the
number of revolutions with an inverter. The compressor 3 is
designed such that the refrigerant supplied from the injection
circuit 13 can be injected into a compression chamber in the
compressor 3. The first expansion valve 11, the second expansion
valve 14, and the third expansion valve 8 are electronic expansion
valves whose degree of opening is variable. The outdoor heat
exchanger 12 exchanges heat with the outside air sent by a fan or
the like. An indoor unit 2 includes an indoor heat exchanger 6. A
gas pipe 5 and a liquid pipe 7 are connecting pipes to connect the
outdoor unit 1 and the indoor unit 2. The refrigeration/air
conditioning equipment uses a mixed HFC-based refrigerant, R410A as
a refrigerant.
The outdoor unit 1 includes a controller 15 and temperature sensors
16. A first temperature sensor 16a is disposed at the discharge
side of the compressor 3, a second temperature sensor 16b is
disposed between the outdoor heat exchanger 12 and the four-way
valve 4, a third temperature sensor 16c is disposed on a
refrigerant pass in a intermediate portion of the outdoor heat
exchanger 12, a fourth temperature sensor 16d is disposed between
the outdoor heat exchanger 12 and the first expansion valve 11, a
fifth temperature sensor 16e is disposed between the
intermediate-pressure receiver 9 and the third expansion valve 8,
and a sixth temperature sensor 16f is disposed at the suction side
of the compressor 3. These temperature sensors measure the
refrigerant temperatures at their respective installation
locations. A seventh temperature sensor 16g measures the outdoor
temperature around the outdoor unit 1.
An eighth temperature sensor 16h, a ninth temperature sensor 16i,
and a tenth temperature sensor 16j are disposed in the indoor unit
2. The eighth temperature sensor 16h is disposed on a refrigerant
pass in an intermediate portion of the indoor heat exchanger 6, and
the ninth temperature sensor 16i is disposed between the indoor
heat exchanger 6 and the liquid pipe 7. These temperature sensors
measure the refrigerant temperatures at their respective
installation locations. The tenth temperature sensor 16j measures
the temperature of air sucked into the indoor heat exchanger 6.
When the load medium is another medium, such as water, the tenth
temperature sensor 16j measures the temperature of the medium
flowing into the indoor heat exchanger 6.
The third temperature sensor 16c and the eighth temperature sensor
16h measures the temperatures of the refrigerant in a gas-liquid
two phase in the intermediate portion of each heat exchanger, and
thereby can determine the saturation temperatures of the
refrigerant under high pressure and low pressure.
The metering and control system 15 in the outdoor unit 1 controls
the operational mode of the compressor 3, pass switching of the
four-way valve 4, the amount of air sent by a fan in the outdoor
heat exchanger 12, and the degrees of opening of the first
expansion valve, the second expansion valve, and the third
expansion valve according to the measured information of the
temperature sensors 16a to 16j and operating conditions instructed
by a user of the refrigeration/air conditioning equipment.
The operation of the refrigeration/air conditioning equipment will
be described below. First, the heating operation will be described
with reference to the refrigerant circuit diagram shown in FIG. 1
and the PH diagram of the heating operation shown in FIG. 2. In the
heating operation, the flow pass of the four-way valve 4 is set in
the direction of the dotted line shown in FIG. 1. A
high-temperature high-pressure gas refrigerant (FIG. 2, point 1)
discharged from the compressor 3 flows out from the outdoor unit 1
via the four-way valve 4, and flows into the indoor unit 2 through
the gas pipe 5. The gas refrigerant flows into the indoor heat
exchanger 6, which serves as a condenser, loses its heat, and is
condensed to a high-pressure low-temperature liquid refrigerant
(FIG. 2, point 2). The heat radiating from the refrigerant is
transferred to the load medium, such as air or water, which heats
the room. The high-pressure low-temperature refrigerant flowing out
from the indoor heat exchanger 6 flows into the outdoor unit 1
through the liquid pipe 7 and is slightly decompressed with the
third expansion valve 8 (FIG. 2, point 3), changing into a
gas-liquid two-phase refrigerant, which flows into the
intermediate-pressure receiver 9. The two-phase refrigerant
transfers heat to a low-temperature refrigerant that is to be
sucked into the compressor 3 in the intermediate-pressure receiver
9, is cooled into a liquid phase (FIG. 2, point 4), and flows out
from the intermediate-pressure receiver 9. One part of the liquid
refrigerant is bypassed through the injection circuit 13, is
decompressed, and is decreased in temperature through the second
expansion valve 14. The other part of the liquid refrigerant is
further cooled by the heat exchange with the bypassed refrigerant
in the second internal heat exchanger 10 (FIG. 2, point 5). The
other part of the liquid refrigerant is decompressed in the first
expansion valve 11 and changes into a two-phase refrigerant (FIG.
2, point 6). Then, the two-phase refrigerant flows into the outdoor
heat exchanger 12, which serves as an evaporator, and absorbs heat
to vaporize (FIG. 2, point 7). The gas refrigerant flows through
the four-way valve 4, is heated by heat exchange with the
high-pressure refrigerant in the intermediate-pressure receiver 9
(FIG. 2, point 8), and is sucked into the compressor 3.
