U.S. patent application number 16/091138 was filed with the patent office on 2019-05-02 for heat exchanger.
The applicant listed for this patent is DENSO CORPORATION. Invention is credited to Tetsuya ITO, Daiki KATO, Masaaki KAWAKUBO, Hiroshi MIEDA, Ryohei SUGIMURA.
Application Number | 20190128577 16/091138 |
Document ID | / |
Family ID | 60085769 |
Filed Date | 2019-05-02 |
View All Diagrams
United States Patent
Application |
20190128577 |
Kind Code |
A1 |
SUGIMURA; Ryohei ; et
al. |
May 2, 2019 |
HEAT EXCHANGER
Abstract
A heat exchanger includes a heat exchanging portion, a reservoir
that performs gas-liquid separation on a gas-liquid two-phase
refrigerant that flows out from the heat exchanging portion into a
gas-phase refrigerant and a liquid-phase refrigerant and stores the
liquid-phase refrigerant, and an inflow passage that allows the
gas-liquid two-phase refrigerant flowing out from the heat
exchanging portion to flow into the reservoir. The inflow passage
is connected so as to be in communication with an inlet port of the
reservoir which is disposed above a liquid surface of the
liquid-phase refrigerant stored in the reservoir.
Inventors: |
SUGIMURA; Ryohei;
(Kariya-city, JP) ; KAWAKUBO; Masaaki;
(Kariya-city, JP) ; KATO; Daiki; (Kariya-city,
JP) ; MIEDA; Hiroshi; (Kariya-city, JP) ; ITO;
Tetsuya; (Kariya-city, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
DENSO CORPORATION |
Kariya-city, Aichi-pref. |
|
JP |
|
|
Family ID: |
60085769 |
Appl. No.: |
16/091138 |
Filed: |
April 3, 2017 |
PCT Filed: |
April 3, 2017 |
PCT NO: |
PCT/JP2017/013975 |
371 Date: |
October 4, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F25B 40/00 20130101;
B60H 1/32281 20190501; F25B 39/00 20130101; F25B 5/04 20130101;
F25B 39/04 20130101; F25B 2400/23 20130101; B60H 1/00335 20130101;
F25B 2400/16 20130101; F28D 1/05391 20130101; F25B 2500/18
20130101; F25B 6/04 20130101; F25B 43/006 20130101; F25B 2339/047
20130101 |
International
Class: |
F25B 43/00 20060101
F25B043/00; F25B 39/00 20060101 F25B039/00 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 8, 2016 |
JP |
2016-078224 |
Dec 2, 2016 |
JP |
2016-234961 |
Claims
1. A heat exchanger for a refrigeration cycle, comprising: a heat
exchanging portion that exchanges heat between a refrigerant
passing through therein and air; a reservoir that performs
gas-liquid separation on a gas-liquid two-phase refrigerant that
flows out from the heat exchanging portion into a gas-phase
refrigerant and a liquid-phase refrigerant, the reservoir storing
the liquid-phase refrigerant; an inflow passage that allows the
gas-liquid two-phase refrigerant flowing out from the heat
exchanging portion to flow into the reservoir; a gas-phase outflow
passage that allows the gas-phase refrigerant to flow out from the
reservoir; and a liquid-phase outflow passage that allows the
liquid-phase refrigerant to flow out from the reservoir; wherein
the inflow passage is connected so as to be in communication with
an inlet port of the reservoir disposed above a liquid surface of
the liquid-phase refrigerant stored in the reservoir, the gas-phase
outflow passage is connected so as to be in communication with a
gas-phase outlet port of the reservoir disposed above the liquid
surface of the liquid-phase refrigerant stored in the reservoir,
the gas-phase outlet port being disposed so as to be connected to a
compressor included in the refrigeration cycle, and the
liquid-phase outflow passage is connected so as to be in
communication with a liquid-phase outlet port of the reservoir
disposed below the liquid surface of the liquid-phase refrigerant
stored in the reservoir.
2. The heat exchanger according to claim 1, wherein the reservoir
includes a partition portion between the inlet port and the
gas-phase outlet port.
3. The heat exchanger according to claim 2, wherein the partition
portion is disposed such that at least a portion thereof faces the
inlet port.
4. The heat exchanger according to claim 1, wherein a buffer
portion is disposed between the inlet port and the liquid surface
of the liquid-phase refrigerant.
5. The heat exchanger according to claim 4, wherein at least part
of the buffer portion is arranged between the inlet port and the
liquid-phase outlet port, and the buffer portion is disposed closer
toward the liquid surface as compared to the inlet port.
6. The heat exchanger according to claim 5, wherein the reservoir
includes a substantially cylindrical main body portion in which the
liquid-phase refrigerant can be stored, and an average distance
from the buffer portion to an inner wall of the main body portion
is equal to or less than one-third of a radius of the main body
portion.
7. The heat exchanger according to claim 1, wherein the reservoir
includes a substantially cylindrical main body portion in which the
liquid-phase refrigerant can be stored, and the main body portion
is formed with a main reservoir space and an auxiliary reservoir
space, the auxiliary reservoir space having a smaller liquid
surface area than the main reservoir space.
8. The heat exchanger according to claim 1, wherein the inflow
passage is disposed such that if a center line of the inflow
passage is extended, the center line reaches an inner wall surface
of the reservoir without passing through a center of the
reservoir.
9. The heat exchanger according to claim 8, wherein the inflow
passage is provided such that the gas-liquid two-phase refrigerant
which flows through the inflow passage then flows in from the inlet
port collides with the inner wall surface of the reservoir and then
falls into the liquid-phase refrigerant stored in the
reservoir.
10. The heat exchanger according to claim 8, wherein a distance
from the inlet port to an inner wall surface portion of the
reservoir that faces the inlet port is shorter than a distance
between the farthest portions of the inner wall surface of the
reservoir.
11. The heat exchanger according to claim 10, wherein the inner
wall surface of the reservoir has a substantially circular cross
section, and the distance from the inlet port to the inner wall
surface portion of the reservoir that faces the inlet port is
shorter than a diameter of the reservoir.
12. The heat exchanger according to claim 11, wherein a part of an
inner wall surface of the inflow passage is disposed so as to
follow the tangent of the inner wall surface of the reservoir.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] This application is based on and claims the benefits of
priority of Japanese Patent Application No. 2016-078224 filed on
Apr. 8, 2016 and Japanese Patent Application No. 2016-234961 filed
on Dec. 2, 2016, the entire disclosure of which is incorporated
herein by reference.
TECHNICAL FIELD
[0002] The present disclosure relates to a heat exchanger.
