U.S. patent application number 16/841260 was filed with the patent office on 2020-07-23 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 | 20200232726 16/841260 |
Document ID | / |
Family ID | 66100861 |
Filed Date | 2020-07-23 |
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United States Patent
Application |
20200232726 |
Kind Code |
A1 |
SUGIMURA; Ryohei ; et
al. |
July 23, 2020 |
HEAT EXCHANGER
Abstract
A heat exchanger has an inflow port through which refrigerant
flows, a cooling outflow port through which the refrigerant flows
out during a cooling operation, and a heating outflow port through
which the refrigerant flows out during a heating operation. A
distance between the inflow port and the heating outflow port is
shorter than a distance between the inflow port and the cooling
outflow port.
Inventors: |
SUGIMURA; Ryohei;
(Kariya-city, JP) ; KAWAKUBO; Masaaki;
(Kariya-city, JP) ; KATO; Daiki; (Kariya-city,
JP) ; ITO; Tetsuya; (Kariya-city, JP) ; MIEDA;
Hiroshi; (Kariya-city, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
DENSO CORPORATION |
Kariya-city |
|
JP |
|
|
Family ID: |
66100861 |
Appl. No.: |
16/841260 |
Filed: |
April 6, 2020 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
PCT/JP2018/037044 |
Oct 3, 2018 |
|
|
|
16841260 |
|
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Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F25B 41/003 20130101;
F25B 39/02 20130101; F25B 6/04 20130101; F25B 39/04 20130101; F25B
41/04 20130101; F25B 39/00 20130101; F25B 29/003 20130101; F28F
13/06 20130101; F25B 5/04 20130101; B60H 1/32 20130101 |
International
Class: |
F28F 13/06 20060101
F28F013/06; F25B 29/00 20060101 F25B029/00; F25B 41/00 20060101
F25B041/00; F25B 41/04 20060101 F25B041/04 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 11, 2017 |
JP |
2017-197822 |
Claims
1. A heat exchanger for a heat pump system that performs a cooling
operation and a heating operation, the heat exchanger comprising: a
heat exchanging portion configured to perform heat exchange between
a refrigerant and an outside air during the cooling operation and
the heating operation; a refrigerant adjustment unit that is
integrally joined with a liquid reservoir that stores liquid
refrigerant, and that switches a flow of the refrigerant during the
cooling operation and the heating operation; an inflow port into
which the refrigerant flows; a cooling outflow port through which
the refrigerant flows out during the cooling operation; and a
heating outflow port through which the refrigerant flows out during
the heating operation, wherein a distance between the inflow port
and the heating outflow port is shorter than a distance between the
inflow port and the cooling outflow port.
2. The heat exchanger according to claim 1, wherein a heat transfer
member is provided between the inflow port and the heating outflow
port.
3. The heat exchanger according to claim 2, wherein the inflow
port, the heating outflow port, and the heat transfer member are
configured by a single connector component.
4. The heat exchanger according to claim 3, wherein the connector
component is connected so that a space between the inflow port and
the heating outflow port is filled with the heat transfer
member.
5. The heat exchanger according to claim 3, wherein the cooling
outflow port is provided in a component different from the
connector component.
6. The heat exchanger according to claim 1, wherein the inflow port
and the heating outflow port are arranged such that a flow
direction of the refrigerant at the inflow port is opposite to a
flow direction of the refrigerant at the heating outflow port.
7. The heat exchanger according to claim 1, wherein the inflow
port, the heating outflow port, and the cooling outflow port are
arranged in this order in a longitudinal direction of the liquid
reservoir.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] This application is a continuation application of
International Patent Application No. PCT/JP2018/037044 filed on
Oct. 3, 2018, which designated the U.S. and based on and claims the
benefits of priority of Japanese Patent Application No. 2017-197822
filed on Oct. 11, 2017. The entire disclosure of all of the above
applications is incorporated herein by reference.
TECHNICAL FIELD
[0002] The present disclosure relates to a heat exchanger used in a
heat pump system that performs a cooling operation and a heating
operation.
BACKGROUND
[0003] A heat exchanger used in a heat pump system performs a
cooling operation and a heating operation.
SUMMARY
[0004] An object of the present disclosure is to provide a heat
exchanger that is capable of improving heating performance and
cooling performance and suppressing generation of abnormal noise
during the cooling operation.