On the other hand, the refrigerant bypassed through the injection
circuit 13 is decompressed to an intermediate pressure with the
second expansion valve 14 and changes into a low-temperature
two-phase refrigerant (FIG. 2, point 9). Then, the low-temperature
two-phase refrigerant exchanges heat with the high-pressure
refrigerant in the second internal heat exchanger 10, is heated by
the heat source 17 (FIG. 2, point 10), and is injected into the
compressor 3. In the compressor 3, the sucked refrigerant (FIG. 2,
point 8) is compressed to an intermediate pressure, is heated (FIG.
2, point 11), and is merged into the injected refrigerant. The
merged refrigerant having a reduced temperature (FIG. 2, point 12)
is compressed to a high pressure and is discharged (FIG. 2, point
1). The heat source 17 for heating a refrigerant can adjust the
amount of heat when necessary.
Next, the cooling operation will be described with reference to the
refrigerant circuit diagram shown in FIG. 1 and the PH diagram of
the cooling operation shown in FIG. 3. In the cooling operation,
the flow pass of the four-way valve 4 is set in the direction of
the solid line shown in FIG. 1. A high-temperature high-pressure
gas refrigerant (FIG. 3, point 1) discharged from the compressor 3
flows into the outdoor heat exchanger 12, which serves as a
condenser, via the four-way valve 4. The gas refrigerant loses its
heat and is condensed to a high-pressure low-temperature
refrigerant (FIG. 3, point 2). The high-pressure low-temperature
refrigerant flowing out from the outdoor heat exchanger 12 is
slightly decompressed with the first expansion valve 11 (FIG. 3,
point 3). The refrigerant is cooled by heat exchange with a
low-temperature refrigerant flowing through the injection circuit
13 in the second internal heat exchanger 10 (FIG. 3, point 4). One
part of the refrigerant is bypassed through the injection circuit
13. The other part of the refrigerant is cooled by the heat
exchange with the refrigerant that is to be sucked into the
compressor 3 in the intermediate-pressure receiver 9 (FIG. 3, point
5). The other part of the refrigerant is decompressed to a low
pressure in the third expansion valve 8, changing into a two-phase
refrigerant (FIG. 3, point 6). Then, the refrigerant flows from the
outdoor unit 1 to the indoor unit 2 through the liquid pipe 7.
Then, the two-phase refrigerant flows into the indoor heat
exchanger 6, which serves as an evaporator. The refrigerant absorbs
heat to evaporate (FIG. 3, point 7) while it supplies cold energy
to the load medium, such as air or water, in the indoor unit 2. The
low-pressure gas refrigerant flowing out from the indoor heat
exchanger 6 flows from the indoor unit 2 to the outdoor unit 1
through the gas pipe 5. The gas refrigerant flows through the
four-way valve 4, is heated by heat exchange with the high-pressure
refrigerant in the intermediate-pressure receiver 9 (FIG. 3, point
8), and is sucked into the compressor 3.
On the other hand, the refrigerant bypassed through the injection
circuit 13 is decompressed to an intermediate pressure with the
second expansion valve 14 and changes into a low-temperature
two-phase refrigerant (FIG. 3, point 9). Then, the low-temperature
two-phase refrigerant exchanges heat with the high-pressure
refrigerant in the second internal heat exchanger 10, is heated in
the heat source 17 (FIG. 3, point 10), and is injected into the
compressor 3. In the compressor 3, the sucked refrigerant (FIG. 3,
point B) is compressed to an intermediate pressure, is heated (FIG.
3, point 11), and is merged into the injected refrigerant. The
merged refrigerant having a reduced temperature (FIG. 3, point 12)
is again compressed to a high pressure and is discharged (FIG. 3,
point 1). The heat source 17 for heating a refrigerant can adjust
the amount of heat when necessary.
The PH diagram of the cooling operation is almost identical with
that of the heating operation. Thus, similar operations can be
achieved in both operation modes.
The control action of the refrigeration/air conditioning equipment
will be explained below. First, the control action in the heating
operation will be described with reference to FIG. 4. FIG. 4 is a
flow chart showing the control action in the heating operation. In
the heating operation, the capacity of the compressor 3, the degree
of opening of the first expansion valve 11, the degree of opening
of the second expansion valve 14, and the degree of opening of the
third expansion valve 8 are set to initial values at step S1. At
step S2, after the expiration of a predetermined time, each
actuator is controlled as follows in a manner that depends on its
operational status. The capacity of the compressor 3 is basically
controlled such that the air temperature measured with the tenth
temperature sensor 16j in the indoor unit 2 is equal to a
temperature set by a user of the refrigeration/air conditioning
equipment.
In other words, the air temperature of the indoor unit 2 is
compared with the set temperature at step S3. When the air
temperature is the same as or close to the set temperature, the
capacity of the compressor 3 is maintained to proceed to the step
S5. When the air temperature is different from the set temperature,
the capacity of the compressor 3 is adjusted at step S4 in the
following manner. When the air temperature is much lower than the
set temperature, the capacity of the compressor 3 is increased.
When the air temperature is much higher than the set temperature,
the capacity of the compressor 3 is decreased.
Each expansion valve is controlled in the following manner. The
third expansion valve 8 is controlled such that the degree of
supercooling SC of the refrigerant at the outlet of the indoor heat
exchanger 6, which is obtained from the difference between the
saturation temperature of the high-pressure refrigerant measured by
the eighth temperature sensor 16h and the outlet temperature of the
indoor heat exchanger 6 measured by the ninth temperature sensor
16i, is equal to a predetermined target value, for example,
10.degree. C. The degree of supercooling SC of the refrigerant at
the outlet of the indoor heat exchanger 6 is compared with the
target value at step S5. When the degree of supercooling SC of the
refrigerant is greater than the target value at the step S5, the
degree of opening of the third expansion valve 8 is increased at
step 6. When the degree of supercooling SC of the refrigerant is
smaller than the target value at the step 5, the degree of opening
of the third expansion valve 8 is decreased at the step S6.