BACKGROUND ART
[0003] Conventionally, for example as described in Patent Document
1 below, a refrigeration cycle device which uses this type of heat
exchanger is known. The refrigeration cycle device described in
Patent Document 1 includes a gas-liquid separator for separating a
refrigerant into a gas-phase refrigerant and a liquid-phase
refrigerant, and a switching means for switching a refrigerant
circuit, in which a refrigerant circulates, between a refrigerant
circuit of a first mode and a refrigerant circuit of a second mode.
Specifically, the gas-liquid separator separates the refrigerant
flowing out of an outside heat exchanger into a gas-phase
refrigerant and a liquid-phase refrigerant, discharges the
gas-phase refrigerant from a gas-phase refrigerant outlet, and
discharges the liquid-phase refrigerant from a liquid-phase
refrigerant outlet. Further, the refrigerant circuit of the first
mode is a refrigerant circuit that causes the liquid-phase
refrigerant to flow out from the liquid-phase refrigerant outlet of
the gas-liquid separator and into a second pressure reducing means
and an evaporator, and further causes the liquid-phase refrigerant
to be sucked into a compressor. The refrigerant circuit of the
second mode is a refrigerant circuit that causes the gas-phase
refrigerant to flow out from the gas-phase refrigerant outlet of
the gas-liquid separator and to be sucked into the compressor.
According to the gas-liquid separator disclosed in Patent Document
1, the refrigerant is introduced from below.
PRIOR ART DOCUMENTS
Patent Documents
[0004] Patent Literature 1: JP 2014-149123 A
SUMMARY OF INVENTION
[0005] When refrigerant is introduced from the lower side of the
gas-liquid separator as described in Patent Document 1, during a
heating operation the gas-phase refrigerant is blown out into the
liquid-phase refrigerant, and the liquid-phase refrigerant becomes
mixed with the gas-phase refrigerant, the liquid surface of the
liquid-phase refrigerant is not stabilized, and the gas-liquid
separator may be unable to function as a reservoir.
[0006] It is an object of the present disclosure to provide a heat
exchanger that can function as a reservoir by suppressing
turbulence in the liquid surface of a reservoir.
[0007] According to the present disclosure, a heat exchanger for a
refrigeration cycle includes a heat exchanging portion (34) that
exchanges heat between a refrigerant passing through therein and
air, a reservoir (36, 36A, 36B, 36C, 36D, 36E, 36F, 36G) that
performs gas-liquid separation on a gas-liquid two-phase
refrigerant that flows out from the heat exchanging portion into a
gas-phase refrigerant and a liquid-phase refrigerant, the reservoir
storing the liquid-phase refrigerant, an inflow passage (12) that
allows the gas-liquid two-phase refrigerant flowing out from the
heat exchanging portion to flow into the reservoir, a gas-phase
outflow passage (13) that allows the gas-phase refrigerant to flow
out from the reservoir, and a liquid-phase outflow passage (14)
that allows the liquid-phase refrigerant to flow out from the
reservoir. The inflow passage is connected so as to be in
communication with an inlet port (81a) of the reservoir disposed
above a liquid surface of the liquid-phase refrigerant stored in
the reservoir, the gas-phase outflow passage is connected so as to
be in communication with a gas-phase outlet port (81b) of the
reservoir disposed above the liquid surface of the liquid-phase
refrigerant stored in the reservoir, and the liquid-phase outflow
passage is connected so as to be in communication with a
liquid-phase outlet port (81c) of the reservoir disposed below the
liquid surface of the liquid-phase refrigerant stored in the
reservoir.
[0008] According to the present disclosure, since the refrigerant
flows in from above the liquid surface, gas-phase refrigerant does
not flow into the liquid-phase refrigerant stored in the reservoir,
and it is possible to suppress disturbances in the liquid
surface.
[0009] Furthermore, according to the present disclosure, a
gas-phase outflow passage and a liquid-phase outflow passage are
provided, and can function as both a receiver and an accumulator.
In particular, when the inflow port is provided in the upper region
when functioning as a receiver, the gas-liquid two-phase
refrigerant flows from above, and it is necessary to address
further problems caused by this.
[0010] Further, according to the present disclosure, the reservoir
preferably includes a partition portion (82, 82B, 82C) between the
inlet port and the gas-phase outlet port.
[0011] By providing a partition portion between the inlet port and
the gas-phase outlet port, the refrigerant flowing in from the
inlet port hits the partition portion before flowing out from the
gas-phase outlet port, and continues downward. Therefore, it is
possible to suppress the liquid-phase refrigerant from flowing out
of the gas-phase outlet port.
[0012] Further, according to the present disclosure, a buffer
portion (83, 83B, 83C) is preferably disposed between the inlet
port and the liquid surface of the liquid-phase refrigerant
[0013] In the case where the incoming refrigerant is substantially
liquid-phase refrigerant, it hits the buffer portion and then
continues toward the liquid surface. Therefore, the refrigerant
does not directly hit the liquid surface of the liquid-phase
refrigerant accumulated inside, and disturbances of the liquid
surface can be suppressed.
[0014] Further, according to the present disclosure, the inflow
passage is preferably disposed such that if a center line of the
inflow passage is extended, the center line reaches an inner wall
surface (816, 812Gb) of the reservoir (36D, 36E, 36F, 36G) without
passing through a center (815, 812Ga) of the reservoir.
[0015] In the case where the incoming refrigerant is substantially
liquid-phase refrigerant, it hits the inner wall surface of the
reservoir and then continues toward the liquid surface. Therefore,
the refrigerant does not directly hit the liquid surface of the
liquid-phase refrigerant accumulated inside, and disturbances of
the liquid surface can be suppressed.
[0016] It is noted that the reference numerals in parentheses
described in "SUMMARY OF INVENTION" and "CLAIMS" indicate the
correspondence relationship with "DESCRIPTION OF EMBODIMENTS"
described later, and "SUMMARY OF INVENTION" and "CLAIMS" are not
limited to "DESCRIPTION OF EMBODIMENTS".
BRIEF DESCRIPTION OF DRAWINGS
[0017] FIG. 1 is a view for explaining an example of a
refrigeration cycle to which a heat exchanger according to each
embodiment is applied.
[0018] FIG. 2 is a view for explaining a case where the
refrigeration cycle shown in FIG. 1 is operated in a cooling
operation.
[0019] FIG. 3 is a view for explaining a case where the
refrigeration cycle shown in FIG. 1 is operated in a heating
operation.
[0020] FIG. 4 is a view for further explaining the heat exchanger
shown in FIG. 1.
[0021] FIG. 5 is a view schematically showing a heat exchanger
according to a first embodiment of the present invention.
[0022] FIG. 6 is a view for explaining the liquid surface height
inside a reservoir.