[0005] A heat exchanger of the present embodiment is a heat
exchanger used for a heat pump system that performs a cooling
operation and a heating operation. The heat exchanger includes a
heat exchanging portion that performs heat exchange between the
refrigerant and the outside air during the cooling operation and
the heating operation, and a refrigerant adjustment unit that is
integrally joined to a liquid reservoir that stores liquid
refrigerant, and that switches the flow of the refrigerant during
the cooling operation and the heating operation. The heat exchanger
has an inflow port through which the refrigerant flows, a cooling
outflow port through which the refrigerant flows out during the
cooling operation, and a heating outflow port through which the
refrigerant flows out during the heating operation. A distance
between the inflow port and the heating outflow port is shorter
than a distance between the inflow port and the cooling outflow
port.
BRIEF DESCRIPTION OF DRAWINGS
[0006] FIG. 1 is a diagram illustrating a heat exchanger according
to one embodiment;
[0007] FIG. 2 is a diagram showing an example of a refrigeration
cycle using the heat exchanger shown in FIG. 1;
[0008] FIG. 3 is a diagram showing a heat exchanger as a
modification;
[0009] FIG. 4 is a diagram showing a heat exchanger as a
modification;
[0010] FIG. 5 is a diagram showing a heat exchanger as a
modification;
[0011] FIG. 6 is a diagram for explaining a connector component
shown in FIG. 1;
[0012] FIG. 7 is a diagram for explaining the connector component
shown in FIG. 1;
[0013] FIG. 8 is a diagram for explaining a connector component
shown in FIG. 3; and
[0014] FIG. 9 is a diagram for explaining the connector component
shown in FIG. 3.
DETAILED DESCRIPTION
[0015] 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.
[0016] As shown in FIG. 1, a heat exchanger 2 according to a
present embodiment includes an upstream heat exchanging portion 20,
a downstream heat exchanging portion 21, and a liquid reservoir 22.
The upstream heat exchanging portion 20 has two upstream cores 201,
202 and header tanks 203, 204, 205. In the present embodiment, as
the illustrated example, the upstream heat exchanging portion 20
has two upstream cores 201, 202, but a single core or three or more
cores may be used. The upstream cores 201, 202 are parts that
exchange 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.
[0017] At the upstream end of the upstream core 201, the header
tank 203 is attached. At the downstream end of the upstream core
202, the header tank 205 is attached. At the downstream end of the
upstream core 201 and the upstream end of the upstream core 202,
the header tank 204 extending across the both of the upstream cores
201, 202 is attached.
[0018] The connection channel 221 is connected to the header tank
203. The connection channel 222 is connected to the header tank
205. The refrigerant flowing in from the connection channel 221
flows into the upstream core 201 through the header tank 203. The
refrigerant flowing through the upstream core 201 flows into the
header tank 204. The refrigerant flowing through the header tank
204 flows into the upstream core 202. The refrigerant flowing
through the upstream core 202 flows into the header tank 205. The
refrigerant flowing into the header tank 205 flows out to the
connection channel 222.
[0019] The connection channel 222 is a flow channel provided in the
liquid reservoir 22. The connection channel 222 is connected to a
liquid reserve space 224 of the liquid reservoir 22. The
refrigerant flowing out to the connection channel 222 flows into a
liquid reserve space 224.
[0020] The liquid reservoir 22 has a substantially cylindrical
shape in which a liquid reserve space 224 is formed. The liquid
reserve space 224 is a portion that separates the gas-liquid
two-phase refrigerant flowing therein from the connection channel
222 into a liquid-phase refrigerant and a gas-phase refrigerant,
and reserves the liquid-phase refrigerant. The liquid reservoir 22
includes an inflow channel 225, the connection channel 221, the
connection channel 222, a heating outflow channel 226, and a
connection channel 223. An inflow port 225a is formed at an end of
the inflow channel 225. A heating outflow port 226a is formed at an
end of the heating outflow channel 226.
[0021] The connection channel 222, the connection channel 223, and
an outflow channel 112 are connected to the liquid reserve space
224. The connection channel 222 is a channel connecting the
upstream heat exchanging portion 20 and the liquid reservoir 22.
The connection channel 223 is a channel connecting the liquid
reservoir 22 and the downstream heat exchanging portion 21. The
liquid-phase refrigerant flowing out from the connection channel
223 flows into the downstream heat exchanging portion 21. The
outflow channel 112 is a flow passage that allows gas-phase
refrigerant to flow out from the liquid reservoir 22.
[0022] The downstream heat exchanging portion 21 has a header tank
211, a downstream core 212, and a header tank 213. A cooling
outflow channel 227 is connected to the header tank 213. A cooling
outflow port 227a is formed at an end of the cooling outflow
channel 227. The header tank 213 is provided at a downstream end of
the downstream core 212. At the upstream end of the downstream core
212, the header tank 211 is provided. The connection channel 223 is
connected to the header tank 211.
