U.S. patent application number 16/629245 was filed with the patent office on 2020-06-25 for refrigeration cycle apparatus and refrigerator including the same.
The applicant listed for this patent is Samsung Electronics Co., Ltd.. Invention is credited to Yuu ITO, Makoto KOBAYASHI, Kazuo SHIMIZU, Tatsuya SHIMIZU, Toshiaki SUZUKI.
Application Number | 20200200451 16/629245 |
Document ID | / |
Family ID | 65357376 |
Filed Date | 2020-06-25 |
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United States Patent
Application |
20200200451 |
Kind Code |
A1 |
KOBAYASHI; Makoto ; et
al. |
June 25, 2020 |
REFRIGERATION CYCLE APPARATUS AND REFRIGERATOR INCLUDING THE
SAME
Abstract
The present disclosure relates to a refrigeration cycle
apparatus including an ejector capable of significantly increasing
the pressure of sucked refrigerant and flowing out the refrigerant
having the increased pressure toward a compressor. The ejector 100
includes a drive refrigerant inlet 111 to allow a first refrigerant
evaporated in a first evaporator to be introduced, a suction
refrigerant inlet 121 to allow a second refrigerant evaporated in a
second evaporator to be introduced, a joining portion 131 to join
the first refrigerant introduced from the drive refrigerant inlet
111 and the second refrigerant introduced from the suction
refrigerant inlet 121, a nozzle neck portion 113 to throttle a flow
passage of the first refrigerant introduced from the drive
refrigerant inlet 111, and a nozzle diffuser portion 114 including
a cylindrical or conical flow passage upstream of the joining
portion 131 to allow the first refrigerant that has passed through
the nozzle neck portion 113 to pass therethrough, and an inner
angle .alpha. of the nozzle diffuser portion 114 in a plane passing
through a center line C is 0.degree. or more and 12.degree. or
less.
Inventors: |
KOBAYASHI; Makoto;
(Yokohama-shi, JP) ; SUZUKI; Toshiaki;
(Yokohama-shi, JP) ; SHIMIZU; Kazuo;
(Yokohama-shi, JP) ; SHIMIZU; Tatsuya;
(Yokohama-shi, JP) ; ITO; Yuu; (Tokyo,
JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Samsung Electronics Co., Ltd. |
Suwon-si, Gyeonggi-do |
|
KR |
|
|
Family ID: |
65357376 |
Appl. No.: |
16/629245 |
Filed: |
July 6, 2018 |
PCT Filed: |
July 6, 2018 |
PCT NO: |
PCT/KR2018/007723 |
371 Date: |
January 7, 2020 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F25B 41/00 20130101;
F25B 2341/0013 20130101; F25B 2341/0011 20130101; F25B 2341/0012
20130101; F25B 9/08 20130101; F25B 5/02 20130101; F25B 1/06
20130101; B60H 2001/3298 20130101 |
International
Class: |
F25B 41/00 20060101
F25B041/00; F25B 9/08 20060101 F25B009/08 |
Foreign Application Data
Date |
Code |
Application Number |
Jul 7, 2017 |
JP |
2017-133732 |
Jun 18, 2018 |
JP |
2018-115443 |
Claims
1. A refrigeration cycle apparatus comprising: a compressor; a
condenser configured to condense a refrigerant compressed in the
compressor; a first evaporator configured to evaporate the
refrigerant condensed in the condenser; a second evaporator
configured to evaporate the refrigerant condensed in the condenser;
and an ejector configured to suck a second refrigerant evaporated
in the second evaporator by a first refrigerant evaporated in the
first evaporator and to discharge the sucked refrigerant toward the
compressor, wherein the ejector includes: a first inlet configured
to allow the first refrigerant to be introduced; a second inlet
configured to allow the second refrigerant to be introduced; a
joining portion configured to join the first refrigerant introduced
through the first inlet and the second refrigerant introduced
through the second inlet; a throttle portion in which a
cross-sectional area of a flow passage of the first refrigerant
introduced through the first inlet is reduced; and a diffuser
portion including a cylindrical or conical flow passage upstream of
the joining portion to allow the first refrigerant that has passed
through the throttle portion to pass therethrough.
2. The refrigeration cycle apparatus according to claim 1, wherein
an inner angle of the diffuser portion is 0 degrees or more and 12
degrees or less.
3. The refrigeration cycle apparatus according to claim 1, wherein
the ejector further includes a parallel portion including a
cylindrical flow passage configured such that the first refrigerant
and the second refrigerant joined downstream of the joining portion
pass therethrough.
4. The refrigeration cycle apparatus according to claim 3, wherein
an area ratio Sr (Sr=Sm/Se) of a flow passage area Sm of the
parallel portion to an outlet area Se of the diffuser portion is
2.5 or more and 5.6 or less.
5. The refrigeration cycle apparatus according to claim 3, wherein
a length ratio Lr (Lr=Lm/De) of a length Lm of the parallel portion
to a diameter De of the most downstream portion of the diffuser
portion is 14 or less.
6. The refrigeration cycle apparatus according to claim 1, wherein
the ejector is configured such that the refrigerant gasified in the
first evaporator is introduced through the first inlet as the first
refrigerant.
7. The refrigeration cycle apparatus according to claim 3, wherein
a ratio f (f=De/Llc) of a diameter De of the most downstream
portion of the diffuser portion to a distance Llc between an outer
end of the most downstream portion of the diffuser portion and an
inner end of the most upstream portion of the parallel portion is
0.82 or more and 1.17 or less.
8. The refrigeration cycle apparatus according to claim 1, wherein
the ejector further includes a decompression portion formed in a
conical shape in which the diameter of a flow passage between the
first inlet and the throttle portion is reduced, and the throttle
portion is formed in a circular shape as a boundary between the
decompression portion and the diffuser portion.
9. The refrigeration cycle apparatus according to claim 1, wherein
the throttle portion includes a cylindrical flow passage.