[0023] FIG. 7 is a view for explaining the interior of a
reservoir.
[0024] FIG. 8 is a view for explaining the interior of a
reservoir.
[0025] FIG. 9 is a view for explaining a reservoir according to a
second embodiment.
[0026] FIG. 10 is a cross-sectional view taken along line X-X of
FIG. 9.
[0027] FIG. 11 is a view for explaining a reservoir according to a
third embodiment.
[0028] FIG. 12 is a view for explaining a reservoir according to a
third embodiment.
[0029] FIG. 13 is a view for explaining a reservoir according to a
modified example of the third embodiment.
[0030] FIG. 14 is a view for explaining a reservoir according to a
fourth embodiment.
[0031] FIG. 15 is a view for explaining a reservoir according to a
fifth embodiment.
[0032] FIG. 16 is a view for explaining a reservoir according to a
modified example of the fifth embodiment.
[0033] FIG. 17 is a view for explaining a reservoir according to a
modified example of the fifth embodiment.
[0034] FIG. 18 is a view for explaining a reservoir according to a
modified example of the second embodiment.
DETAILED DESCRIPTION
[0035] Hereinafter, the present embodiments will be described with
reference to the attached drawings. In order to facilitate the ease
of understanding, the same reference numerals are attached to the
same constituent elements in each drawing where possible, and
redundant explanations are omitted.
[0036] As shown in FIG. 1, an integrated valve device 6 is used in
a vehicle air conditioner 2 which is installed in a vehicle and
which performs air conditioning in a passenger compartment. The
vehicle air conditioner 2 includes a refrigeration cycle device 3,
a water cycle device 4, and an air conditioning unit 5. The air
conditioning unit 5 is a unit for blowing warm air or cold air into
the passenger compartment. The refrigeration cycle device 3 and the
water cycle device 4 are form a heat pump unit which adjusts the
temperature of the air blown out from the air conditioning unit
5.
[0037] The refrigeration cycle device 3 and the integrated valve
device 6 will be described. The refrigeration cycle device 3
includes a refrigerant flow passage 30, a compressor 31, a
condenser 32, a first heat exchanger 34, a second heat exchanger
35, a reservoir 36, an expansion valve 37, an evaporator 38, and
the integrated valve device 6. The first heat exchanger 34, the
second heat exchanger 35, and the reservoir 36 correspond to the
heat exchanger of the present invention.
[0038] The integrated valve device 6 includes a fixed throttle 61,
a first valve 62, a second valve 64, and a third valve 63. The
water cycle device 4 includes a water flow passage 40, a water pump
41, a water-side heat exchanger 42, and a heater core 43. The air
conditioning unit 5 includes a casing 51, an air mix door 52, a
blower fan 53, and an inside/outside air switching door 54.
[0039] The refrigerant flow passage 30 is a flow passage in which
refrigerant flows, and connects the compressor 31, the condenser
32, the first heat exchanger 34, the second heat exchanger 35, the
reservoir 36, the expansion valve 37, and the evaporator 38. Here,
HFC refrigerant or HFO refrigerant, for example, may be used as
refrigerant. Oil for lubricating the compressor 31 is mixed in the
refrigerant.
[0040] The compressor 31 is an electric compressor and includes an
suction port 311 and a discharge port 312. The compressor 31 sucks
refrigerant from the suction port 311 and compresses the
refrigerant. The compressor 31 discharges the refrigerant, which is
in an overheated state due to being compressed, from the discharge
port 312. The refrigerant discharged from the discharge port 312
flows into the condenser 32.
[0041] The condenser 32 is a conventional heat exchanger and
includes an inlet port 321 and an outlet port 322. The condenser 32
is configured to exchange heat with the water-side heat exchanger
42. Since the condenser 32 and the water-side heat exchanger 42 are
configured so as to be capable of exchanging heat with each other,
they form a water-refrigerant heat exchanger. The high temperature
and high pressure refrigerant discharged from the compressor 31
flows into the condenser 32 from the inlet port 321. The
refrigerant, having flown into the condenser 32, exchanges heat
with water flowing through the water-side heat exchanger 42, and
flows out from the outlet port 322 in a lower temperature state.
The refrigerant flowing out from the outlet port 322 then flows
into the fixed throttle 61 and the first valve 62 which form a part
of the integrated valve device 6.
[0042] When the first valve 62 is closed, the refrigerant is
decompressed through the fixed throttle 61. As such, the pressure
of the refrigerant is reduced, and this low pressure refrigerant
flows into the first heat exchanger 34. Conversely, when the first
valve 62 is opened, the refrigerant is not decompressed and flows
into the first heat exchanger 34 as a high pressure
refrigerant.
[0043] The first heat exchanger 34 is an outside heat exchanger
disposed outside of the passenger compartment, and is configured
heat exchange with outside air. The refrigerant that flows into the
first heat exchanger 34 exchanges heat with the outside air and
then flows into the reservoir 36.
[0044] The reservoir 36 separates gas-phase refrigerant from
liquid-phase refrigerant, and stores the liquid-phase refrigerant.
The separated gas-phase refrigerant then flows into the third valve
63. The gas-phase refrigerant that flows into the third valve 63
then flows toward the compressor 31 when the third valve 63 is
opened. Conversely, the separated liquid-phase refrigerant is
stored in the reservoir 36 and flows out toward the second heat
exchanger 35.
[0045] The second heat exchanger 35 is an outside heat exchanger
disposed outside of the passenger compartment, and is configured
heat exchange with outside air. The second heat exchanger 35
further enhances the heat exchange efficiency of the refrigerant by
cooperating with the first heat exchanger 34 to exchange heat
between the incoming liquid-phase refrigerant and outside air. The
refrigerant that flows out from the second heat exchanger 35 then
flows into the second valve 64.
[0046] The second valve 64 is configured as a three-way valve that
selectively allows the incoming refrigerant to flow toward either
the compressor 31 or the expansion valve 37. The expansion valve 37
decompresses the incoming refrigerant and then discharges the
refrigerant. The refrigerant discharged from the expansion valve 37
then flows toward the evaporator 38. The expansion valve 37 is a
temperature-sensitive mechanical expansion valve that decompresses
and expands the refrigerant flowing into the evaporator 38 such
that the degree of superheating of the refrigerant discharged from
the evaporator 38 falls within a predetermined range.
[0047] The evaporator 38 has an inlet port 381 and an outlet port
382. The refrigerant flowing toward the evaporator 38 flows into
the evaporator 38 from the inlet port 381. Since the evaporator 38
is disposed in the casing 51, the evaporator 38 exchanges heat with
the air flowing in the casing 51. The refrigerant flowing in the
evaporator 38 exchanges heat with the air flowing in the casing 51
and then flows out from the outlet port 382 toward the compressor
31.