The first expansion valve 11 is controlled such that the degree of
superheat SH of the refrigerant sucked into the compressor 3, which
is obtained from the difference between the suction temperature of
the compressor 3 measured by the sixth temperature sensor 16f and
the saturation temperature of the low-pressure refrigerant measured
by the third temperature sensor 16c, is equal to a predetermined
target value, for example, 10.degree. C. In other words, the degree
of superheat SH of the refrigerant, which is the temperature of the
refrigerant sucked into the compressor 3, is compared with the
target value at step S7. When the degree of superheat SH of the
refrigerant sucked into the compressor 3 is equal or close to the
target value, the degree of opening of the first expansion valve 11
is maintained to proceed to the next step S9. When the degree of
superheat SH is different from the target value, the degree of
opening of the first expansion valve 11 is changed at step S8 in
the following manner. When the degree of superheat SH of the
refrigerant sucked into the compressor 3 is greater than the target
value, the degree of opening of the first expansion valve 11 is
increased, and when the degree of superheat SH of the refrigerant
is smaller than the target value, the degree of opening of the
first expansion valve 11 is decreased.
Next, the second expansion valve 14 is controlled such that the
discharge temperature of the compressor 3 measured by the first
temperature sensor 16a is equal to a predetermined target value,
for example, 90.degree. C. In other words, the discharge
temperature of the compressor 3 is compared with the target value
at step S19. When the discharge temperature of the compressor 3 is
equal or close to the target value at the step S9, the degree of
opening of the second expansion valve 14 is maintained and the
operation loops back to the step 2.
When the degree of opening of the second expansion valve 14 is
changed, the state of the refrigerant changes as follows. When the
degree of opening of the second expansion valve 14 increases, the
flow rate of the refrigerant flowing into the injection circuit 13
increases. The amount of heat exchanged in the second internal heat
exchanger 10 does not change significantly with the flow rate of
the refrigerant in the injection circuit 13. Thus, when the flow
rate of the refrigerant flowing through the injection circuit 13
increases, the enthalpy difference of the refrigerant (FIG. 2,
difference between point 9 and point 10) in the injection circuit
13 at the second internal heat exchanger 10 decreases. Thus, the
enthalpy of the refrigerant to be injected (FIG. 2, point 10)
decreases.
Accordingly, after the injected refrigerant is merged, the enthalpy
of the refrigerant (FIG. 2, point 12) decreases. This also
decreases the enthalpy and the temperature of the refrigerant
discharged from the compressor 3 (FIG. 2, point 1). Conversely,
when the degree of opening of the second expansion valve 14
decreases, the enthalpy and the temperature of the refrigerant
discharged from the compressor 3 increase. Thus, the degree of
opening of the second expansion valve 14 is controlled at step S10
such that when the discharge temperature of the compressor 3 is
higher than a target value, the degree of opening of the second
expansion valve 14 is increased, and when the discharge temperature
is lower than the target value, the degree of opening of the second
expansion valve 14 is decreased. Then, the operation loops back to
the step 2.
Next, the control action during the cooling operation will be
described with reference to FIG. 5. FIG. 5 is a flow chart showing
the control action in the cooling operation. In the cooling
operation, the capacity of the compressor 3, the degree of opening
of the first expansion valve 11, the degree of opening of the
second expansion valve 14, and the degree of opening of the third
expansion valve 8 are set to initial values at step S11. At step
S12, after the expiration of a predetermined time, each actuator is
controlled as follows in a manner that depends on its operational
status.
First, the capacity of the compressor 3 is basically controlled
such that the air temperature measured with the tenth temperature
sensor 16j in the indoor unit 2 is equal to a temperature set by a
user of the refrigeration/air conditioning equipment. In other
words, the air temperature of the indoor unit 2 is compared with
the set temperature at step S13. When the air temperature is the
same as or close to the set temperature, the capacity of the
compressor 3 is maintained to proceed to step S15. When the air
temperature is different from the set temperature the capacity of
the compressor 3 is adjusted at step S14 in the following manner.
When the air temperature is much higher than the set temperature,
the capacity of the compressor 3 is increased. When the air
temperature is lower than the set temperature, the capacity of the
compressor 3 is decreased.
Each expansion valve is controlled in the following manner. The
first expansion valve 11 is controlled such that the degree of
supercooling SC of the refrigerant at the outlet of the outdoor
heat exchanger 12, which is obtained from the difference between
the saturation temperature of the high-pressure refrigerant
measured by the temperature sensor 16c and the outlet temperature
of the outdoor heat exchanger 12 measured by the temperature sensor
16d, is equal to a predetermined target value, for example,
10.degree. C. In other words, the degree of supercooling SC of the
refrigerant at the outlet of the outdoor heat exchanger 12 is
compared with the target value at step S15. When the degree of
supercooling SC at the outlet of the outdoor heat exchanger 12 is
equal or close to the target value, the degree of opening of the
first expansion valve 11 is maintained to proceed to the next step
S17. The degree of opening of the first expansion valve 11 is
changed at step S16 such that when the degree of supercooling SC at
the outlet of the outdoor heat exchanger 12 is greater than the
target value, the degree of opening of the first expansion valve 11
is increased, and when the degree of supercooling SC of the
refrigerant is smaller than the target value, the degree of opening
of the first expansion valve 11 is decreased.