10. A refrigerator comprising a refrigeration cycle apparatus
including: a compressor; a condenser configured to condense a
refrigerant compressed in the compressor; a first evaporator
configured to evaporate the refrigerant condensed in the condenser;
a second evaporator configured to evaporate the refrigerant
condensed in the condenser; and an ejector configured to suck a
second refrigerant evaporated in the second evaporator by a first
refrigerant evaporated in the first evaporator and to discharge the
sucked refrigerant toward the compressor, wherein the ejector
includes: a first inlet configured to allow the first refrigerant
to be introduced; a second inlet configured to allow the second
refrigerant to be introduced; a joining portion configured to join
the first refrigerant introduced through the first inlet and the
second refrigerant introduced through the second inlet; a throttle
portion in which a cross-sectional area of a flow passage of the
first refrigerant introduced through the first inlet is reduced;
and a diffuser portion including a cylindrical or conical flow
passage upstream of the joining portion to allow the first
refrigerant that has passed through the throttle portion to pass
therethrough.
11. The refrigerator according to claim 10, wherein an inner angle
of the diffuser portion is 0 degrees or more and 12 degrees or
less.
12. The refrigerator according to claim 10, wherein the ejector
further includes a parallel portion including a cylindrical flow
passage configured such that the first refrigerant and the second
refrigerant joined downstream of the joining portion pass
therethrough.
13. The refrigerator according to claim 12, wherein an area ratio
Sr (Sr=Sm/Se) of a flow passage area Sm of the parallel portion to
an outlet area Se of the diffuser portion is 2.5 or more and 5.6 or
less.
14. The refrigerator according to claim 12, wherein a length ratio
Lr (Lr=Lm/De) of a length Lm of the parallel portion to a diameter
De of the most downstream portion of the diffuser portion is 14 or
less.
15. The refrigerator according to claim 10, wherein the ejector is
configured such that the refrigerant gasified in the first
evaporator is introduced through the first inlet as the first
refrigerant.
16. The refrigerator according to claim 12, wherein a ratio f
(f=De/Llc) of a diameter De of the most downstream portion of the
diffuser portion to a distance Llc between an outer end of the most
downstream portion of the diffuser portion and an inner end of the
most upstream portion of the parallel portion is 0.82 or more and
1.17 or less.
17. The refrigerator according to claim 10, wherein the ejector
further includes a decompression portion formed in a conical shape
in which the diameter of a flow passage between the first inlet and
the throttle portion is reduced, and the throttle portion is formed
in a circular shape as a boundary between the decompression portion
and the diffuser portion.
18. The refrigerator according to claim 10, wherein the throttle
portion includes a cylindrical flow passage.
19. A refrigerator comprising a first evaporator configured to cool
air inside a refrigerating chamber; a second evaporator configured
to cool air inside a freezing chamber; an ejector including a
nozzle into which a drive refrigerant of a gaseous state evaporated
in the first evaporator is introduced, a suction portion into which
a suction refrigerant of a gaseous state evaporated in the second
evaporator is sucked, a mixing portion in which the drive
refrigerant and the suction refrigerant are mixed, and a diffuser
configured to boost and flow out the mixed refrigerant; and a
compressor into which the mixed refrigerant flowing out of the
ejector is introduced, wherein the nozzle includes: a decompression
portion configured to depressurize the drive refrigerant and
including a conical flow passage whose diameter decreases along a
flow direction; a circular or cylindrical throttle portion having
the smallest cross-sectional area of the flow passage of the drive
refrigerant; and a diffuser portion configured to increase the flow
speed of the drive refrigerant that has passed through the throttle
portion and including a cylindrical or conical flow passage, and
wherein the mixing portion includes: a joining portion configured
to join the drive refrigerant introduced into the nozzle and the
suction refrigerant introduced into the suction portion and
including a conical flow passage whose diameter increases along a
flow direction; and a parallel portion configured to allow the
drive refrigerant and the suction refrigerant joined in the joining
portion to pass therethrough and including a cylindrical flow
passage.
20. The refrigerator according to claim 19, wherein an inner angle
of the diffuser portion is 0 degrees or more and 12 degrees or
less, an area ratio Sr (Sr=Sm/Se) of a flow passage area Sm of the
parallel portion to an outlet area Se of the diffuser portion is
2.5 or more and 5.6 or less, a length ratio Lr (Lr=Lm/De) of a
length Lm of the parallel portion to a diameter De of the most
downstream portion of the diffuser portion is 14 or less, and a
ratio f (f=De/Llc) of a diameter De of the most downstream portion
of the diffuser portion to a distance Llc between an outer end of
the most downstream portion of the diffuser portion and an inner
end of the most upstream portion of the parallel portion is 0.82 or
more and 1.17 or less.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application is a 371 National Stage of International
Application No. PCT/KR2018/007723, filed Jul. 6, 2018, which claims
priority to Japanese Patent Application No. 2017-133732, filed Jul.
7, 2017, and Japanese Patent Application No. 2018-115443, filed
Jun. 18, 2018, the disclosures of which are herein incorporated by
reference in their entirety.
BACKGROUND
1. Field
[0002] The present disclosure relates to a refrigeration cycle
apparatus.
2. Description of Related Art
[0003] The present disclosure relates to a refrigeration cycle
apparatus for a refrigerator for cooling a plurality of cooling
spaces by a refrigeration cycle including an ejector.
[0004] As an example, a cooling system disclosed in patent
literature JP 2009-236330 A is configured as follows. That is, the
cooling system includes a compressor for compressing a refrigerant,
a condenser for condensing the compressed refrigerant through
cooling, a plurality of evaporators set at different pressures in
combination with each expansion valve expanding the refrigerant
delivered from the condenser, and an ejector disposed at a joining
point of the refrigerants flowing out of the plurality of
evaporators and configured to pressurize the refrigerant introduced
from the evaporator set to a low pressure by the refrigerant
introduced from the evaporator set to a high pressure.
[0005] In order to reduce the power consumption of the compressor
to improve the efficiency of the refrigeration cycle (Coefficient
of Performance; COP), the ejector needs to significantly increase
the pressure of the suction refrigerant and flow out the
refrigerant having the increased pressure toward the
compressor.
SUMMARY
[0006] The present disclosure is directed to providing a
refrigeration cycle apparatus including an ejector capable of
significantly increasing the pressure of sucked refrigerant and
flowing out the refrigerant having the increased pressure toward a
compressor, and a refrigerator including the same.