[0048] Next, the water cycle device 4 will be described. The water
flow passage 40 is a flow passage in which water flows, and
connects the water pump 41, the water-side heat exchanger 42, and
the heater core 43. The water pump 41 has an inlet port 411 and a
discharge port 412. The water pump 41 sucks in water from the inlet
port 411 and discharges water from the discharge port 412. By
driving the water pump 41, it is possible to form a flow of water
in the water flow passage 40.
[0049] The water discharged from the discharge port 412 due to the
operation of the water pump 41 flows toward the water-side heat
exchanger 42. As described above, the water-side heat exchanger 42
and the condenser 32 form a water-refrigerant heat exchanger. The
water-side heat exchanger 42 has an inlet port 421 and an outlet
port 422. The water that flows into the water-side heat exchanger
42 from the inlet port 421 is heat exchanged with the refrigerant
flowing through the condenser 32, and then flows out from the
outlet port 422. Since the refrigerant flowing through the
condenser 32 is a high temperature and high pressure refrigerant,
the water flowing through the water side heat exchanger 42 is
heated and then flows toward the heater core 43.
[0050] The heater core 43 is disposed in the casing 51 of the air
conditioning unit 5. The heater core 43 is for exchanging heat with
the air flowing in the casing 51. The heater core 43 has an inlet
port 431 and an outlet port 432. Water which is heated by flowing
through the water-side heat exchanger 42 flows into the inlet port
431. The water flowing into the heater core 43 exchanges heat with
the air flowing in the casing 51. The water flowing in the heater
core 43 is reduced in temperature and then flows out from the
outlet port 432 toward the water pump 41.
[0051] Next, the air conditioning unit 5 will be described. The
casing 51 forms a flow passage that carries the conditioned air
that will flow into the passenger compartment. From an upstream
side in the casing 51, the inside/outside air switching door 54,
the blower fan 53, the evaporator 38, the air mix door 52, and the
heater core 43 are arranged.
[0052] The inside/outside air switching door 54 is a door for
switching between intaking the air flowing in the casing 51 from
outside the passenger compartment or inside the passenger
compartment. The blower fan 53 generates an air flow in the casing
51 and sends the conditioned air into the passenger compartment.
The air mix door 52 is a door for switching between whether or not
the air flowing in the casing 51 passes through the heater core
43.
[0053] The vehicle air conditioner 2 is configured to open and
close the respective valves of the integrated valve device 6 to
adjust the amount of refrigerant flowing through the refrigeration
cycle device 3, to drive the water pump 41 to adjust the amount of
water flowing through the water cycle device 4, and to drive the
blower fan 53 to adjust the amount of air flowing through the air
conditioning unit 5, thereby cooling or heating the passenger
compartment.
[0054] With reference to FIG. 2, the operation of the vehicle air
conditioner 2 performing a cooling operation will be described. In
FIG. 2, the flow of the refrigerant is indicated by FLc. During the
cooling operation, the water pump 41 is not driven, and as such no
water flow is generated in the water cycle device 4. Accordingly,
the high-temperature and high-pressure gas-phase refrigerant
discharged from the compressor 31 flows toward the integrated valve
device 6 without undergoing changes. During the cooling operation,
the first valve 62 is in an open state. Accordingly, the
refrigerant flowing from the condenser 32 flows toward the first
heat exchanger 34 without being pressure reduced.
[0055] The high-temperature and high-pressure gas-phase refrigerant
flowing into the first heat exchanger 34 is heat-exchanged with the
outside air. As a result, the temperature of the refrigerant
decreases, and the refrigerant is cooled into a gas-liquid
two-phase refrigerant and flows out to the reservoir 36. During the
cooling operation, the reservoir 36 mainly functions as a receiver
that allows liquid-phase refrigerant to flow out. The third valve
63 is closed, and thus the liquid-phase refrigerant flows out from
the reservoir 36 to the second heat exchanger 35.
[0056] During the cooling operation, the second heat exchanger 35
functions as a subcooler. The refrigerant flowing into the second
heat exchanger 35 is further cooled through heat exchange with the
outside air. During the cooling operation, the first heat exchanger
34 and the second heat exchanger 35 function as a condenser of the
refrigeration cycle device 3.
[0057] The liquid-phase refrigerant that flows out from the second
heat exchanger 35 then flows into the second valve 64. During the
cooling operation, the second valve 64 is switched such that the
incoming refrigerant is only allowed to flow toward the expansion
valve 37. The refrigerant decompressed by the expansion valve 37
flows into the evaporator 38.
[0058] During the cooling operation, the blower fan 53 is driven,
and the air mix door 52 is positioned so as to close the heater
core 43 side. Therefore, the air flowing in the casing 51 is cooled
through heat exchange with the low-temperature refrigerant in the
evaporator 38. The cooled air flows in the casing 51 and is
supplied into the passenger compartment.
[0059] With reference to FIG. 3, the operation of the vehicle air
conditioner 2 performing a heating operation will be described. In
FIG. 3, the flow of the refrigerant is indicated by FLh. During the
heating operation, the water pump 41 is driven, and as such a water
flow is generated in the water cycle device 4. Therefore, the
high-temperature and high-pressure gas-phase refrigerant discharged
from the compressor 31 flows into in the condenser 32, at which
point the refrigerant exchanges heat with the water flowing in the
water-side heat exchanger 42 and is cooled. Then, the refrigerant
flows toward the integrated valve device 6. During the heating
operation, the first valve 62 is in a closed state. Accordingly,
the refrigerant flowing from the condenser 32 is pressure reduced,
and then flows toward the first heat exchanger 34.
[0060] The low-pressure gas-liquid two-phase refrigerant flowing
into the first heat exchanger 34 heat exchanges with the outside
air and evaporates, and then flows out to the reservoir 36. In the
case of the heating operation, the reservoir 36 mainly functions as
an accumulator which allows gas-phase refrigerant to flow out. The
third valve 63 is opened, and thus the gas-phase refrigerant flows
out toward the compressor 31.
[0061] In the reservoir 36, the incoming refrigerant is separated
into gas and liquid-phases, and the liquid-phase refrigerant is
stored. The liquid-phase refrigerant flows out toward the second
heat exchanger 35. The second valve 64 opens a flow passage toward
the suction port 311, and so liquid-phase refrigerant and oil
gradually return to the compressor 31.
[0062] During the heating operation, the blower fan 53 is driven,
and the air mix door 52 is positioned so as to open the heater core
43 side. Therefore, the air flowing in the casing 51 is heated
through heat exchange with high temperature water in the heater
core 43. The heated air flows in the casing 51 and is supplied into
the passenger compartment.