[0023] The liquid-phase refrigerant flows from the connection
channel 223 into the header tank 211, and the liquid-phase
refrigerant flows from the header tank 211 into the downstream core
212. The downstream core 212 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 212 is directed to the
header tank 213 while being subcooled.
[0024] The liquid-phase refrigerant flowing into the header tank
213 from the downstream core 212 flows out to the cooling outflow
channel 227. The cooling outflow channel 227 is connected to a
channel connected to an expansion valve constituting a
refrigeration cycle device at the cooling outflow port 227a, and an
evaporator is connected to a position beyond the expansion
valve.
[0025] A refrigerant adjustment unit 10 is provided above the
liquid reservoir 22. The refrigerant adjustment unit 10 includes an
inflow channel 110, an outflow channel 111, an outflow channel 112,
and a connection channel 113. The inflow channel 110 is arranged so
as to be connected to the inflow channel 225. The outflow channel
111 is arranged so as to be connected to the heating outflow
channel 226. The outflow channel 112 is provided so as to
communicate with the liquid reserve space 224, and is connected to
the outflow channel 111 inside the refrigerant adjustment unit 10.
The connection channel 113 is arranged so as to be connected to the
connection channel 221.
[0026] The inflow channel 225 and the inflow channel 110 are flow
channels into which the high-pressure refrigerant flowing from a
compressor flows. The connection channel 221 and the connection
channel 113 are flow channels through which the inflowing
refrigerant is let out at high pressure or at low pressure as it is
and flows out toward the upstream heat exchanging portion 20.
[0027] The outflow channel 112 is a flow channel into which the
gas-phase refrigerant flowing out of the liquid reserve space 224
flows. The outflow channel 111 is a flow channel which sends the
refrigerant flowing into the outflow channel 112 to the
compressor.
[0028] The refrigerant adjustment unit 10 includes a throttle 101,
an on-off valve 102, and a flow control valve 103. The throttle
101, the on-off valve 102, and the flow control valve 103 will be
described later together with an example of a refrigeration cycle
to which the heat exchanger 2 is applied.
[0029] Subsequently, an example of a refrigeration cycle to which
the heat exchanger 2 of the present embodiment is applied will be
described with reference to FIG. 2. As shown in FIG. 2, the
refrigeration cycle device 71 is applied to a vehicle air
conditioner 7. The vehicle air conditioner is a device that adjusts
the temperature inside the vehicle compartment by adjusting the
temperature of the air blown into the vehicle compartment which is
the air-conditioning target space. The vehicle air conditioner 7
includes the refrigeration cycle device 71, a cooling water circuit
72, and an air-conditioning unit 73.
[0030] The refrigeration cycle device 71 is configured to
selectively switch between a cooling mode for cooling the vehicle
compartment by cooling the blown air and a heating mode for heating
the vehicle compartment by heating the blown air. The refrigeration
cycle device 71 is a compression type refrigeration cycle device
constituted of a heat pump circuit in which the refrigerant
circulates.
[0031] The refrigeration cycle device 71 includes a decompressor
30, an evaporator 31, an accumulator 32, a compressor 33, a
water-cooled condenser 34, and a heat exchanger 2. Here, HFC
refrigerant or HFO refrigerant, for example, may be used as the
refrigerant circulating in the refrigeration cycle device 71. Oil,
i.e. refrigerating machine oil, for lubricating the compressor 33
is mixed in the refrigerant. Therefore, a part of the refrigerating
machine oil circulates in the refrigeration cycle device 71
together with the refrigerant.
[0032] The compressor 33 draws the refrigerant through an intake
port, compresses the refrigerant, and discharges the compressed
refrigerant in a superheated state in the refrigeration cycle
device 71. The compressor 33 is an electric compressor. The
refrigerant discharged from a discharge port flows into the
water-cooled condenser 34.
[0033] The water-cooled condenser 34 is a well-known
water-refrigerant heat exchanger. The water-cooled condenser 34 has
a first heat exchanging portion 341 and a second heat exchanging
portion 342.
[0034] The first heat exchanging portion 341 is located between the
discharge port of the compressor 33 and the heat exchanger 2. That
is, the refrigerant discharged from the compressor 33 flows through
the first heat exchanging portion 341.
[0035] The second heat exchanging portion 342 is provided in the
middle of the cooling water circuit 72 through which the engine
cooling water flows. In the cooling water circuit 72, the cooling
water circulates by a cooling pump 37. The cooling water
circulates, in order, the second heat exchanging portion 342, a
heater core 35, a cooling pump 37, and an engine 36.