Next, the third expansion valve 8 is controlled such that the
degree of superheat SH of the refrigerant sucked into the
compressor 3, which is obtained from the difference between the
suction temperature of the compressor 3 measured by the sixth
temperature sensor 16f and the saturation temperature of the
low-pressure refrigerant measured by the eight temperature sensor
16h, is equal to a predetermined target value, for example,
10.degree. C. In other words, the degree of superheat SH of the
refrigerant sucked into the compressor 3 is compared with the
target value at step S17. When the degree of superheat SH of the
refrigerant sucked into the compressor 3 is equal or close to the
target value, the degree of opening of the third expansion valve 8
is maintained to proceed to the next step S19. When the degree of
superheat SH is different from the target value, the degree of
opening of the third expansion valve 8 is changed at step S18 such
that when the degree of superheat SH of the refrigerant sucked into
the compressor 3 is greater than the target value, the degree of
opening of the third expansion valve 8 is increased, and when the
degree of superheat SH of the refrigerant is smaller than the
target value, the degree of opening of the third expansion valve B
is decreased.
Next, the second expansion valve 14 is controlled such that the
discharge temperature of the compressor 3 measured by the first
temperature sensor 16a is equal to a predetermined target value,
for example, 90.degree. C. In other words, the discharge
temperature of the compressor 3 is compared with the target value
at step S19. When the discharge temperature of the compressor 3 is
equal or close to the target value, the degree of opening of the
second expansion valve 14 is maintained and the operation loops
back to the step 12. The variations in the state of the refrigerant
at the time when the degree of opening of the second expansion
valve 14 is changed are similar to those in the heating operation.
Thus, the degree of opening of the second expansion valve 14 is
controlled such that when the discharge temperature of the
compressor 3 is higher than the target value, the degree of opening
of the second expansion valve 14 is increased, and when the
discharge temperature is lower than the target value, the degree of
opening of the second expansion valve 14 is decreased. Then, the
operation loops back to the step S12.
Next, the circuitry of the Embodiment 1 and operations and effects
achieved by the controls will be described. Since both the cooling
operation and the heating operation can be performed in a similar
way in this equipment, the heating operation is representatively
described below. The circuitry of the equipment is a so-called gas
injection circuit. In other words, after the refrigerant flows out
from the indoor heat exchanger 6, which serves as a condenser, and
is decompressed to an intermediate pressure, a gas component of the
refrigerant is injected into a compressor 3.
In typical refrigeration/air conditioning equipment, the
intermediate-pressure refrigerant is often separated into liquid
and gas with a gas-liquid separator and is then injected. However,
in the refrigeration/air conditioning equipment according to this
embodiment, as shown in FIG. 6, the refrigerant is thermally
separated into liquid and gas by heat exchange in the second
internal heat exchanger 10, and is then injected.
The gas injection circuit has the following effects. The gas
injection increases the flow rate of the refrigerant discharged
from the compressor 3: the flow rate of the refrigerant discharged
from the compressor 3 Gdis=the flow rate of the refrigerant sucked
into the compressor 3 Gsuc+the flow rate of the injected
refrigerant Ginj. This increases the flow rate of the refrigerant
flowing into the heat exchanger, which serves as a condenser, and
thereby increases the heating capacity in the heating
operation.
On the other hand, as shown in FIG. 6, the heat exchange in the
second internal heat exchanger 10 decreases the enthalpy of the
refrigerant flowing into the heat exchanger, which serves as an
evaporator. Thus, the difference in the enthalpy of the refrigerant
in the evaporator increases. Accordingly, the cooling capacity also
increases in the cooling operation.
Furthermore, the gas injection also improves the efficiency. The
refrigerant flowing into the heat exchanger, which serves as an
evaporator, is generally a gas-liquid two-phase refrigerant, the
gas component of which does not contribute to cooling capacity.
However, the compressor 3 does work of increasing the pressure of
this low-pressure gas refrigerant, in addition to the gas
refrigerant vaporized in the evaporator. In the gas injection, part
of the gas refrigerant flowing into the evaporator is drawn at an
intermediate pressure, is injected into the compressor 3, and is
compressed from the intermediate pressure to high pressure. Thus,
there is no need to compress the gas refrigerant to be injected
from low pressure to intermediate pressure. This improves the
efficiency. This effect can be achieved in both the heating
operation and the cooling operation.
Next, the correlation between the gas-injection flow rate and the
heating capacity will be described. When the gas-injection flow
rate is increased, as described above, the flow rate of the
refrigerant discharged from the compressor 3 increases, but the
discharge temperature of the compressor 3 decreases, and the
temperature of the refrigerant flowing into the indoor heat
exchanger 6, which serves as a condenser, also decreases. In terms
of the heat-exchange performance of the condenser, the amount of
exchanged heat generally increases as the temperature distribution
in the heat exchanger extends. FIG. 7 shows the changes in the
refrigerant temperature at the time when the condensation
temperatures are the same but the refrigerant temperatures at the
inlet of the condenser are different. The temperature distributions
at a portion where the refrigerant in the condenser is in a
superheated gas state are different.