[0007] One aspect of the present disclosure provides a
refrigeration cycle apparatus including a compressor, a condenser
configured to condense a refrigerant compressed in the compressor,
a first evaporator configured to evaporate the refrigerant
condensed in the condenser, a second evaporator configured to
evaporate the refrigerant condensed in the condenser, and an
ejector configured to suck a second refrigerant evaporated in the
second evaporator by a first refrigerant evaporated in the first
evaporator and to discharge the sucked refrigerant toward the
compressor, wherein the ejector includes a first inlet configured
to allow the first refrigerant to be introduced, a second inlet
configured to allow the second refrigerant to be introduced, a
joining portion configured to join the first refrigerant introduced
through the first inlet and the second refrigerant introduced
through the second inlet, a throttle portion formed by reducing a
cross-sectional area of a flow passage of the first refrigerant
introduced through the first inlet, and a diffuser portion
including a cylindrical or conical flow passage upstream of the
joining portion to allow the first refrigerant that has passed
through the throttle portion to pass therethrough.
[0008] An inner angle of the diffuser portion may be 0.degree. or
more and 12.degree. or less.
[0009] The ejector may further include a parallel portion including
a cylindrical flow passage configured such that the first
refrigerant and the second refrigerant joined downstream of the
joining portion passes therethrough.
[0010] An area ratio Sr (Sr=Sm/Se) of a flow passage area Sm of the
parallel portion to an outlet area Se of the diffuser portion may
be 2.5 or more and 5.6 or less.
[0011] A length ratio Lr (Lr=Lm/De) of a length Lm of the parallel
portion to a diameter De of the most downstream portion of the
diffuser portion may be 14 or less.
[0012] The ejector may be configured such that the refrigerant
gasified in the first evaporator is introduced through the first
inlet as the first refrigerant.
[0013] A ratio f (f=De/Llc) of a diameter De of the most downstream
portion of the diffuser portion to a distance Llc between an outer
end of the most downstream portion of the diffuser portion and an
inner end of the most upstream portion of the parallel portion may
be 0.82 or more and 1.17 or less.
[0014] The ejector may further include a decompression portion
formed in a conical shape in which the diameter of a flow passage
between the first inlet and the throttle portion is reduced, and
the throttle portion may be formed in a circular shape as a
boundary between the decompression portion and the diffuser
portion.
[0015] The throttle portion may include a cylindrical flow
passage.
[0016] Another aspect of the present disclosure provides a
refrigerator that includes a refrigeration cycle apparatus
including a compressor, a condenser configured to condense a
refrigerant compressed in the compressor, a first evaporator
configured to evaporate the refrigerant condensed in the condenser,
a second evaporator configured to evaporate the refrigerant
condensed in the condenser, and an ejector configured to suck a
second refrigerant evaporated in the second evaporator by a first
refrigerant evaporated in the first evaporator and to discharge the
sucked refrigerant toward the compressor, wherein the ejector
includes a first inlet configured to allow the first refrigerant to
be introduced, a second inlet configured to allow the second
refrigerant to be introduced, a joining portion configured to join
the first refrigerant introduced through the first inlet and the
second refrigerant introduced through the second inlet, a throttle
portion formed by reducing a cross-sectional area of a flow passage
of the first refrigerant introduced through the first inlet, and a
diffuser portion including a cylindrical or conical flow passage
upstream of the joining portion to allow the first refrigerant that
has passed through the throttle portion to pass therethrough.
[0017] An inner angle of the diffuser portion may be 0.degree. or
more and 12.degree. or less.
[0018] The ejector may further include a parallel portion including
a cylindrical flow passage configured such that the first
refrigerant and the second refrigerant joined downstream of the
joining portion passes therethrough.
[0019] An area ratio Sr (Sr=Sm/Se) of a flow passage area Sm of the
parallel portion to an outlet area Se of the diffuser portion may
be 2.5 or more and 5.6 or less.
[0020] A length ratio Lr (Lr=Lm/De) of a length Lm of the parallel
portion to a diameter De of the most downstream portion of the
diffuser portion may be 14 or less.
[0021] The ejector may be configured such that the refrigerant
gasified in the first evaporator is introduced through the first
inlet as the first refrigerant.
[0022] A ratio f (f=De/Llc) of a diameter De of the most downstream
portion of the diffuser portion to a distance Llc between an outer
end of the most downstream portion of the diffuser portion and an
inner end of the most upstream portion of the parallel portion may
be 0.82 or more and 1.17 or less.
[0023] The ejector may further include a decompression portion
formed in a conical shape in which the diameter of a flow passage
between the first inlet and the throttle portion is reduced, and
the throttle portion may be formed in a circular shape as a
boundary between the decompression portion and the diffuser
portion.
[0024] The throttle portion may include a cylindrical flow
passage.
[0025] Another aspect of the present disclosure provides a
refrigerator including a first evaporator configured to cool air
inside a refrigerating chamber, a second evaporator configured to
cool air inside a freezing chamber, an ejector including a nozzle
into which a drive refrigerant of a gaseous state evaporated in the
first evaporator is introduced, a suction portion into which a
suction refrigerant of a gaseous state evaporated in the second
evaporator is sucked, a mixing portion in which the drive
refrigerant and the suction refrigerant are mixed, and a diffuser
configured to boost and flow out the mixed refrigerant, and a
compressor into which the mixed refrigerant flowing out of the
ejector is introduced, wherein the nozzle includes a decompression
portion configured to depressurize the drive refrigerant and
including a conical flow passage whose diameter decreases along a
flow direction, a circular or cylindrical throttle portion having
the smallest cross-sectional area of the flow passage of the drive
refrigerant, and a diffuser portion configured to increase the flow
speed of the drive refrigerant that has passed through the throttle
portion and including a cylindrical or conical flow passage, and
wherein the mixing portion includes a joining portion configured to
join the drive refrigerant introduced into the nozzle and the
suction refrigerant introduced into the suction portion and
including a conical flow passage whose diameter increases along a
flow direction, and a parallel portion configured to allow the
drive refrigerant and the suction refrigerant joined in the joining
portion to pass therethrough and including a cylindrical flow
passage.