[0036] The water-cooled condenser 34 cools the refrigerant by
performing a heat exchange between the refrigerant flowing through
the first heat exchanging portion 341 and the cooling water flowing
through the second heat exchanging portion 342. The refrigerant
flowing out of the first heat exchanging portion 341 flows to the
refrigerant adjustment unit 10 of the heat exchanger 2.
[0037] In the cooling water circuit 72, the refrigerant heated by
the engine 36 and the second heat exchanging portion 342 flows
through the heater core 35, and thus the heater core 35 is heated.
The heater core 35 is disposed in a casing 39 of the
air-conditioning unit 73. The heater core 35 heats the blown air by
exchanging heat between the cooling water flowing through the
heater core 35 and the blown air flowing through the casing 39. The
water-cooled condenser 34 functions as a radiator that indirectly
radiates heat of the refrigerant discharged from the compressor 33
and flowing into the first heat exchanging portion 341 to the blown
air through the cooling water and the heater core 35.
[0038] The throttle 101 and the on-off valve 102 of the refrigerant
adjustment unit 10 function as a pressure adjustment unit. The
throttle 101 and the on-off valve 102 correspond to a pressure
regulation portion that adjusts a pressure of the refrigerant
flowing into the upstream heat exchanging portion 20 so as to
switch between the heating mode in which the refrigerant absorbs
heat in the upstream heat exchanging portion 20 of the heat
exchanger 2 from the outside air and the cooling mode in which the
refrigerant releases heat to the outside air.
[0039] The refrigerant flowing out of the first heat exchanging
portion 341 of the water-cooled condenser 34 flows to the throttle
101 through the inflow channel 225. The throttle 101 decompresses
and discharges the refrigerant flowing out from the first heat
exchanging portion 341 of the water-cooled condenser 34. As the
throttle 101, for example, a nozzle or an orifice with a fixed
aperture can be used, but a nozzle or an orifice with a variable
aperture can also be used. The refrigerant discharged from the
throttle 101 flows through the connection channel 221 to the
upstream heat exchanging portion 20.
[0040] A bypass channel 114 is a refrigerant flow channel that
guides the refrigerant flowing out of the first heat exchanging
portion 341 to the upstream heat exchanging portion 20 while
bypassing the throttle 601. The on-off valve 102 is a solenoid
valve that opens and closes the bypass channel 114.
[0041] In the heating mode, the on-off valve 102 is closed. As a
result, in the heating mode, the refrigerant flowing out of the
first heat exchanging portion 341 of the water-cooled condenser 34
flows through the throttle 101, so that the refrigerant is
decompressed and flows to the upstream heat exchanging portion
20.
[0042] In contrast, the on-off valve 102 is fully closed in the
cooling mode. As a result, in the cooling mode, the refrigerant
flowing out of the first heat exchanging portion 341 of the
water-cooled condenser 34 bypasses the throttle 101 and flows
through the bypass channel 114. The refrigerant flowing out of the
first heat exchanging portion 341 flows to the upstream heat
exchanging portion 20 without being decompressed.
[0043] The heat exchanger 2 is an outdoor heat exchanger located on
a vehicle front side in the engine room. The heat exchanger 2
includes the upstream heat exchanging portion 20, the liquid
reservoir 22, the downstream heat exchanging portion 21, and the
refrigerant adjustment unit 10.
[0044] The refrigerant flowing out of the throttle 101 and the
on-off valve 102 as a pressure adjusting unit flows into the
upstream heat exchanging portion 20. The upstream heat exchanging
portion 20 exchanges heat between the refrigerant flowing therein
and the outside air that is the air outside the vehicle compartment
blown by a blower fan (not shown). In the heating mode, the
upstream heat exchanging portion 20 works as an evaporator that
evaporates the refrigerant by performing a heat exchange between
the refrigerant flowing therein and the outside air. In the cooling
mode, the upstream heat exchanging portion 20 works as a condenser
that cools the refrigerant by performing a heat exchange between
the refrigerant flowing therein and the outside air.
[0045] The liquid reservoir 22 separates the refrigerant flowing
out from the upstream heat exchanging portion 20 into a gas-phase
refrigerant and a liquid-phase refrigerant, discharges the
gas-phase refrigerant and the liquid-phase refrigerant separately,
and stores the liquid-phase refrigerant. The liquid reservoir 22
discharges the separated gas-phase refrigerant to the heating
outflow channel 226 and discharges the separated liquid-phase
refrigerant to the cooling outflow channel 227.