In the condenser, although the amount of heat exchanged in the
refrigerant in a two-phase state at the condensation temperature
dominates, the amount of heat exchanged at a portion where the
refrigerant is in a superheated gas state accounts for about 20% to
30% of the total amount of exchanged heat and has a significant
impact on the amount of exchanged heat. If an injection flow rate
is too high and the refrigerant temperature at a portion where the
refrigerant is in a superheated gas state lowers drastically,
heat-exchange performance in the condenser will decrease, resulting
in low heating capacity. FIG. 8 shows the correlation between the
gas-injection flow rate and the heating capacity. The heating
capacity reaches the maximum at a certain gas-injection flow
rate.
Next, operations and effects of heat exchange in the
intermediate-pressure receiver 9 between the refrigerant 9a for
exchanging heat and the through-pipe 18a in the suction pipe 18 of
the compressor 3 according to the Embodiment 1 will be described.
In the heating operation, the gas-liquid two-phase refrigerant
flows into the intermediate-pressure receiver 9 from the third
expansion valve 8. The gas-liquid two-phase refrigerant is cooled
by the heat exchange between the through-pipe 18a in the suction
pipe 18 of the compressor 3 and the refrigerant 9a in the
intermediate-pressure receiver 9, and flows out as a liquid
refrigerant. In the cooling operation, the gas-liquid two-phase
refrigerant at the outlet of the second internal heat exchanger 10
flows into the intermediate-pressure receiver 9, is cooled, and
flows out as a liquid refrigerant. Thus, the enthalpy of the
refrigerant flowing into the indoor heat exchanger 6, which serves
as an evaporator, decreases. This increases the difference in the
enthalpy of the refrigerant in the evaporator. Accordingly, the
cooling capacity also increases in the cooling operation.
On the other hand, the refrigerant to be sucked into the compressor
3 is heated, and the suction temperature increases. This also
increases the discharge temperature of the compressor 3. In the
compression stroke of the compressor 3, the compression of the
refrigerant having a higher temperature generally requires a
greater amount of work for the same pressure increase. Thus, the
effect on the efficiency of the heat exchange in the
intermediate-pressure receiver 9 between the refrigerant 9a for
exchanging heat and the through-pipe 18a in the suction pipe 18 of
the compressor 3 influences both the increase in the performance
due to the greater enthalpy difference in the evaporator and the
increase in work of compression. When the increase in the
performance due to the greater enthalpy difference in the
evaporator has a greater influence, the operational efficiency of
the equipment increases.
The heat exchange in the intermediate-pressure receiver between the
refrigerant 9a and the through-pipe 18a in the suction pipe 18 is
mainly performed by a gas refrigerant in the gas-liquid two-phase
refrigerant coming into contact with the through-pipe 18a in the
suction pipe 18 and condensing into liquid. Thus, when the liquid
refrigerant left in the intermediate-pressure receiver 9 decreases,
the contact area between the gas refrigerant and the through-pipe
18a in the suction pipe 18 increases. This increases the amount of
heat exchanged. Conversely, when the liquid refrigerant left in the
intermediate-pressure receiver 9 increases, the contact area
between the gas refrigerant and the through-pipe 18a in the suction
pipe 18 decreases. This decreases the amount of heat exchanged.
Thus, the intermediate-pressure receiver 9 has the following
effects. First, since the refrigerant flowing out the
intermediate-pressure receiver 9 is liquid, the refrigerant flowing
into the second expansion valve 14 in the heating operation is
always a liquid refrigerant. This stabilizes the flow rate of the
second expansion valve 14 and ensures stable control and stable
operation.
Furthermore, the heat exchange in the intermediate-pressure
receiver 9 stabilizes the pressure of the intermediate-pressure
receiver 9, the inlet pressure of the second expansion valve 14,
and the flow rate of the refrigerant flowing into the injection
circuit 13. For example, load fluctuations and associated
fluctuations in the high pressure side cause fluctuations in the
pressure of the intermediate-pressure receiver 9. The heat exchange
in the intermediate-pressure receiver 9 reduces such pressure
fluctuations. When the load increases and the high pressure
increases, the pressure of the intermediate-pressure receiver 9
also increases. This increases the pressure difference from the low
pressure. This also increases the temperature difference in the
heat exchange in the intermediate-pressure receiver 9, thus
increasing the amount of exchanged heat. The increase in the amount
of exchanged heat enhances the condensation of the gas component of
the gas-liquid two-phase refrigerant flowing into the
intermediate-pressure receiver 9, thus suppressing the pressure
increase. Thus, the pressure increase of the intermediate-pressure
receiver 9 is prevented. Conversely, when the load decreases and
the high pressure decreases, the pressure of the
intermediate-pressure receiver 9 also decreases. This reduces the
pressure difference from the low pressure. This also reduces the
temperature difference in the heat exchange in the
intermediate-pressure receiver 9, thus decreasing the amount of
exchanged heat. The decrease in the amount of exchanged heat
prevents the condensation of the gas component of the gas-liquid
two-phase refrigerant flowing into the intermediate-pressure
receiver 9, suppressing the pressure decrease. Thus, the pressure
decrease of the intermediate-pressure receiver 9 is prevented.
In this way, the heat exchange in the intermediate-pressure
receiver 9 autonomously generates variations in the amount of
exchanged heat, following the fluctuations in the operational
status. This prevents the pressure fluctuations of the
intermediate-pressure receiver 9.