[0063] In the integrated valve device 6 of the present embodiment,
the fixed throttle 61, the first valve 62, the second valve 64, and
the third valve 63 are integrally formed, and may be housed inside
the reservoir 36.
[0064] As shown in FIG. 4, when the integrated valve device 6 is
inserted into and positioned within the reservoir 36, an insertion
end portion 90 is inserted to the lowest position. A fourth outlet
port 74 is provided so as to extend downward from the insertion end
portion 90. Since the first heat exchanger 34 and the second heat
exchanger 35 are disposed on one side of the integrated valve
device 6, the inlet port and outlet port of the integrated valve
device 6 which allow refrigerant to be exchanged with the first
heat exchanger 34 and the second heat exchanger 35 are disposed
toward the side of the first heat exchanger 34 and the second heat
exchanger 35. From this viewpoint, a first outlet port 76, through
which refrigerant flows out to the first heat exchanger 34, is
arranged above the first heat exchanger 34 side. A second inlet
port 75, through which refrigerant flows in from the second heat
exchanger 35, is disposed on the second heat exchanger 35 side and
below the first outlet port 76. A first inlet port 71, A second
outlet port 72, and A third outlet port 73 are provided an opposite
side from the side that faces the first heat exchanger 34 and the
second heat exchanger 35. An inflow passage 12, a gas-phase outflow
passage 13, and a liquid-phase outflow passage 14 will be described
next.
[0065] A heat exchanger 300 according to a first embodiment of the
present invention will be described with reference to FIG. 5. The
heat exchanger 300 described with reference to FIG. 5 is described
while simplifying the descriptions of the first heat exchanger 34,
the second heat exchanger 35, and the reservoir 36 described with
reference to FIGS. 1 to 4 above, and for the sake of convenience,
explanations thereof are omitted except where necessary.
[0066] The heat exchanger 300 includes the first heat exchanger 34
that is an upstream heat exchanging portion, the second heat
exchanger 35 that is a downstream heat exchanging portion, and the
reservoir 36. The first heat exchanger 34 has an upstream core 342
and header tanks 341, 343. In the present embodiment, the
illustrated example is provided with a single upstream core 342,
but two or more cores may be used. The upstream core 342 is a part
that exchanges heat between the refrigerant flowing therein and the
air flowing outside, and includes tubes through which the
refrigerant flows and fins provided between the tubes.
[0067] At the upstream side end of the upstream core 342, the
header tank 341 is attached. At the downstream side end of the
upstream core 342, the header tank 343 is attached.
[0068] An inflow passage 11 is provided in the header tank 341. An
inflow passage 12 is provided in the header tank 343. The
refrigerant flowing in from the inflow passage 11 flows into the
upstream core 342 from the header tank 341. The refrigerant flowing
through the upstream core 342 flows into the header tank 343. The
refrigerant flowing into the header tank 343 flows out to the
inflow passage 12. The inflow passage 12 is connected to the
reservoir 36. The refrigerant flowing out to the inflow passage 12
flows into a main body portion 81 of the reservoir 36.
[0069] The reservoir 36 has the main body portion 81, the inflow
passage 12, the liquid-phase outflow passage 14, and the gas-phase
outflow passage 13. The main body portion 81 is a portion that
separates the gas-liquid two-phase refrigerant flowing in from the
inflow passage 12 into a liquid-phase refrigerant and a gas-phase
refrigerant, and stores the liquid-phase refrigerant.
[0070] The inflow passage 12, the liquid-phase outflow passage 14,
and the gas-phase outflow passage 13 are connected to the main body
portion 81. The inflow passage 12 is a passage that connects the
first heat exchanger 34 to the reservoir 36. The inflow passage 12
is connected to an inlet port 81a provided in the main body portion
81. The liquid-phase outflow passage 14 is a flow passage that
connects the reservoir 36 to the second heat exchanger 35. The
liquid-phase outflow passage 14 is connected to a liquid-phase
outlet port 81c provided in the main body portion 81. The
liquid-phase refrigerant flowing out from the liquid-phase outflow
passage 14 flows into the second heat exchanger 35. The gas-phase
outflow passage 13 is a flow passage that allows gas-phase
refrigerant to flow out from the reservoir 36. The gas-phase
outflow passage 13 is connected to a gas-phase outlet port 81b
provided in the main body portion 81
[0071] The second heat exchanger 35 has a header tank 351, a
downstream core 352, and a header tank 353. The liquid-phase
outflow passage 14 is connected to the header tank 351. The header
tank 351 is provided at the upstream end of the downstream core
352. At the downstream end of the downstream core 352, the header
tank 353 is provided. An outflow passage 15 is connected to the
header tank 353.
[0072] Liquid-phase refrigerant flows from the header tank 351 to
the downstream core 352. The downstream core 352 is a part that
exchanges heat between the refrigerant flowing therein and the air
flowing outside, and includes tubes through which the refrigerant
flows and fins provided between the tubes. Accordingly, the
liquid-phase refrigerant flowing into the downstream core 352 is
directed to the header tank 353 while being subcooled.
[0073] The liquid-phase refrigerant flowing into the header tank
353 from the downstream core 352 then flows out to the outflow
passage 15. The outflow passage 15 is connected to an expansion
valve included in the refrigeration cycle device, and an evaporator
is connected before the expansion valve.
[0074] In the present embodiment, the header tank 341 and the
header tank 353 are formed by partitioning an integrally formed
tank with a partitioning portion 356. Similarly, the header tank
343 and the header tank 351 are formed by partitioning an
integrally formed tank with the partitioning portion 356.
[0075] The liquid-phase outflow passage 14 is connected to the
reservoir 36 on the lower side, and the inflow passage 12 is
connected at a higher point as compared to the liquid-phase outflow
passage 14. The inflow passage 12 is connected at a point higher
than the middle of the reservoir 36 in the longitudinal direction.
In FIG. 4, the height of the reservoir 36 is the height until the
lower end 90 of the fourth outlet port 74. The height of the
reservoir 36 is defined as a height limit at which liquid
refrigerant can be substantially stored.
[0076] As shown in FIG. 6, the height of the reservoir 36 is set by
stack up "leak over years", "load fluctuation buffer", "surplus
etc." on top of each other. "Leakage over years" refers to an
expected amount of refrigerant that leaks from various parts over a
number of years of use when the heat exchanger 2 is used for the
refrigeration cycle. "Load fluctuation buffer" is an expected
amount of fluctuation in the amount of liquid-phase refrigerant
that flows in during the operation of the refrigeration cycle.
Since the combined height of "leakage over years" and "load
fluctuation buffer" is liquid surface height required in the design
of the reservoir 36, the inflow passage 12 is preferably provided
above this height.