[0046] The heating outflow channel 226 is connected to the
refrigerant channel 712 at the heating outflow port 226a. The
refrigerant channel 712 is connected to a part of the refrigerant
channel 711. The refrigerant channel 711 is a passage that guides
the refrigerant flowing out from the decompressor 30 to the intake
port of the compressor 33. The heating outflow channel 226 is a
passage that guides the gas-phase refrigerant discharged from the
liquid reservoir 22 to the compressor 33.
[0047] The liquid-phase refrigerant flows into the downstream heat
exchanging portion 21 from the liquid reservoir 22. The downstream
heat exchanging portion 21 further improves the heat exchange
efficiency of the refrigerant in the heat exchanger 2 by exchanging
heat between the incoming liquid-phase refrigerant and the outside
air. Specifically, the downstream heat exchanging portion 21
evaporates, in the heating mode, the liquid-phase refrigerant by
exchanging heat between the liquid-phase refrigerant flowing
therein and the outside air. As a result, since the liquid-phase
refrigerant remaining without being evaporated in the upstream heat
exchanging portion 20 can be evaporated, the function as the
evaporator in the heat exchanger 2 is improved. However, since the
number of tubes is small and the refrigerant passage area is small
due to the small installation space, the downstream heat exchanging
portion 21 may be operated without flowing the refrigerant in order
to avoid an increase in refrigerant pressure loss. In the cooling
mode, the downstream heat exchanging portion 21 works as a
subcooler that further cools the liquid-phase refrigerant by
performing a heat exchange between the refrigerant flowing therein
and the outside air. As a result, the function of the heat
exchanger 2 as a condenser is improved.
[0048] The refrigerant flowing out of the downstream heat
exchanging portion 21 flows into the decompressor 30 through the
cooling outflow channel 227 and the refrigerant channel 713
connected to the cooling outflow channel 227. The decompressor 30
decompresses the incoming refrigerant and then discharges the
refrigerant. The refrigerant decompressed by the decompressor 30
flows into the evaporator 31. In addition, the refrigerant
discharged from the evaporator 31 flows into the decompressor 30.
The decompressor 30 is a thermosensitive mechanical expansion valve
that decompresses and expands the refrigerant flowing into the
evaporator 31 such that the degree of superheating of the
refrigerant discharged from the evaporator 31 falls within a
predetermined range.
[0049] The refrigerant discharged from the decompressor 30 flows
into the evaporator 31. The evaporator 31 is a heat exchanger that
cools the blown air by exchanging heat between the refrigerant
flowing therein and the blowing air flowing through the casing 39
of the air-conditioning unit 73 in the cooling mode. In the
evaporator 31, heat exchange is performed between the blown air and
the refrigerant, whereby the refrigerant is evaporated. The
evaporated refrigerant is discharged from the evaporator 31 and
flows into the intake port of the compressor 33 via the
decompressor 30 and the refrigerant channel 711.
[0050] The flow control valve 103 is provided at an intermediate
position from the outflow channel 112 to the heating outflow
channel 226. The flow control valve 103 is an electromagnetic valve
that can change the cross-sectional area of the heating outflow
channel 226 by adjusting an opening degree. By adjusting the
opening of the flow control valve 103, the flow rate of the
refrigerant flowing through the heating outflow channel 226 can be
adjusted.
[0051] The air-conditioning unit 73 includes the casing 39 and an
air passage switching door 38. The blown air flows through the
casing 39. The evaporator 31 and the heater core 35 are arranged in
the casing 39 in order from the upstream side to the downstream
side of the blown air. The evaporator 31 cools the blown air by
exchanging heat between the refrigerant flowing therein and the
blown air. A warm-air passage in which the heater core 35 is
provided and a cold-air passage in which the heater core 35 is not
provided are located downstream of the evaporator 31 in the casing
39.
[0052] The air passage switching door 38 is configured to switch
its position between a first door position illustrated with a solid
line at which the cold-air passage is closed and the warm-air
passage is opened and a second door position illustrated with a
dashed line at which the warm-air passage is closed and the
cold-air passage is opened. Multiple opening portions (not shown)
that are open in the vehicle compartment are located downstream of
the warm-air passage and the cold-air passage in the casing 39.
[0053] In the air-conditioning unit 73, the air passage switching
door 38 is positioned at the first door position illustrated with
the solid line in the heating mode. As a result, since the blown
air passing through the evaporator 31 flows through the warm-air
passage, the blown air is heated by the heater core 35 and flows to
the downstream side. On the other hand, the air passage switching
door 38 is positioned at the second door position illustrated with
the dashed line in the cooling mode. Thus, since the blown air
passing through the evaporator 31 flows through the cold-air
passage, the blown air cooled by the evaporator 31 flows directly
to the downstream side.