Furthermore, the heat exchange in the intermediate-pressure
receiver 9 stabilizes the operation of the equipment. For example,
when the state of the low-pressure side changes and the degree of
superheat of the refrigerant at the outlet of the outdoor heat
exchanger 12 serving as an evaporator increases, the temperature
difference in the heat exchange in the intermediate-pressure
receiver 9 decreases. Thus, the amount of heat exchanged decreases,
and therefore the gas refrigerant is hardly condensed. This
increases the gas refrigerant level and decreases the liquid
refrigerant level in the intermediate-pressure receiver 9. The
decrement of the liquid refrigerant is carried over into the
outdoor heat exchanger 12, increasing the liquid refrigerant level
in the outdoor heat exchanger 12. This suppresses the increase in
the degree of superheat of the refrigerant at the outlet of the
outdoor heat exchanger 12, thus suppressing the operational
fluctuations of the equipment. Conversely, when the state of the
low-pressure side changes and the degree of superheat of the
refrigerant at the outlet of the outdoor heat exchanger 12 serving
as an evaporator decreases, the temperature difference in the heat
exchange in the intermediate-pressure receiver 9 increases. Thus,
the amount of exchanged heat increases, and therefore the gas
refrigerant is easily condensed. This decreases the gas refrigerant
level and increases the liquid refrigerant level in the
intermediate-pressure receiver 9. The increment of the liquid
refrigerant is derived from the outdoor heat exchanger 12, thus
decreasing the liquid refrigerant level in the outdoor heat
exchanger 12. This suppresses the decrease in the degree of
superheat of the refrigerant at the outlet of the outdoor heat
exchanger 12, thus suppressing the operational fluctuations of the
equipment.
The suppression of the fluctuations in the degree of superheat also
results from autonomous generation of the variations in the amount
of exchanged heat, following the fluctuations in the operational
status, through the heat exchange in the intermediate-pressure
receiver 9.
Next, as in the Embodiment 1, the effect of the heat exchange in
the intermediate-pressure receiver 9 in combination with the gas
injection from the injection circuit 13 will be described. The heat
exchange in the intermediate-pressure receiver 9 increases the
suction temperature of the compressor 3. Thus, in terms of the
change in the compressor 3 in the presence of the injection, the
enthalpy of the refrigerant compressed from a low pressure to an
intermediate pressure (FIG. 2 and FIG. 3, point 11) increases, and
the enthalpy of the refrigerant after the injected refrigerant is
merged (FIG. 2 and FIG. 3, point 12) also increases. Thus, the
discharge enthalpy of the compressor 3 (FIG. 2 and FIG. 3, point 1)
also increases, and the discharge temperature of the compressor 3
increases. FIG. 9 shows the change in the correlation between the
gas-injection flow rate and the heating capacity, depending on the
presence of the heat exchange in the intermediate-pressure receiver
9. In the presence of the heat exchange in the
intermediate-pressure receiver 9, the discharge temperature of the
compressor 3 is higher than that in the absence of the heat
exchange at the same injection level. This higher discharge
temperature also increases the temperature of the refrigerant at
the inlet of the condenser, the amount of heat exchanged in the
condenser, and the heating capacity. Accordingly, the injection
flow rate at the peak of the heating capacity increases. This also
increases the peak value of the heating capacity, thus improving
the heating capacity.
When further increase in the heating capacity is desired, a heat
source 17 for heating a refrigerant, such as an electric heater, is
provided in the injection circuit 13. The heat source 17 can
suppress the decrease in the discharge temperature of the
compressor 3 and increase the injection flow rate. The heat source
17 can also increase the peak value of the heating capacity, as
shown in FIG. 9.
Furthermore, even in the absence of the heat exchange in the
intermediate-pressure receiver 9, the degree of superheat at the
inlet of the compressor 3 and the discharge temperature of the
compressor 3 can be increased by controlling the degree of opening
of the first expansion valve 11. However, in this case, the degree
of superheat of the refrigerant at the outlet of the outdoor heat
exchanger 12, which serves as an evaporator, is also increased.
This decreases the heat exchange efficiency of the outdoor heat
exchanger 12. When the heat exchange efficiency of the outdoor heat
exchanger 12 decreases, the evaporation temperature must be
decreased to achieve the same amount of exchanged heat. Thus, the
low pressure is decreased in the operation. The decrease in the low
pressure also decreases the flow rate of the refrigerant sucked
into the compressor 3. Thus, such an operation contrarily decreases
the heating capacity. Conversely, in the presence of the heat
exchange in the intermediate-pressure receiver 9, the refrigerant
at the outlet of the outdoor heat exchanger 12, which serves as an
evaporator, is maintained in an appropriate state. Thus, the
discharge temperature of the compressor 3 can be increased with
excellent heat exchange efficiency. Thus, the decrease in the low
pressure as described above can be avoided, and the heating
capacity can be easily increased.
Furthermore, in the circuitry of the Embodiment 1, part of the
high-pressure refrigerant is bypassed, is decompressed, is
superheated into a gas in the second internal heat exchanger 10,
and is injected. Thus, as compared with conventional equipment in
which a gas separated with a gas-liquid separator is injected, the
distribution of the refrigerant does not fluctuate when the
injection level changes in response to the variations in control or
operational status. Thus, more stable operation can be
achieved.
In terms of the structure for performing the heat exchange in the
intermediate-pressure receiver 9, any structure can achieve a
similar effect, provided that the heat is exchanged with the
refrigerant in the intermediate-pressure receiver 9. For example,
the suction pipe of the compressor 3 may be in contact with the
outer periphery of the intermediate-pressure receiver 9 for heat
exchange.