[0026] An inner angle of the diffuser portion may be 0.degree. or
more and 12.degree. or less, an area ratio Sr (Sr=Sm/Se) of a flow
passage area Sm of the parallel portion to an outlet area Se of the
diffuser portion may be 2.5 or more and 5.6 or less, a length ratio
Lr (Lr=Lm/De) of a length Lm of the parallel portion to a diameter
De of the most downstream portion of the diffuser portion may be 14
or less, and a ratio f (f=De/Llc) of a diameter De of the most
downstream portion of the diffuser portion to a distance Llc
between an outer end of the most downstream portion of the diffuser
portion and an inner end of the most upstream portion of the
parallel portion may be 0.82 or more and 1.17 or less.
[0027] According to the present disclosure, a refrigeration cycle
apparatus including an ejector capable of significantly increasing
the pressure of the suction refrigerant and flowing out the
refrigerant having the increased pressure toward a compressor can
be provided.
BRIEF DESCRIPTION OF THE DRAWINGS
[0028] FIG. 1 is a diagram illustrating a schematic configuration
of a refrigeration cycle apparatus according to an embodiment.
[0029] FIG. 2 is a view illustrating a schematic configuration of a
refrigerator to which the refrigeration cycle apparatus according
to an embodiment is applied.
[0030] FIG. 3 is a view illustrating a schematic configuration of
an ejector.
[0031] FIG. 4 is a graph illustrating a correlation between an
angle .alpha. and a boosting rate PLR.
[0032] FIG. 5A is a view illustrating the flow speed of a
refrigerant in a nozzle diffuser portion of a nozzle and a mixing
portion when the angle .alpha. is 1.5.degree..
[0033] FIG. 5B is a view illustrating the flow speed of the
refrigerant in the nozzle diffuser portion of the nozzle and the
mixing portion when the angle .alpha. is 1.5.degree..
[0034] FIG. 6 is a graph illustrating a correlation between an area
ratio Sr and the boosting ratio PLR.
[0035] FIG. 7 is a graph illustrating a correlation between a
length ratio Lr and the boosting ratio PLR.
[0036] FIG. 8 is an enlarged view of a portion VIII of FIG. 3.
[0037] FIG. 9 is a graph illustrating a correlation between a ratio
f and the boosting rate PLR.
[0038] FIG. 10 is a graph illustrating a correlation between the
angle .alpha., the ratio f, and the boosting rate PLR.
[0039] FIG. 11 is a view illustrating a modification example of the
nozzle of the ejector.
SUMMARY
[0040] Hereinafter embodiments of the present disclosure are
described in detail with reference to the accompanying
drawings.
[0041] FIG. 1 is a diagram illustrating a schematic configuration
of a refrigeration cycle apparatus 1 according to an
embodiment.
[0042] The refrigeration cycle apparatus 1 includes a compressor 10
for compressing a refrigerant, a condenser 20 for condensing the
refrigerant compressed by the compressor 10, and a flow control
valve 30. In the refrigeration cycle apparatus 1 according to the
present embodiment, an R600a refrigerant is used.
[0043] The refrigeration cycle apparatus 1 also includes a first
expansion device 40 and a first evaporator 50. The refrigeration
cycle apparatus 1 also includes a second expansion device 60 and a
second evaporator 70. The first expansion device 40 and the second
expansion device 60 include an expansion valve or a capillary tube,
and decompress and expand the refrigerant flowing out of the
condenser 20. The first evaporator 50 and the second evaporator 70
will be described later.
[0044] The refrigeration cycle apparatus 1 also includes an ejector
100 configured to suck the refrigerant transferred from the second
evaporator 70 by the refrigerant transferred from the first
evaporator 50. The ejector 100 will be described later.
[0045] The refrigeration cycle apparatus 1 also includes a
refrigerant pipe 80 for sequentially connecting the compressor 10,
the condenser 20, and the flow control valve 30. The refrigeration
cycle apparatus 1 also includes a first branch pipe 81 and a second
branch pipe 82 branched from downstream of the flow control valve
30. The first expansion device 40 and the first evaporator 50 are
sequentially connected by the first branch pipe 81. The second
expansion device 60 and the second evaporator 70 are sequentially
connected by the second branch pipe 82. The first branch pipe 81 is
connected to a drive refrigerant inlet 111 of the ejector 100,
which will be described later, and the second branch pipe 82 is
connected to a suction refrigerant inlet 121 of the ejector 100,
which will be described later. The refrigeration cycle apparatus 1
also includes a compressed refrigerant pipe 83 for connecting a
mixed refrigerant outlet 141 of the ejector 100, which will be
described later, and a suction side of the compressor 10.
[0046] FIG. 2 is a view illustrating a schematic configuration of a
refrigerator 200 to which the refrigeration cycle apparatus 1
according to the present embodiment is applied.
[0047] The refrigerator 200 includes a refrigerating chamber 220 to
refrigerate food and the like and a freezing chamber 230 to freeze
food and the like, which are partitioned in a housing 210 by a
partition. The refrigerator 200 also includes a machine room 240
provided in the rear of the freezing chamber 230.
[0048] The refrigerator 200 includes a first cold air passage 221
provided in the rear of the refrigerating chamber 220. The first
evaporator 50 of the refrigeration cycle apparatus 1 and a
refrigerating chamber blower 222 for blowing air into the
refrigerating chamber 220 are installed in the first cold air
passage 221. The first evaporator 50 evaporates the refrigerant
depressurized by the first expansion device 40 by exchanging heat
with cold air in the first cold air passage 221. The cold air
cooled by heat exchange with the first evaporator 50 is raised in
the first cold air passage 221 by the refrigerating chamber blower
222 and is discharged to the refrigerating chamber 220 through a
discharge port of the first cold air passage 221, thereby cooling
the inside of the refrigerating chamber 220. The evaporation
temperature of the first evaporator 50 is adjusted by the first
expansion device 40 in order to cool the inside of the
refrigerating chamber 220.
[0049] The refrigerator 200 includes a second cold air passage 231
provided in the rear of the freezing chamber 230. The second
evaporator 70 of the refrigeration cycle apparatus 1 and a freezing
chamber blower 232 for blowing air into the freezing chamber 230
are installed in the second cold air passage 231. The second
evaporator 70 evaporates the refrigerant depressurized by the
second expansion device 60 by exchanging heat with cold air in the
second cold air passage 231. The cold air cooled by heat exchange
with the second evaporator 70 is raised in the second cold air
passage 231 by the freezing chamber blower 232 and is discharged to
the freezing chamber 230 through a discharge port of the second
cold air passage 231, thereby cooling the inside of the freezing
chamber 230. The evaporation temperature of the second evaporator
70 is adjusted by the second expansion device 60 in order to cool
the inside of the freezing chamber 230.