[0054] The heat exchanger 2 of the present embodiment is a heat
exchanger used for a heat pump system that performs a cooling
operation and a heating operation. The heat exchanger 2 includes an
upstream heat exchanging portion 20 and a downstream heat
exchanging portion 21 that are heat exchangers that perform heat
exchange between the refrigerant and the outside air during the
cooling operation and the heating operation, and a refrigerant
adjustment unit 10 that is integrally joined to the liquid
reservoir 22 that stores liquid refrigerant, and that switches the
flow of the refrigerant during the cooling operation and the
heating operation. The heat exchanger 2 has an inflow port 225a
through which the refrigerant flows, a cooling outflow port 227a
through which the refrigerant flows out during the cooling
operation, and a heating outflow port 226a through which the
refrigerant flows out during the heating operation. The distance
between the inflow port 225a and the heating outflow port 226a is
shorter than the distance between the inflow port 225a and the
cooling outflow port 227a.
[0055] In the present embodiment, the distance between the inflow
port 225a and the heating outflow port 226a is shorter than the
distance between the inflow port 225a and the cooling outflow port
227a, so that the heat transfer between the inflow port 225a and
the heating outflow port 226a is promoted. Therefore, during the
heating operation, the difference between the enthalpy of the
refrigerant before entering the heat exchanger 2 and the enthalpy
of the refrigerant after leaving the heat exchanger 2 increases, so
that the heating performance is improved. Further, since the
dryness of the gas-liquid two-phase refrigerant introduced from the
inflow port 225a decreases, the density of the refrigerant
increases and the pressure loss of the refrigerant decreases, so
that the heating performance is improved. Further, as the dryness
of the gas-liquid two-phase refrigerant introduced from the inflow
port 225a decreases, the liquid-phase component of the gas-liquid
two-phase refrigerant increases, so that the distribution
performance of the refrigerant improves and the heating performance
improves.
[0056] In the present embodiment, the distance between the inflow
port 225a and the cooling outflow port 227a is longer than the
distance between the inflow port 225a and the heating outflow port
226a, so that the heat transfer between the inflow port 225a and
the cooling outflow port 227a can be suppressed. When the heat
transfer between the inflow port 225a and the cooling outflow port
227a is promoted, there is a concern that the compressor power may
be deteriorated due to a decrease in the enthalpy difference, or a
problem may occur due to a decrease in the degree of supercooling.
By suppressing the heat transfer between the inflow port 225a and
the cooling outflow port 227a, it is possible to suppress
compressor power deterioration due to a decrease in the enthalpy
difference. Further, by suppressing the decrease in the degree of
supercooling, it is possible to avoid a decrease in cooling
performance due to an increase in refrigerant pressure loss and a
deterioration in distribution of the evaporator 31 as the dryness
of the refrigerant flowing into the evaporator 31 increases.
Further, generation of abnormal noise due to mixing of the
gas-phase refrigerant into the refrigerant flowing into the
decompressor 30 can also be suppressed.
[0057] In the heat exchanger 2 of the present embodiment, a heat
transfer member 27 is provided between the inflow port 225a and the
heating outflow port 226a. In the present embodiment, a part of the
side wall of the liquid reservoir 22 between the inflow channel 225
and the heating outflow channel 226 is the heat transfer member 27.
By providing the heat transfer member 27 between the inflow port
225a and the heating outflow port 226a, the heat transfer between
the inflow port 225a and the heating outflow port 226a can be
further promoted.
[0058] Further, in the heat exchanger 2 of the present embodiment,
as shown in FIGS. 1, 6, and 7, the inflow port 225a and the heating
outflow port 226a are formed by a single connector component 25.
FIG. 6 is a diagram showing the connector component 25 in FIG. 1
more specifically. FIG. 7 is a diagram showing the connector
component 25 from the direction looking straight at the inflow port
225a and the heating outflow port 226a in FIG. 6. Further, like the
heat exchanger 2A shown in FIGS. 3, 8, and 9, the inflow port
225Aa, the heating outflow port 226Aa, and the heat transfer member
27A can be configured by a single connector component 25A. FIG. 8
is a diagram more specifically showing the connector component 25A
in FIG. 3. FIG. 9 is a diagram showing the connector component 25A
from the direction looking straight at the inflow port 225Aa and
the heating outflow port 226Aa in FIG. 8. By configuring the inflow
port 225Aa, the heating outflow port 226Aa, and the heat transfer
member 27A with a single connector component 25A, it is possible to
easily realize a configuration that promotes heat transfer between
the inflow port 225Aa and the heating outflow port 226Aa.