Furthermore, the refrigerant supplied to the injection circuit 13
may be supplied from the bottom of the intermediate-pressure
receiver 9. In this case, in both the cooling operation and the
heating operation, a liquid refrigerant flows into the second
expansion valve 14. Thus, the flow rate at the second expansion
valve 14 is consistent. This ensures the control stability.
As described above, the second expansion valve 14 is controlled
such that the discharge temperature of the compressor 3 is equal to
the target value. This target value is determined to provide the
maximum heating capacity. As shown in FIG. 9, on the basis of the
correlation among the gas-injection flow rate, the heating
capacity, and the discharge temperature, there is a discharge
temperature at which the heating capacity reaches the maximum.
Thus, this discharge temperature is previously determined and is
employed as the target value. The target value of the discharge
temperature is not necessarily a constant value. The target value
may be changed as required in a manner that depends on the
operating condition or characteristics of an apparatus, such as a
condenser. In this way, the gas injection level can be adjusted to
achieve the maximum heating capacity by controlling the discharge
temperature.
The gas injection level can be adjusted not only to achieve the
maximum heating capacity, but also to achieve the maximum
operational efficiency. When a large heating capacity is required,
for example, during the startup of the refrigeration/air
conditioning equipment, the gas injection level is adjusted to
achieve the maximum heating capacity. When the room temperature has
increased after the equipment operates for a certain period of time
and large heating capacity is no longer required, the gas injection
level is adjusted to achieve the maximum efficiency. FIG. 10 shows
the correlation among the injection flow rate, the heating
capacity, and the operational efficiency. At the maximum
operational efficiency, the injection flow rate is smaller and the
discharge temperature is higher than those at the maximum heating
capacity. At the injection flow rate at which the heating capacity
reaches the maximum, since the discharge temperature is lower, the
heat-exchange performance of the condenser decreases. In addition,
because the intermediate pressure is decreased to increase the
injection flow rate, work of compressing the injected refrigerant
increases. Thus, the efficiency is lower than that at the maximum
operational efficiency.
Thus, as a target value of the discharge temperature controlled
with the second expansion valve 14, not only a target value that
provides the maximum heating capacity, but also a target value that
provides the maximum operational efficiency are taken into
consideration. According to the operational conditions, for
example, the operation capacity of the compressor 3 or the air
temperature of the indoor unit side, when the heating capacity is
required, the target value that provides the maximum heating
capacity is specified, and when the heating capacity is not
required, the target value that provides the maximum operational
efficiency is specified. Such an operation can achieve both large
heating capacity and efficient operation.
As described above, the first expansion valve 11 is controlled to
adjust the degree of superheat at the inlet of the compressor 3 to
the target value. Such control can optimize the degree of superheat
at the outlet of the heat exchanger, which serves as an evaporator,
ensuring excellent heat-exchange performance of the evaporator. In
addition, such control can moderately ensure the difference in the
enthalpy of the refrigerant, allowing the operation with high
efficiency. While the degree of superheat at the outlet of the
evaporator that allows such an operation depends on the
characteristics of the heat exchanger, it is about 2.degree. C.
Since the refrigerant is further heated by the
intermediate-pressure receiver 9, the target value of the degree of
superheat at the inlet of the compressor 3 is larger than this
value. For example, the target value is 10.degree. C., as described
above.
Thus, the first expansion valve 11 may be controlled such that the
degree of superheat at the outlet of the evaporator, or in the case
of the heating operation the degree of superheat at the outlet of
the outdoor heat exchanger 12 obtained from the temperature
difference between the second temperature sensor 16b and the third
temperature sensor 16c is equal to the target value, for example,
2.degree. C. as described above. However, when the degree of
superheat at the outlet of the evaporator is directly controlled
and the target value is as low as about 2.degree. C., the
refrigerant at the outlet of the evaporator is transiently in a
gas-liquid two phase, which prevents appropriate determination of
the degree of superheat. This makes the control difficult. When the
degree of superheat at the inlet of the compressor 3 is detected,
the target value can be increased. Furthermore, the heating in the
intermediate-pressure receiver 9 prevents the sucked refrigerant
from being in gas-liquid two phase, and thereby prevents
inappropriate detection of the degree of superheat. This makes the
control easier and stable.
As described above, the third expansion valve 8 is controlled to
adjust the degree of supercooling at the outlet of the indoor heat
exchanger 6, which serves as a condenser, to the target value. Such
control can ensure excellent heat-exchange performance in the
condenser and moderately ensure the difference in the enthalpy of
the refrigerant, allowing the operation with high efficiency. While
the degree of supercooling at the outlet of the condenser that
allows such an operation depends on the characteristics of the heat
exchanger, it is about 5.degree. C. to 10.degree. C. Furthermore,
the target value of the degree of supercooling may be higher than
this value. For example, the target value of about 10.degree. C. to
15.degree. C. allows the operation with increased heating capacity.
Thus, the target value of the degree of supercooling may be changed
in a manner that depends on the operational conditions. During the
startup of the equipment, the target value of the degree of
supercooling may be slightly higher to ensure high heating
capacity. At a steady state at room temperature, the target value
of the degree of supercooling may be slightly lower for the
efficient operation.
The refrigerant of the refrigeration/air conditioning equipment is
not limited to R410A and may be another refrigerant.