[0050] The compressor 10 is disposed in the machine room 240.
[0051] The condenser 20 is disposed in the machine room 240, at a
lower portion of the housing 210 and the like.
[0052] The ejector 100 is installed in the first cold air passage
221 or in the second cold air passage 231. However, the ejector 100
may be installed in a wall of a rear portion of the housing
210.
[0053] In the refrigeration cycle apparatus 1 configured as
described above, a high temperature and high pressure refrigerant
compressed by the driving of the compressor 10 is radiated and
condensed by the condenser 20. A part of the refrigerant condensed
in the condenser 20 is introduced into the ejector 100 via the
first expansion device 40 and the first evaporator 50 through the
first branch pipe 81. On the other hand, a part of the refrigerant
condensed in the condenser 20 is introduced into the ejector 100
via the second expansion device 60 and the second evaporator 70
through the second branch pipe 82. The refrigerant joined in the
ejector 100 flows out from the diffuser 140, which will be
described later, and is introduced into the compressor 10.
<An Ejector 100>
[0054] FIG. 3 is a view illustrating a schematic configuration of
the ejector 100.
[0055] The ejector 100 includes a nozzle 110 through which the
refrigerant (hereinafter referred to as "drive refrigerant")
evaporated in the first evaporator 50 passes, and a suction portion
120 for sucking the refrigerant (hereinafter referred to as
"suction refrigerant") evaporated in the second evaporator 70.
[0056] The ejector 100 also includes a mixing portion 130 for
mixing the drive refrigerant and the suction refrigerant, and a
diffuser 140 for boosting and flowing out the mixed refrigerant
mixed in the mixing portion 130.
[0057] The nozzle 110 is provided with a drive refrigerant inlet
111 into which the drive refrigerant flows.
[0058] The suction portion 120 is provided with the suction
refrigerant inlet 121 into which the suction refrigerant flows.
[0059] The diffuser 140 is provided with the mixed refrigerant
outlet 141 through which the mixed refrigerant flows out.
[0060] The nozzle 110 includes a decompression portion 112 for
depressurizing the drive refrigerant, a nozzle neck portion 113
having a reduced cross-sectional area of the flow passage of the
drive refrigerant, and a nozzle diffuser portion 114 for increasing
the flow speed of the drive refrigerant.
[0061] The decompression portion 112 has a substantially conical
flow passage whose diameter decreases toward the right side in FIG.
3.
[0062] The nozzle diffuser portion 114 has a substantially conical
flow passage whose diameter increases toward the right side in FIG.
3, or has a substantially cylindrical flow passage whose diameter
is the same. The nozzle diffuser portion 114 will be described in
detail later.
[0063] The nozzle neck portion 113 is the portion having the
smallest flow passage area between the decompression portion 112
and the nozzle diffuser portion 114.
[0064] The suction portion 120 has a substantially cylindrical flow
passage formed around the nozzle 110.
[0065] The mixing portion 130 includes a joining portion 131 having
a substantially conical flow passage whose diameter increases
toward the right side in FIG. 3, and a parallel portion 132 having
a substantially cylindrical flow passage whose diameter is the
same.
[0066] The diffuser 140 has a substantially conical flow passage
whose diameter increases toward the right side in FIG. 3.
[0067] In the ejector 100 configured as described above, the drive
refrigerant, which is a gaseous refrigerant after evaporating
(gasified) by heat exchange in the first evaporator 50, that is,
which is a refrigerant containing no droplets or a refrigerant
containing a small amount of droplets, is introduced through the
drive refrigerant inlet 111 of the nozzle 110. In addition, the
suction refrigerant, which is a gaseous refrigerant after
evaporating (gasified) by heat exchange in the second evaporator
70, that is, which is a refrigerant containing no droplets or a
refrigerant containing a small amount of droplets, is introduced
into the suction refrigerant inlet 121 of the suction portion
120.
[0068] The ejector 100 joins the drive refrigerant introduced into
the drive refrigerant inlet 111 and the suction refrigerant
introduced into the suction refrigerant inlet 121, in the mixing
portion 130 to form a mixed refrigerant, and then flows out the
mixed refrigerant through the mixed refrigerant outlet 141.
[0069] With this configuration, the drive refrigerant introduced
through the drive refrigerant inlet 111 is decompressed and
expanded in the decompression portion 112 due to the decrease in
the flow passage area. The flow speed of the drive refrigerant
increasing by decompression further increases in the nozzle neck
portion 113 and then further more increases in the nozzle diffuser
portion 114. Accordingly, the ultra-high speed drive refrigerant
flows out of the nozzle 110.
[0070] The suction refrigerant sucked through the suction
refrigerant inlet 121 of the suction portion 120 is sucked into the
ultra-high speed drive refrigerant by the pressure difference
between the suction refrigerant inlet 121 and an outlet of the
nozzle 110. The high speed drive refrigerant flowing out of the
outlet of the nozzle 110 and the low speed suction refrigerant
begin to mix in the joining portion 131 of the mixing portion 130.
Kinetic energy exchange occurs between the drive refrigerant and
the suction refrigerant.
[0071] Also, due to the deceleration caused by the flow passage
enlargement in the diffuser 140, the dynamic pressure is converted
to the static pressure, the pressure increases, and the mixed
refrigerant flows out through the diffuser 140.
[0072] The ejector 100 according to the present embodiment has a
function of sucking the suction refrigerant through the suction
refrigerant inlet 121 by lowering the static pressure by flowing
the drive refrigerant introduced through the drive refrigerant
inlet 111 at a high speed. The higher the pressure (hereinafter
referred to as "outlet pressure Pc") of the mixed refrigerant
flowing out toward the compressor 10 through the mixed refrigerant
outlet 141 of the diffuser 140 with respect to the pressure
(hereinafter referred to as "suction pressure Pe") of the suction
refrigerant in the suction refrigerant inlet 121, the higher the
performance of the ejector 100. That is, when the value obtained by
dividing the outlet pressure Pc by the suction pressure Pe is
referred to as a "boosting rate PLR" (the boosting rate PLR=the
outlet pressure Pc/the suction pressure Pe), the higher the
boosting rate PLR, the higher the performance of the ejector 100.