[0059] Further, the connector component 25A is connected so that
the space between the inflow port 225Aa and the heating outflow
port 226Aa is filled with the heat transfer member 27A. Since the
inflow port 225Aa and the heating outflow port 226Aa are connected
by the heat transfer member 27A, a sufficient heat transfer path
can be secured, and the heat transfer between the inflow port 225Aa
and the heating outflow port 226Aa is further promoted.
[0060] Further, in the heat exchanger 2 and the heat exchanger 2A
of the present embodiment, the cooling outflow port 227a is
provided in a component different from the connector components 25
and 25A. More specifically, the cooling outflow port 227a is
provided at an end of the cooling outflow channel 227 connected to
the header tank 213 constituting the downstream heat exchanging
portion 21. Since the cooling outflow port 227a is provided on a
part different from the connector components 25, 25A equipped with
the inflow ports 225a, 225Aa and the heating outflow ports 226a,
226Aa, the heat transfer between the inflow ports 225a, 225Aa and
the cooling outflow ports 227a can be suppressed.
[0061] Further, as in the heat exchanger 2B shown in FIG. 4, a
cooling outflow port 227Ba can be provided in the liquid reservoir
22B. In the heat exchanger 2B, only the upstream heat exchanging
portion 20B is provided, and the heat exchange portion
corresponding to the downstream heat exchanging portion 21 is not
provided. The cooling outflow port 227Ba is provided at an end of a
cooling outflow channel 227B connected to the liquid reservoir
22B.
[0062] Further, in the heat exchangers 2, 2A, 2B of the present
embodiment, the inflow ports 225a, 225Aa and the heating outflow
ports 226a, 226Aa are arranged so that a flow direction of the
refrigerant at the inflow ports 225a, 225Aa is opposite to a flow
direction of the refrigerant at the heating outflow ports 226a,
226Aa. Since the flow direction of the refrigerant at the inflow
ports 225a, 225Aa is opposite to the flow direction of the
refrigerant at the heating outflow ports 226a, 226Aa, the heat
transfer between the inflow ports 225a, 225Aa and the heating
outflow ports 226a, 226Aa is more improved.
[0063] In the heat exchangers 2, 2A, 2B of the present embodiment,
the inflow ports 225a, 225Aa, the heating outflow ports 226a,
226Aa, and the cooling outflow ports 227a, 227Ba are arranged in
this order in a longitudinal direction of the liquid reservoirs 22,
22B.
[0064] Since the cooling outflow ports 227a, 227Ba are not arranged
between the inflow ports 225a, 225Aa and the heating outflow ports
226a, 226Aa, the heat transfer between the inflow ports 225a, 225Aa
and the heating outflow ports 226a, 226Aa can be promoted. The
heating outflow ports 226a, 226Aa are disposed between the inflow
ports 225a, 225Aa and the cooling outflow ports 227a, 227Ba, the
heating outflow ports 226a, 226Aa. Therefore, under the cooling
operation, the heating outflow ports 226a, 226Aa and the flow
channels connected thereto function as a heat insulating layer, and
the heat transfer between the inflow ports 225a, 225Aa and the
cooling outflow ports 227a, 227Ba can be suppressed, and heat
damage can be avoided.
[0065] Further, as in the heat exchanger 2C shown in FIG. 5, the
refrigerant flowing from the connection channel 222 may be directly
introduced into the refrigerant adjustment unit 10C. The
refrigerant flowing from the connection channel 222 flows into the
refrigerant adjustment unit 10C from the refrigerant introduction
port 115C. As shown in FIG. 5, when the flow control valve 103C is
located at the uppermost position, the outflow channel 112C is
opened, and the refrigerant flows into the liquid reserve space
224. On the other hand, when the flow control valve 103C is located
at the lowest position, the outflow channel 112C is closed, and the
refrigerant flows toward the heating outflow port 226a.
[0066] The 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.
[0067] In an assumable example, regarding a heat exchanger used in
a heat pump system that performs a cooling operation and a heating
operation, the heat exchanger described in Patent Document 1 (JP
2009-236404 A) is known. In the heat exchanger described in Patent
Document 1, during the cooling operation, a high-temperature and
high-pressure gas-phase refrigerant flows into a condensing heat
exchange part, is cooled, becomes a gas-liquid two-phase
refrigerant, and the gas-liquid two-phase refrigerant flows into a
liquid receiving part. The liquid-phase refrigerant obtained by
saturating the gas-liquid two-phase refrigerant flowing into the
liquid receiving part flows into the supercooling heat exchange
part, is supercooled, and then flows into a utilizing side heat
exchanger. On the other hand, during the heating operation, the
low-pressure gas-liquid two-phase refrigerant flows into the
condensing heat exchange part, performs heat exchange in the
condensing heat exchange part, evaporates, becomes a gaseous
refrigerant, and then flows into the liquid receiving part. The
gas-phase refrigerant flowing into the liquid receiving part is
returned to a compressor without flowing through the supercooling
heat exchange part.