[0077] As shown in FIG. 7, a partition portion 82 and a buffer
portion 83 are provided in the main body portion 81 of the
reservoir 36. The partition portion 82 is a cylindrical portion
extending downward from the gas-phase outflow passage 13. The
buffer portion 83 is connected to the lower end of the partition
portion 82 and is provided so as to gradually increase in diameter
from the lower end of the partition portion 82.
[0078] During the cooling operation, In the case where the incoming
refrigerant from the inflow passage 12 is substantially
liquid-phase refrigerant, the incoming refrigerant will hit the
buffer portion 83 and then continue toward the liquid surface.
Therefore, the refrigerant does not directly hit the liquid surface
of the liquid-phase refrigerant accumulated inside, and
disturbances of the liquid surface can be suppressed.
[0079] As shown in FIG. 8, during the heating operation, when the
refrigerant flowing in from the inflow passage 12 is substantially
gas-phase refrigerant, gas-liquid separation is performed while
swirling around the partition portion 82. The gas-liquid separated
liquid-phase refrigerant falls down while hitting the buffer
section 83. Therefore, the refrigerant does not directly hit the
liquid surface of the liquid-phase refrigerant accumulated inside,
and disturbances of the liquid surface can be suppressed. Since the
liquid-phase refrigerant may be separated in this manner, the
gas-phase refrigerant enters the partition portion 82 from the
lower end of the buffer portion 83 and flows out from the gas-phase
outflow passage 13.
[0080] From the viewpoint of suppressing disturbances of the liquid
surface, as shown in FIGS. 9 and 10, in a reservoir 36A of a second
embodiment, the interior of the reservoir 36A is preferably divided
into a plurality of spaces. A main reservoir space 811A and an
auxiliary reservoir space 812A are formed in a main body portion
81A of the reservoir 36A.
[0081] As shown in FIG. 10, when the refrigerant flows in from the
inflow passage 12, the refrigerant is distributed to the main
reservoir space 811A and the auxiliary reservoir space 812A, and
the liquid-phase refrigerant is stored. In the present embodiment,
a partition wall 814 A for partitioning the main reservoir space
811A from the auxiliary reservoir space 812A is provided high
enough to face the inflow passage 12, and a communication passage
813A is provided above the partition wall 814A. The partition wall
814A is not necessarily provided at a position high enough to face
the inflow passage 12, and may be provided to a lower position
instead.
[0082] In a reservoir 36B according to a third embodiment shown in
FIG. 11, a partition portion 82B and a buffer portion 83B are
provided in the main body portion 81. The partition portion 82B is
a cylindrical portion extending downward from the gas-phase outflow
passage 13. The buffer portion 83B is connected to the lower end of
the partition portion 82B, and is configured as a disk-shaped
member.
[0083] As shown in FIG. 12, which is a view along the direction of
the arrow A in FIG. 11, the disk-like buffer portion 83B is formed
by a disk member 831. The disk member 831 is provided with an
outflow hole 84B connected to the gas-phase outflow passage 13.
Four notches 832 are provided along the periphery of the disk
member 831.
[0084] As a modified example, a buffer portion 83Ba as shown in
FIG. 13 may be formed by a disc member 831a. The disk member 831a,
is provided with four dropdown holes 833 around the outflow hole
84B. In this manner, it is possible to stop the swirling flow of
the gas-liquid two-phase refrigerant flowing in from the inflow
passage 12 while suppressing any gas-liquid separated liquid-phase
refrigerant from directly hitting the liquid surface. Accordingly,
gas-phase refrigerant can be sent out to the gas-phase outflow
passage 13.
[0085] FIG. 14 shows a reservoir 36C according to a fourth
embodiment. The reservoir 36C is provided with a partition portion
82C and a buffer portion 83C in the main body portion 81. The
partition portion 82C is a cylindrical portion extending downward
from the gas-phase outflow passage 13. The buffer portion 83C is
provided below the partition portion 82C, and is a plate member
extending from the inner wall of the main body portion 81.
[0086] FIG. 15 is a cross-sectional view taken along a cross
section orthogonal to the axis passing through a center 815, which
is the central axis of a reservoir 36D in the longitudinal
direction according to a fifth embodiment. According to the
reservoir 36D, the mounting position and the mounting angle of an
inflow passage 12D with respect to the main body 81 is designed so
as to reduce disturbances in the liquid surface caused by
liquid-phase refrigerant flowing into and vigorously hitting the
accumulated liquid-phase refrigerant.
[0087] The inflow passage 12D is provided with respect to the main
body portion 81 such that if the inflow passage 12D is extended
along a center line 121D, the inflow passage 12D does not pass
through the center 815 of the reservoir 36D. As shown in the cross
section view of FIG. 15, the center line 121D of the inflow passage
12D is a line that substantially equally divides the width of the
inflow passage 12D along the flow direction of the refrigerant.
[0088] The inflow passage 12D is provided such that the gas-liquid
two-phase refrigerant which flows through the inflow passage 12D
then flows in from an inlet port 81aD collides with an inner wall
surface 816 of the reservoir 36D and then falls into the
liquid-phase refrigerant stored in the reservoir.
[0089] The reservoir 36D is provided such that a distance Ld from
the inflow port 81aD to an inner wall surface portion 816aD of the
reservoir 36D which faces the inflow port 81aD is shorter than a
distance d between the farthest portions of the inner wall surface
816 of the reservoir 36D.
[0090] Since the main body portion 81 is substantially cylindrical,
the center 815 is the center of the circular cross section. The
distance d between the farthest portions of the inner wall surface
816 of the reservoir 36D is the diameter of the inner wall surface
816. Accordingly, the inner wall surface 816 of the reservoir 36D
has a substantially circular cross section, and the distance Ld
from the inflow port 81aD to the inner wall surface 816aD of the
reservoir 36D which faces the inflow port 81aD is shorter than the
diameter d of the inner wall surface 816.
[0091] FIG. 16 shows a reservoir 36E according to a modified
example of the fifth embodiment. In the reservoir 36E, an inflow
port 81aE is placed further upward as compared to the inflow port
81aD shown in FIG. 15. When only considering the position of the
inflow port 81aE, the inflow port 81aE is located at a position
that directly faces toward the center 815 of the main body portion
81. However, by changing the angle of an inflow passage 12E, the
inflow passage 12E is provided with respect to the main body
portion 81 such that if a center line 121E of the inflow passage
12E is extended, the inflow passage 12E does not pass through the
center 815 of the reservoir 36E.
[0092] The inflow passage 12E is provided such that the gas-liquid
two-phase refrigerant which flows through the inflow passage 12E
then flows in from the inlet port 81aE collides with the inner wall
surface 816 of the reservoir 36E and then falls into the
liquid-phase refrigerant stored in the reservoir 36E.