This is because the higher the pressure of the refrigerant
introduced into the compressor 10, the more the efficiency (a
performance factor COP) of the refrigeration cycle apparatus 1 may
be improved.
[0073] In the ejector 100 according to the present embodiment as
described above, the gaseous refrigerant after evaporating
(gasified) by heat exchange in the first evaporator 50 is
introduced through the drive refrigerant inlet 111 of the nozzle
110 as the drive refrigerant. When the drive refrigerant introduced
through the drive refrigerant inlet 111 of the nozzle 110 is a
liquid refrigerant, the nozzle 110 through which the drive
refrigerant passes needs to have functions of evaporating the
liquid refrigerant and flowing the refrigerant at a high speed.
This is because while a part of the liquid refrigerant evaporates
to become a gas, the remainder in a droplet state interferes with
the speeding up of the refrigerant.
[0074] Because the ejector 100 according to the present embodiment
is an ejector in which the drive refrigerant is a single phase type
(which does not contain droplets or contains a small amount of
droplets), the nozzle 110 through which the drive refrigerant
passes may increase the boosting rate (PLR) by having a function of
increasing the flow speed of the drive refrigerant at a high speed
even if the nozzle 110 does not have a function of evaporating the
refrigerant.
[0075] As a result of a study by the present inventors, it was
found that an inner angle .alpha. (an angle formed between straight
lines L having a cross-sectional shape cut from the surface passing
through a center line C of a flow passage outer circumferential
surface (an inner circumferential surface of the portion forming
the flow passage in the nozzle diffuser portion 114) of the nozzle
diffuser portion 114) of the nozzle diffuser portion 114 is
appropriately 0.degree. or more and 12.degree. or less.
[0076] FIG. 4 is a graph illustrating a correlation between the
inner angle .alpha. and the boosting rate PLR. FIG. 4 illustrates a
correlation when an area ratio Sr, which will be described later,
is 3.4 and a length ratio Lr, which will be described later, is
8.0.
[0077] FIG. 5A is a view illustrating the flow speed of the
refrigerant in the nozzle diffuser portion 114 of the nozzle 110
and the mixing portion 130 when the angle .alpha. is 1.5.degree..
FIG. 5B is a view illustrating the flow speed of the refrigerant in
the nozzle diffuser portion 114 of the nozzle 110 and the mixing
portion 130 when the angle .alpha. is 1.5.degree.. FIGS. 5A and 5B
illustrates that the higher the flow speed of the refrigerant, the
finer the hatching. The finest hatching represents the supersonic
speed. In FIGS. 5A and 5B, hatching indicating the cross section of
the nozzle 110 is omitted.
[0078] When the angle .alpha. is 15.degree., because the drive
refrigerant is about to flow along an inner circumferential surface
of the nozzle diffuser portion 114 but is pushed by the suction
refrigerant, separation occurs in the nozzle diffuser portion 114,
resulting in loss. Accordingly, as illustrated in FIG. 5B, the flow
speed at a flow passage outlet 114a of the nozzle diffuser portion
114 decreases. When the flow speed decreases, the static pressure
increases, and the force to suck the suction refrigerant decreases.
As a result, the boosting rate PLR decreases, so that the
efficiency of the refrigeration cycle apparatus 1 becomes difficult
to increase.
[0079] In contrast, as illustrated in FIG. 5A, when the angle
.alpha. is 1.5.degree., because the flow speed of the drive
refrigerant flowing along the inner circumferential surface of the
nozzle diffuser portion 114 is fast and thus no separation occurs
in the nozzle diffuser portion 114, no decrease in flow speed
occurs. In addition, because the flow speed at the flow passage
outlet 114a of the nozzle diffuser portion 114 is fast, the static
pressure decreases, and the force to suck the suction refrigerant
increases. As a result, the boosting rate PLR increases, so that
the efficiency of the refrigeration cycle apparatus 1 becomes easy
to increase.
[0080] As a result of a study by the present inventors, it was
found that as illustrated in FIG. 4, when the angle .alpha. is
0.degree. or more and 12.degree. or less, the boosting rate PLR
becomes 1.15 or more, so that the boosting rate PLR is larger than
in a case where the angle .alpha. is larger than 12.degree..
Accordingly, by making the angle .alpha. into 0.degree. or more and
12.degree. or less, the performance of the ejector 100 may be
further improved than in the case where the angle .alpha. is larger
than 12.degree.. As a result, by making the angle .alpha. into
0.degree. or more and 12.degree. or less, the efficiency (the
performance factor COP) of the refrigeration cycle apparatus 1 may
be improved rather than in the case where the angle .alpha. is
larger than 12.degree..
[0081] It is further appropriate that the angle .alpha. is
0.degree. or more and 9.5.degree. or less. When the angle .alpha.
is 0.degree. or more and 9.5.degree. or less, the boosting rate PLR
becomes 1.20 or more, so that the boosting rate PLR is larger than
in a case where the angle .alpha. is larger than 9.5.degree.. It is
particularly appropriate that the angle .alpha. is 1.5.degree. or
more and 4.degree. or less. When the angle .alpha. is 1.5.degree.
or more and 4.degree. or less, the boosting rate PLR becomes 1.225
or more, so that the boosting rate PLR is larger than in a case
where the angle .alpha. is 0.degree. or more and 1.5.degree. or
less, and larger than 4.degree..
[0082] As a result of a study by the present inventors, it was
found that it is appropriate that the area ratio Sr (Sr=a parallel
portion area Sm/an outlet area Se) of the parallel portion area Sm
(refer to FIG. 3), which is the flow passage area of the parallel
portion 132 of the mixing portion 130, to the outlet area Se (refer
to FIG. 3), which is the area of the flow passage outlet 114a of
the nozzle diffuser portion 114, is 2.5 or more and 5.6 or
less.
[0083] FIG. 6 is a graph illustrating a correlation between the
area ratio Sr and the boosting ratio PLR. FIG. 6 illustrates a
correlation when the angle .alpha. is 1.5.degree. and the length
ratio Lr is 8.0.