[0068] The heat exchanger in Patent Document 1 has following
problems to be solved during the heating operation. As a first
problem during the heating operation, only the condensing heat
exchange part is used during the heating operation, and the
supercooling heat exchange part is not used. Therefore, the entire
core portion of the heat exchanger cannot be used. There is a
problem that the heating performance is low for product
constitution. As a second problem during the heating operation, a
gas-phase refrigerant with a large specific volume flows around the
supercooling heat exchanging part, and refrigerant pressure loss
becomes high. Therefore, there is a problem that the heating
performance becomes low. As a third problem during the heating
operation, since the gas-liquid two-phase refrigerant is introduced
from above into the core portion of the heat exchanger,
distribution property of the refrigerant flowing through the
condensing heat exchange part deteriorates. Therefore, there is a
problem that the heating performance is reduced.
[0069] The heat exchanger in Patent Document 1 has following
problems to be solved during the cooling operation. As a first
problem during the cooling operation, in the case where a
refrigerant adjusting part which is integrally connected to a
liquid reservoir for storing a liquid refrigerant and switches a
flow of the refrigerant during the cooling operation and the
heating operation is provided, the refrigerant flowing into the
refrigerant adjusting part becomes a high-temperature and
high-pressure gas-phase refrigerant. Therefore, there is a problem
that the refrigerant flowing in the heat exchanger is heated, the
degree of supercooling is insufficient, and the cooling performance
is reduced. As a second problem during the cooling operation, the
degree of supercooling is insufficient, and the gas-phase
refrigerant is mixed into the refrigerant flowing into an expansion
valve. Therefore, there is a problem that an abnormal noise is
generated.
[0070] An object of the present disclosure is to provide a heat
exchanger that is capable of improving heating performance and
cooling performance and suppressing generation of abnormal noise
during the cooling operation.
[0071] A heat exchanger of the present embodiment is a heat
exchanger used for a heat pump system that performs a cooling
operation and a heating operation. The heat exchanger includes a
heat exchanging portion that performs heat exchange between the
refrigerant and the outside air during the cooling operation and
the heating operation, and a refrigerant adjustment unit that is
integrally joined to a liquid reservoir that stores liquid
refrigerant, and that switches the flow of the refrigerant during
the cooling operation and the heating operation. The heat exchanger
has an inflow port through which the refrigerant flows, a cooling
outflow port through which the refrigerant flows out during the
cooling operation, and a heating outflow port through which the
refrigerant flows out during the heating operation. A distance
between the inflow port and the heating outflow port is shorter
than a distance between the inflow port and the cooling outflow
port.
[0072] The distance between the inflow port and the heating outflow
port is shorter than the distance between the inflow port and the
cooling outflow port, so that the heat transfer between the inflow
port and the heating outflow port is promoted. Therefore, during
the heating operation, the difference between the enthalpy of the
refrigerant before entering the heat exchanger and the enthalpy of
the refrigerant after leaving the heat exchanger increases, so that
the heating performance is improved. Further, since the dryness of
the gas-liquid two-phase refrigerant introduced from the inflow
port decreases, the density of the refrigerant increases and the
pressure loss of the refrigerant decreases, so that the heating
performance is improved. Further, as the dryness of the gas-liquid
two-phase refrigerant introduced from the inflow port decreases,
the liquid-phase component of the gas-liquid two-phase refrigerant
increases, so that the distribution performance of the refrigerant
improves and the heating performance improves.
[0073] The distance between the inflow port and the heating outflow
port is shorter than the distance between the inflow port and the
cooling outflow port, so that the heat transfer between the inflow
port and the heating outflow port is promoted. When the heat
transfer between the inflow port and the cooling outflow port is
promoted, there is a concern that the compressor power may be
deteriorated due to a decrease in the enthalpy difference, or a
problem may occur due to a decrease in the degree of supercooling.
By suppressing the heat transfer between the inflow port and the
cooling outflow port, it is possible to suppress compressor power
deterioration due to a decrease in the enthalpy difference.
Further, by suppressing the decrease in the degree of supercooling,
it is possible to avoid a decrease in cooling performance due to an
increase in refrigerant pressure loss and a deterioration in
distribution of the evaporator as the dryness of the refrigerant
flowing into the evaporator increases. Further, generation of
abnormal noise due to mixing of the gas-phase refrigerant into the
refrigerant flowing into the decompressor can also be
suppressed.
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