Furthermore, the positions of the intermediate-pressure receiver 9
and the second internal heat exchanger 10 are not limited to those
in the refrigerant circuitry shown in FIG. 1. Even when the
positional relationship between the upstream and the downstream is
reversed, a similar effect can be obtained. Furthermore, the
position from which the injection circuit 13 is drawn is not
limited to that in the refrigerant circuitry shown in FIG. 1. A
similar effect can be obtained for any position, provided that the
injection circuit 13 can be drawn from another
intermediate-pressure portion and a high-pressure liquid portion.
In view of the control stability of the second expansion valve 14,
the position from which the injection circuit 13 is drawn is
desirably the position at which the refrigerant is completely in a
liquid phase rather than in a gas-liquid two phase.
In this Embodiment 1, the intermediate-pressure receiver 9, the
second internal heat exchanger 10, and the injection circuit 13 are
disposed between the first expansion valve 11 and the third
expansion valve 8. Thus, in both the cooling operation and the
heating operation, a similar injection can be performed.
While the saturation temperatures of the refrigerant are measured
with the refrigerant temperature sensors in the middle of the
condenser and the evaporator, pressure sensors that can sense high
pressure and low pressure may be provided to determine the
saturation temperatures from the measured pressures.
FIG. 11 is a flow chart showing the control action during the
heating and defrosting operation of the refrigeration/air
conditioning equipment. In FIG. 11, the heating operation as
described above is performed, and at step S21 the capacity of the
compressor 3, the degree of opening of the first expansion valve
11, the degree of opening of the second expansion valve 14, and the
degree of opening of the third expansion valve 8 are set to initial
values. At step S22, after the expiration of a predetermined time,
each actuator is controlled as follows on the basis of its
operational status. The capacity of the compressor 3 is basically
controlled such that an outdoor piping temperatures measured with
the second temperature sensor 16b, the third temperature sensor
16c, and the fourth temperature sensor 16d in the outdoor unit 1
are equal to a temperature set by a user of the refrigeration/air
conditioning equipment.
In other words, the outdoor piping temperature of the outdoor unit
1 is compared with the set temperature at step S23. When the
outdoor piping temperature is equal to or less than the set
temperature (for example, -5.degree. C.), it is concluded that
frost forms on the outdoor heat exchanger 12, which serves as an
evaporator. Then, the four-way valve is rotated to start a
defrosting operation at step S24. To be more specific, the
defrosting operation is performed by passing a high-pressure
high-temperature refrigerant discharged from the compressor 3
through the outdoor heat exchanger 12, as in the cooling cycle.
While the decrease in the discharge temperature is suppressed by
opening the second expansion valve 14 and heating the refrigerant
with the heat source 17, the circulating volume of the refrigerant
flowing into the condenser is increased by the gas injection. This
reduces the time of the defrosting operation.
Next, at step S25, the outdoor piping temperature is compared with
the set temperature. When the outdoor piping temperature is equal
to or more than the set temperature (for example, 8.degree. C.), it
is concluded that frost has melted, and the operation proceeds to
step S26. The four-way valve 4 is rotated to return to the heating
operation and restart the operation. While the decrease in the
discharge temperature is suppressed by opening the second expansion
valve 14, carrying out the injection, and heating the refrigerant
with the heat source 17, as in the defrosting operation, the
circulating volume of the refrigerant flowing into the condenser is
increased. In addition, increased heating capacity accelerates the
startup of the heating operation. Next, at step S27, the indoor
piping temperature is compared with a set temperature. When the
indoor piping temperature is equal to or less than the set
temperature, go to step S28. The second expansion valve 14 is
closed to finish the injection. Heating by the heat source 17 is
also completed.
Next, operations and effects during the heating and defrosting
operation will be described. In the defrosting operation, frost
forming on refrigerant pipe of the outdoor heat exchanger 12 during
the heating operation is melted by the heat of the refrigerant.
This is performed by rotating the four-way valve 4 to flow the
refrigerant as in the cooling operation. At the same time, the
second expansion valve 14 is opened to inject a gas into the
compressor 3. This increases the flow rate of the refrigerant
discharged from the compressor 3 and the flow rate of the
refrigerant flowing into the outdoor heat exchanger 12, which
serves as a condenser. On the other hand, as described above, the
discharge temperature of the compressor 3 tends to decrease. Thus,
the heat-exchange performance of the condenser is also maximized in
this case.
More specifically, as shown in FIG. 12, there is a gas-injection
flow rate at which the defrosting time is minimized. Furthermore,
in this embodiment, the heat exchange in the intermediate-pressure
receiver 9 provides further improvement, that is, shortening of the
defrosting time.
Furthermore, when the heating operation is started after the
completion of the defrosting operation, the gas injection can
provide high heating capacity, that is, enhance the startup of the
heating operation.
The use of the heat source for heating a refrigerant, such as an
electric heater, provided in the injection circuit 13, can suppress
the decrease in the discharge temperature of the compressor 3 and
increase the amount of refrigerant to be injected. This can further
shorten the defrosting time. In addition, another use of the heat
source for heating a refrigerant during a return to the heating
operation can further enhance the startup of the heating
operation.
While in the foregoing description the period of the injection
during a return to the heating operation is defined as a period
until the heating capacity reaches a predetermined value, even when
the period of the injection is controlled using the condensation
temperature, or is predefined, a similar effect can be
achieved.
* * * * *