[0084] As illustrated in FIG. 6, when the area ratio Sr is 2.5 or
more and 5.6 or less, the boosting rate PLR becomes 1.15 or more,
so that the boosting rate PLR is larger than in a case where the
area ratio Sr is smaller than 2.5 and in a case where the area
ratio Sr is larger than 5.6.
[0085] When the ratio of the parallel portion area Sm of the
parallel portion 132 of the mixing portion 130 to the outlet area
Se of the flow passage outlet 114a of the nozzle diffuser portion
114 is excessively small, the space to suck the suction refrigerant
is small and the force to suck the suction refrigerant decreases,
so that the boosting rate PLR becomes decreases.
[0086] On the other hand, when the ratio of the parallel portion
area Sm of the parallel portion 132 of the mixing portion 130 to
the outlet area Se of the flow passage outlet 114a of the nozzle
diffuser portion 114 is excessively large, because the space to
suck the suction refrigerant becomes large and the drive
refrigerant and the suction refrigerant become difficult to
exchange kinetic energy, the force to suck the suction refrigerant
decreases.
[0087] As a result, when the area ratio Sr is smaller than 2.5 and
the area ratio Sr is larger than 5.6, the boosting rate PLR
decreases, so that the efficiency of the refrigeration cycle
apparatus 1 becomes difficult to increase.
[0088] In contrast, when the area ratio Sr is 2.5 or more and 5.6
or less, because the space to suck the suction refrigerant may be
secured and the drive refrigerant and the suction refrigerant may
exchange kinetic energy, the force to suck the suction refrigerant
increases. As a result, the boosting rate PLR increases and the
efficiency of the refrigeration cycle apparatus 1 increases.
[0089] Accordingly, by making the area ratio Sr into 2.5 or more
and 5.6 or less, the performance of the ejector 100 may be further
improved than in the case where the area ratio Sr is smaller than
2.5 and in the case where the area ratio Sr is larger than 5.6. As
a result, by making the area ratio Sr into 2.5 or more and 5.6 or
less, the efficiency of the refrigeration cycle apparatus 1 may be
further improved than in the case where the area ratio Sr is
smaller than 2.5 and in the case where the area ratio Sr is larger
than 5.6.
[0090] It is further appropriate that the area ratio Sr is 2.8 or
more and 4.3 or less. When the area ratio Sr is 2.8 or more and 4.3
or less, the boosting rate PLR becomes 1.20 or more, so that the
boosting rate PLR is larger than in a case where the area ratio Sr
is smaller than 2.8 and in a case where the area ratio Sr is larger
than 4.3. Accordingly, by making the area ratio Sr into 2.8 or more
and 4.3 or less, the efficiency of the refrigeration cycle
apparatus 1 may be improved.
[0091] As a result of a study by the present inventors, it was
found that it is appropriate that the length ratio Lr (Lr_=a
parallel portion length Lm/an outlet diameter De) of the parallel
portion length Lm (refer to FIG. 3), which is a length of the
parallel portion 132 of the mixing portion 130 in the centerline
direction, to the outlet diameter De (refer to FIG. 3), which is a
diameter of the flow passage outlet 114a (the most downstream) of
the nozzle diffuser portion 114, is 14 or less.
[0092] FIG. 7 is a graph illustrating a correlation between the
length ratio Lr and the boosting ratio PLR. FIG. 7 illustrates a
correlation when the angle .alpha. is 1.5.degree. and the area
ratio Sr is 3.4.
[0093] As illustrated in FIG. 7, when the length ratio Lr is 14 or
less, the boosting ratio PLR becomes 1.1 or more, so that the
boosting ratio PLR is larger than in a case where the length ratio
Lr is larger than 14.
[0094] When the length ratio Lr of the parallel portion length Lm
of the parallel portion 132 of the mixing portion 130 to the outlet
diameter De of the flow passage outlet 114a of the nozzle diffuser
portion 114 is excessively large (when the length ratio Lr is
larger than 14), it is considered that the boosting rate PLR
becomes small because the pressure loss in the parallel portion 132
of the mixing portion 130 becomes large and the flow speed of the
refrigerant decreases.
[0095] In contrast, when the length ratio Lr is 14 or less, the
pressure loss in the parallel portion 132 of the mixing portion 130
is small, the flow speed of the refrigerant increases, and the
static pressure decreases. As a result, the force to suck the
suction refrigerant increases. Also, because the drive refrigerant
and the suction refrigerant may perform kinetic energy exchange in
the parallel portion 132 of the mixing portion 130, the force to
suck the suction refrigerant is improved.
[0096] Accordingly, by making the length ratio Lr into 14 or less,
the boosting ratio PLR may be increased more than in the case where
the length ratio Lr is larger than 14, and the performance of the
ejector 100 may be improved. As a result, by making the length
ratio Lr into 14 or less, the efficiency of the refrigeration cycle
apparatus 1 may be further improved than in the case where the
length ratio Lr is larger than 14.
[0097] It is further appropriate that the length ratio Lr is 3.0 or
more and 12.5 or less. When the length ratio Lr is 3.0 or more and
12.5 or less, the boosting rate PLR becomes 1.20 or more, so that
the boosting rate PLR is larger than in a case where the length
ratio Lr is smaller than 3.0 and in a case where the length ratio
Lr is larger than 12.5. Accordingly, by making the length ratio Lr
into 3.0 or more and 12.5 or less, the efficiency of the
refrigeration cycle apparatus 1 may be improved.
<Regarding the Shape of the Joining Portion 131>
[0098] FIG. 8 is an enlarged view of a portion VIII of FIG. 3.
[0099] The joining portion 131 of the mixing portion 130 is a space
between the nozzle 110 and the parallel portion 132 of the mixing
portion 130 in the centerline direction. Also, the joining portion
131 is a space in a curved surface Cs that linearly connects an
outer end 110a of the outlet of the nozzle 110 and an inner end
132a of the inlet of the parallel portion 132 in a radial
direction. The shape of the cross section obtained by cutting the
curved surface Cs from a surface passing through the center line C
becomes a straight line Lc shown by broken lines in FIG. 8. Also,
the curved surface Cs is a surface showing the boundary between the
suction portion 120 and the joining portion 131, and at the same
time is an outlet through which the suction refrigerant flows out
from the suction portion 120.