[0093] The reservoir 36E is provided such that a distance Le from
the inflow port 81aE to an inner wall surface portion 816aE of the
reservoir 36E which faces the inflow port 81aE is shorter than a
distance d between the farthest portions of the inner wall surface
816 of the reservoir 36E.
[0094] Since the main body portion 81 is substantially cylindrical,
the center 815 is the center of the circular cross section. The
distance d between the farthest portions of the inner wall surface
816 of the reservoir 36E is the diameter of the inner wall surface
816. Accordingly, the inner wall surface 816 of the reservoir 36E
has a substantially circular cross section, and the distance Le
from the inflow port 81aE to the inner wall surface 816aE of the
reservoir 36E which faces the inflow port 81aE is shorter than the
diameter d of the inner wall surface 816.
[0095] FIG. 17 shows a reservoir 36F according to a modified
example of the fifth embodiment. In the reservoir 36F, an inflow
port 81aF is moved downward in the figure as compared to the inflow
port 81aD shown in FIG. 15. Similarly, an inflow passage 12F is
also moved downward in the figure. Here, by moving the inflow
passage 12F downward in the figure and without changing the angle
of the inflow passage 12F, the inflow passage 12F is provided with
respect to the main body portion 81 such that if a center line 121F
of the inflow passage 12F is extended, the inflow passage 12F does
not pass through the center 815 of the reservoir 36F.
[0096] The inflow passage 12F is provided such that the gas-liquid
two-phase refrigerant which flows through the inflow passage 12F
then flows in from the inlet port 81aF collides with the inner wall
surface 816 of the reservoir 36F and then falls into the
liquid-phase refrigerant stored in the reservoir 36F.
[0097] The reservoir 36F is provided such that a distance Lf from
the inflow port 81aF to an inner wall surface portion 816aF of the
reservoir 36F which faces the inflow port 81aF is shorter than a
distance d between the farthest portions of the inner wall surface
816 of the reservoir 36F.
[0098] The inner wall surface 816 of the reservoir 36F has a
substantially circular cross section, and the distance Lf from the
inflow port 81aF to the inner wall surface 816aF of the reservoir
36F which faces the inflow port 81aF is shorter than the diameter d
of the inner wall surface 816.
[0099] Further, a part of the inner wall surface 122F of the inflow
passage 12F is disposed so as to follow the tangent of the inner
wall surface 816 of the reservoir 36F.
[0100] Similar to the reservoir 36A described with reference to
FIGS. 9 and 10, the same effects can be obtained by designing the
arrangement of the inflow passage 12. FIG. 18 shows a reservoir 36G
as a modified example of the reservoir 36A, and shows a cross
section corresponding to the cross section shown in FIG. 9
[0101] An inflow passage 12G is provided with respect to a main
body portion 81G such that if a center line 121G of the inflow
passage 12G is extended, the center line 121G does not pass through
a center 812Ga of an auxiliary reservoir space 812G. As shown in
the cross section view of FIG. 18, the center line 121G of the
inflow passage 12G is a line that substantially equally divides the
width of the inflow passage 12G along the flow direction of the
refrigerant.
[0102] The inflow passage 12G is provided such that the gas-liquid
two-phase refrigerant which flows through the inflow passage 12G
then flows in from an inlet port 81aG collides with an inner wall
surface 812Gb of the auxiliary reservoir space 812G, and then falls
into the liquid-phase refrigerant stored in the auxiliary reservoir
space 812G.
[0103] The auxiliary reservoir space 812G is provided such that a
distance Lg2 from the inflow port 81aG to an opposing inner wall
surface 812Gc is shorter than a distance d2 between the farthest
portions of the inner wall surface 812Gb of the auxiliary reservoir
space 812G.
[0104] The arrangement of a communication passage 813G that
connects the auxiliary reservoir space 812G to a main reservoir
space 811G may be designed similarly to the arrangement of the
inflow passage 12G. The communication passage 813G is provided such
that if a center line 813Ga of the communication passage 813G is
extended, the center line 813Ga does not pass through a center
811Ga of the main reservoir space 811G. As shown in the cross
section view of FIG. 18, the center line 813Ga of the communication
passage 813G is a line that substantially equally divides the width
of the communication passage 813G along the flow direction of the
refrigerant.
[0105] Since the main reservoir space 811G is substantially
cylindrical, the center 811Ga is the center of the circular cross
section. The distance d1 between the farthest portions of an inner
wall surface 811Gb of the main reservoir space 811G is the diameter
of the inner wall surface 811Gb. Accordingly, the inner wall
surface 811Gb has a substantially circular cross section, and a
distance Lg1 from the inlet port 811Gc connected to the main
reservoir space 811G to an inner wall surface portion 811Gd that
faces the inlet port 811Gc is shorter than the diameter d1 of the
inner wall surface 811Gb.
[0106] As described above, the heat exchanger 300 according to the
present embodiment includes the first heat exchanger 34 which is an
upstream heat exchanging portion that exchanges heat between a
refrigerant passing through therein and air, the reservoir 36, 36A,
36B, 36C, 36D, 36E, 36F, 36G that performs gas-liquid separation on
a gas-liquid two-phase refrigerant that flows out from the first
heat exchanger 34 into a gas-phase refrigerant and a liquid-phase
refrigerant, the reservoir 36, 36A, 36B, 36C, 36D, 36E, 36F, 36G
storing the liquid-phase refrigerant, the inflow passage 12, 12D,
12E, 12F, 12G that allows the gas-liquid two-phase refrigerant
flowing out from the first heat exchanger 34 to flow into the
reservoir 36, 36A, 36B, 36C, 36D, 36E, 36F, 36G, the gas-phase
outflow passage 13 that allows the gas-phase refrigerant to flow
out from the reservoir 36, 36A, 36B, 36C, 36D, 36E, 36F, 36G, and
the liquid-phase outflow passage 14 that allows the liquid-phase
refrigerant to flow out from the reservoir 36, 36A, 36B, 36C, 36D,
36E, 36F, 36G. The inflow passage 12, 12D, 12E, 12F, 12G is
connected so as to be in communication with the inlet port 81a,
81aD, 81aE, 81aF, 81aG which is disposed above a liquid surface of
the liquid-phase refrigerant stored in the reservoir 36, 36A, 36B,
36C, 36D, 36E, 36F, 36G, the gas-phase outflow passage 13 is
connected so as to be in communication with a gas-phase outlet port
81b which is disposed above the liquid surface of the liquid-phase
refrigerant stored in the reservoir 36, 36A, 36B, 36C, 36D, 36E,
36F, 36G, and the liquid-phase outflow passage 14 is connected so
as to be in communication with a liquid-phase outlet port 81c which
is disposed below the liquid surface of the liquid-phase
refrigerant stored in the reservoir 36, 36A, 36B, 36C, 36D, 36E,
36F, 36G.