[0100] As a result of a study by the present inventors, it was
found that it is appropriate that a ratio f (f=the outlet diameter
De/a length Llc) of the outlet diameter De of the nozzle diffuser
portion 114 of the nozzle 110 to the length Llc (the distance
between the end 110a of the nozzle 110 and the end 132a of the
parallel portion 132) of the straight line Lc is 0.82 or more and
1.17 or less.
[0101] FIG. 9 is a graph illustrating a correlation between the
ratio f and the boosting rate PLR.
[0102] As illustrated in FIG. 9, when the ratio f is 0.82 or more
and 1.17 or less, the boosting rate PLR becomes 1.15 or more, so
that the boosting rate PLR is larger than in a case where the ratio
f is smaller than 0.82 and in a case where the ratio f is larger
than 1.17.
[0103] When the ratio f of the outlet diameter De of the nozzle
diffuser portion 114 to the length Llc of the straight line Lc is
excessively small, because the space to suck the suction
refrigerant becomes large and the drive refrigerant and the suction
refrigerant become difficult to exchange kinetic energy, the force
to suck the suction refrigerant decreases.
[0104] On the other hand, when the ratio f of the outlet diameter
De of the nozzle diffuser portion 114 to the length Llc of the
straight line Lc is excessively large, because the space to suck
the suction refrigerant is small and the force to suck the suction
refrigerant decreases, the boosting rate PLR decreases.
[0105] As a result, when the ratio f is smaller than 0.82 and is
larger than 1.17, the boosting rate PLR decreases, so that the
efficiency of the refrigeration cycle apparatus 1 becomes difficult
to increase.
[0106] In contrast, when the ratio f is 0.82 or more and 1.17 or
less, because the space to suck the suction refrigerant may be
secured and the kinetic energy exchange between the drive
refrigerant and the suction refrigerant is facilitated, the force
to suck the suction refrigerant increases. As a result, the
boosting rate PLR increases and the efficiency of the refrigeration
cycle apparatus 1 increases.
[0107] Accordingly, by making the ratio f into 0.82 or more and
1.17 or less, the performance of the ejector 100 may be further
improved than in the case where the ratio f is smaller than 0.82
and in the case where the ratio f is larger than 1.17. As a result,
by making the ratio f into 0.82 or more and 1.17 or less, the
efficiency of the refrigeration cycle apparatus 1 may be further
improved than in the case where the ratio f is smaller than 0.82
and in the case where the ratio f is larger than 1.17.
[0108] It is further appropriate that the ratio f is 0.85 or more
and 1.12 or less. When the ratio f is 0.85 or more and 1.12 or
less, the boosting rate PLR becomes 1.20 or more, so that the
boosting rate PLR is larger than in the case where the ratio f is
smaller than 0.85 and in the case where the ratio f is larger than
1.12. Accordingly, by making the ratio f into 0.85 or more and 1.12
or less, the efficiency of the refrigeration cycle apparatus 1 may
be improved.
[0109] FIG. 10 is a graph illustrating a correlation between the
angle .alpha., the ratio f, and the boosting rate PLR.
[0110] When the length Llc of the straight line Lc is the same,
because the outlet diameter De of the nozzle diffuser portion 114
of the nozzle 110 becomes larger as the angle .alpha. becomes
larger, as illustrated in FIG. 10, the ratio f becomes larger as
the angle .alpha. becomes larger. In this way, the ratio f changes
depending on the angle .alpha.. Also, because the outlet area Se
becomes larger as the outlet diameter De becomes larger and the
area ratio Sr becomes smaller as the outlet area Se becomes larger,
the ratio f becomes larger as the area ratio Sr becomes smaller. In
this way, the ratio f changes depending on the area ratio Sr. Also,
because the length ratio Lr becomes smaller as the outlet diameter
De becomes larger, the ratio f becomes larger as the length ratio
Lr becomes smaller. In this way, the ratio f changes depending on
the length ratio Lr.
[0111] As described above, the ejector 100 includes the drive
refrigerant inlet 111 as an example of a first inlet for allowing
the drive refrigerant as an example of a first refrigerant to be
introduced, and the suction refrigerant inlet 121 as an example of
a second inlet for allowing the suction refrigerant as an example
of a second refrigerant to be introduced. The ejector 100 also
includes the joining portion 131 for allowing the drive refrigerant
introduced through the drive refrigerant inlet 111 and the suction
refrigerant introduced through the suction refrigerant inlet 121 to
join, and the parallel portion 132 having a cylindrical flow
passage downstream of the joining portion 131 for allowing the
joined drive refrigerant and suction refrigerant to pass
therethrough. The ejector 100 also includes the nozzle neck portion
113 as an example of a throttle portion for reducing the
cross-sectional area of the flow passage of the drive refrigerant
introduced through the drive refrigerant inlet 111, and the nozzle
diffuser portion 114 as an example of a diffuser having a
cylindrical or conical flow passage upstream of the joining portion
131 for allowing the drive refrigerant that has passed through the
nozzle neck portion 113 to pass therethrough. Also, in the ejector
100, the ratio f as an example of a ratio of the outlet diameter De
of the most downstream portion of the nozzle diffuser portion 114
to the distance (the length Llc) between the end 110a as an example
of an outer end at the most downstream portion of the nozzle
diffuser portion 114 and the end 132a as an example of an inner end
at the most upstream portion of the parallel portion 132 is 0.82 or
more and 1.17 or less. According to the ejector 100 configured as
described above, compared to the case where the ratio f is smaller
than 0.82 or the ratio f is larger than 1.17, the performance of
the ejector 100 may be improved. As a result, the efficiency of the
refrigeration cycle apparatus 1 including the ejector 100 may be
improved.
<A Modification Example of the Nozzle 110 of the Ejector
100>
[0112] FIG. 11 is a view illustrating a modification example of the
nozzle 110 of the ejector 100.
[0113] In the above-described embodiment, the nozzle neck portion
113 of the nozzle 110 has a circular shape as a boundary between
the substantially conical flow passage in the decompression portion
112 and the substantially conical flow passage in the nozzle
diffuser portion 114, the present disclosure is not particularly
limited to this shape. As illustrated in FIG. 11, the nozzle neck
portion 113 may have a substantially cylindrical flow passage
having the same diameter.
* * * * *