[0107] According to the present embodiment, since the refrigerant
flows in from above the liquid surface, gas-phase refrigerant does
not flow into the liquid-phase refrigerant stored in the reservoir,
and it is possible to suppress disturbances in the liquid
surface.
[0108] Further, according to the present embodiment, the reservoir
36, 36A, 36B, 36C, 36D, 36E, 36F, 36G includes the partition
portion 82, 82B, 82C between the inlet port 81a and the gas-phase
outlet port 81b.
[0109] By providing a partition portion between the inlet port and
the gas-phase outlet port, the refrigerant flowing in from the
inlet port hits the partition portion before flowing out from the
gas-phase outlet port, and continues downward. Therefore, it is
possible to suppress the liquid-phase refrigerant from flowing out
of the gas-phase outlet port 81b.
[0110] Further according to the present embodiment, the partition
portion 82, 82B, 82C is disposed such that at least a portion
thereof faces the inlet port 81a. Due to this facing arrangement,
it is possible to ensure that the refrigerant flowing in from the
inlet port 81a collides with the partition portion 82, 82B,
82C.
[0111] Further according to the present embodiment, the buffer
portion 83, 83B, 83C is provided between the inlet port 81a and the
liquid surface of the liquid-phase refrigerant. By providing the
buffer portion 83, 83 B, 83 C, it is possible to prevent the
refrigerant flowing in from the inlet port 81a from directly
falling onto the liquid surface, and it is possible to reduce
disturbances of the liquid surface.
[0112] Further according to the present embodiment, at least part
of the buffer portion 83, 83B, 83C is arranged between the inlet
port 81a and the liquid-phase outlet port 81c, and is disposed
closer toward the liquid surface as compared to the inlet port 81a.
Due to this positioning, the liquid-phase refrigerant flowing in
from the inlet port 81a will more reliably collide with the buffer
portion 83, 83B, 83C, and it is possible to prevent disturbances in
the liquid surface.
[0113] In the present embodiment, the reservoirs 36, 36B, 36C each
have a substantially cylindrical main body portion 81 capable of
storing the liquid-phase refrigerant therein, and the body portions
81 to the inner wall is preferably equal to or less than one-third
of the radius of the main body 81.
[0114] With such a configuration, it is possible to suppress
disturbances in the liquid surface.
[0115] Further according to the present embodiment, the inflow
passage 12D, 12E, 12F, 12G is disposed such that if the center line
121D, 121E, 121F, 121G of the inflow passage 12D, 12E, 12F, 12G is
extended, the center line 121D, 121E, 121F, 121G reaches the inner
wall surface 816, 812Gb of the reservoir 36D, 36E, 36F, 36G without
passing through the center 815, 812Ga of the reservoir 36D, 36E,
36F, 36G.
[0116] With such a configuration, the gas-liquid two-phase
refrigerant flowing in from the inflow passage 12D, 12E, 12F, 12G
is able to hit the inner wall surface 816, 812Gb of the reservoir
36D, 36E, 36F, 36G and then fall down. Accordingly, it is possible
to prevent the incoming refrigerant from directly falling into the
liquid-phase refrigerant stored in the reservoir 36D, 36E, 36F,
36G, thereby suppressing disturbances in the liquid surface of the
liquid-phase refrigerant.
[0117] Further according to the present embodiment, the inflow
passage 12D, 12E, 12F, 12G is provided such that the gas-liquid
two-phase refrigerant which flows through the inflow passage 12D,
12E, 12F, 12G then flows in from the inlet port 81aD, 81aE, 81aF,
81aG collides with the inner wall surface 816, 812Gb of the
reservoir 36D, 36E, 36F, 36G and then falls into the liquid-phase
refrigerant stored in the reservoir 36D, 36E, 36F, 36G.
[0118] With such a configuration, the gas-liquid two-phase
refrigerant flowing in from the inflow passage 12D, 12E, 12F, 12G
is able to reliably hit the inner wall surface 816, 812Gb of the
reservoir 36D, 36E, 36F, 36G and then fall down.
[0119] Further according to the present embodiment, the distance
Ld, Le, Lf, Lg1, Lg2 from the inlet port 81aD, 81aE, 81aF, 81aG to
an inner wall surface portion 816aD, 816aE, 816aG, 811Gd, 812Gc of
the reservoir 36D, 36E, 36F, 36G that faces the inlet port 81aD,
81aE, 81aF, 81aG is shorter than a distance d, d1, d2 between the
farthest portions of the inner wall surface of the reservoir 36D,
36E, 36F, 36G.
[0120] With such a configuration, the gas-liquid two-phase
refrigerant flowing in from the inflow passage 12D, 12E, 12F, 12G
is able to reliably hit the inner wall surface 816, 812Gb of the
reservoir 36D, 36E, 36F, 36G and then fall down.
[0121] Further according to the present embodiment, the inner wall
surface 816, 812Gb of the reservoir 36D, 36E, 36F, 36G has a
substantially circular cross section, and the distance Ld, Le, Lf,
Lg1 from the inlet port 81aD, 81aE, 81aF, 81aG to the inner wall
surface portion 816aD, 816aE, 816aG, 811Gd of the reservoir 36D,
36E, 36F, 36G that faces the inlet port 81aD, 81aE, 81aF, 81aG is
shorter than the diameter d, d1 of the reservoir 36D, 36E, 36F,
36G.
[0122] With such a configuration, the incoming gas-liquid two-phase
refrigerant is able to reliably hit the inner wall surface 816,
811Gb of the reservoir 36D, 36E, 36F, 36G and then fall down.
[0123] Further according to the present embodiment, a part of the
inner wall surface 122F of the inflow passage 12F is disposed so as
to follow the tangent of the inner wall surface 816 of the
reservoir 36F.
[0124] With such a configuration, the incoming gas-liquid two-phase
refrigerant is able to reliably hit the inner wall surface 816 of
the reservoir 36F and then fall down.
[0125] The present embodiments have been described with reference
to specific examples above. However, the present disclosure is not
limited to these specific examples. Those skilled in the art
appropriately design modifications to these specific examples,
which are also included in the scope of the present disclosure as
long as they have the features of the present disclosure. The
elements, the arrangement, the conditions, the shape, etc. of the
specific examples described above are not limited to those
exemplified and can be appropriately modified. The combinations of
elements included in each of the above described specific examples
can be appropriately modified as long as no technical inconsistency
occurs.
* * * * *