TECHNICAL FIELD
[0001] The present invention relates to a plate-type heat exchanger and a refrigeration
cycle apparatus, particularly, a plate-type heat exchanger having a plurality of heat
exchange areas, as well as a refrigeration cycle apparatus including the plate-type
heat exchanger.
BACKGROUND ART
[0002] A plate-type heat exchanger having a plurality of heat exchange areas has been known.
Such a plate-type heat exchanger is described in, for example, Japanese Patent Laying-Open
No.
2005-106385 (Patent Literature 1). The plate-type heat exchanger described in this publication
has two heat exchange areas (a condensation portion and a supercooling portion) divided
based on a state of refrigerant, and each of the two heat exchange areas is provided
with a flow path for a heated fluid and a flow path for the refrigerant. The flow
path for the refrigerant is provided with a liquid receiver located between the condensation
portion and the supercooling portion and disposed external to the heat exchanger.
The heated fluid exchanges heat, in the supercooling portion, with the refrigerant
liquefied in the liquid receiver after being condensed by the condensation portion,
and then exchanges heat, in the condensation portion, with the refrigerant that is
in an overheated state before being supplied to the liquid receiver.
[0003] The above-described plate-type heat exchanger has a boundary plate (partition plate)
for separating the condensation portion from the supercooling portion. The flow path
for the heated fluid, which is located closest to the supercooling portion side in
the condensation portion, is provided adjacent to the flow path for the refrigerant,
which is located closest to the condensation portion side in the supercooling portion,
with the boundary plate being interposed therebetween.
CITATION LIST
PATENT LITERATURE
[0004] PTL 1: Japanese Patent Laying-Open No.
2005-106385
SUMMARY OF INVENTION
TECHNICAL PROBLEM
[0005] However, in the above-described plate-type heat exchanger, a comparatively large
differential pressure is formed between the heated fluid in the condensation portion
and the refrigerant in the supercooling portion. When the maximum pressure of the
refrigerant is maintained to be comparatively high without fluctuations, the differential
pressure is always applied to the boundary plate. As a result, the partition plate
thus always fed with the differential pressure is deformed gradually to result in
breakage, disadvantageously.
[0006] Moreover, the above-described differential pressure may be repeatedly fluctuated
depending on an operating condition of the refrigeration cycle apparatus. This is
due to the following reason: pressure of the refrigerant may be fluctuated depending
on the operating condition, load, and the like, whereas pressure of the heated fluid
is less fluctuated depending on the operating condition than the pressure of the refrigerant.
The partition plate repeatedly fed with the fluctuated differential pressure is slightly
deformed repeatedly to result in breakage due to fatigue, disadvantageously.
[0007] That is, in the above-described plate-type heat exchanger, a risk of the partition
plate being damaged is high, and therefore the plate-type heat exchanger does not
have sufficiently high reliability, disadvantageously.
[0008] A main object of the present invention is to provide a plate-type heat exchanger
and a refrigeration cycle apparatus, in each of which a partition plate is suppressed
from being broken and each of which has sufficiently high reliability.
SOLUTION TO PROBLEM
[0009] A plate-type heat exchanger according to the present invention includes: a first
heat exchanging unit and a second heat exchanging unit each having a plurality of
heat transfer plates stacked in a first direction; and a partition plate disposed
between the first heat exchanging unit and the second heat exchanging unit in the
first direction, the partition plate having a first side and a second side in the
first direction, the first side facing the heat transfer plates of the first heat
exchanging unit, the second side facing the heat transfer plates of the second heat
exchanging unit. The first heat exchanging unit has: a first flow path in which a
first fluid flows in a second direction crossing the first direction; and a second
flow path in which a second fluid flows in a third direction crossing the first direction.
In the first heat exchanging unit, the first flow path or the second flow path is
provided between heat transfer plates adjacent in the first direction among the plurality
of heat transfer plates. The first flow path and the second flow path are provided
alternately in the first direction. The second heat exchanging unit has: a third flow
path in which the first fluid flows in a fourth direction crossing the first direction;
and a fourth flow path in which a third fluid flows in a fifth direction crossing
the first direction. In the second heat exchanging unit, the third flow path or the
fourth flow path is provided between heat transfer plates adjacent in the first direction
among the plurality of heat transfer plates. The third flow path and the fourth flow
path are provided alternately in the first direction. The partition plate is provided
with a flow port via which the first fluid flows from the first flow path to the third
flow path. A distance from at least a portion of the first flow path to the partition
plate is shorter than a distance from the second flow path to the partition plate.
A distance from at least a portion of the third flow path to the partition plate is
shorter than a distance from the fourth flow path to the partition plate.
ADVANTAGEOUS EFFECTS OF INVENTION
[0010] According to the present invention, there can be provided a plate-type heat exchanger
and a refrigeration cycle apparatus, in each of which a partition plate is suppressed
from being broken and each of which has sufficiently high reliability.
BRIEF DESCRIPTION OF DRAWINGS
[0011]
Fig. 1 (a) is a perspective view showing a plate-type heat exchanger according to
a first embodiment when viewed from the side of one entrance/exit plate, and Fig.
1 (b) is a perspective view showing the plate-type heat exchanger according to the
first embodiment when viewed from the side of the other entrance/exit plate.
Fig. 2 shows an exemplary flow path for each fluid in the plate-type heat exchanger
according to the first embodiment.
Fig. 3 is an exploded view showing an exemplary configuration of the plate-type heat
exchanger according to the first embodiment.
Fig. 4 is a plan view showing an exemplary first heat transfer plate of the plate-type
heat exchanger according to the first embodiment.
Fig. 5 is a side view of the first heat transfer plate shown in Fig. 4.
Fig. 6 is a plan view showing an exemplary partition plate of the plate-type heat
exchanger according to the first embodiment.
Fig. 7 is a side view of the partition plate shown in Fig. 6.
Fig. 8 is a partial cross sectional view along a long side direction of the partition
plate, and shows the exemplary partition plate of the plate-type heat exchanger according
to the first embodiment as well as an exemplary heat transfer plate disposed close
to the partition plate.
Fig. 9 is a plan view showing an exemplary first entrance/exit plate of the plate-type
heat exchanger according to the first embodiment.
Fig. 10 is a side view of the first entrance/exit plate shown in Fig. 9.
Fig. 11 is a plan view showing an exemplary second entrance/exit plate of the plate-type
heat exchanger according to the first embodiment.
Fig. 12 is a side view of the first entrance/exit plate shown in Fig. 11.
Fig. 13 is a schematic view showing an exemplary refrigeration cycle apparatus including
the plate-type heat exchanger according to the first embodiment.
Fig. 14 is an exploded view showing an exemplary configuration of a plate-type heat
exchanger according to a second embodiment.
Fig. 15 is a cross sectional view showing an exemplary second flow path formed close
to a first entrance/exit plate of the plate-type heat exchanger according to the second
embodiment.
Fig. 16 is a cross sectional view showing an exemplary fourth flow path formed close
to a second entrance/exit plate of the plate-type heat exchanger according to the
second embodiment.
Fig. 17 is a cross sectional view showing an exemplary partition plate of a plate-type
heat exchanger according to a third embodiment.
Fig. 18 is a cross sectional view showing an exemplary heat transfer plate of the
plate-type heat exchanger according to the third embodiment.
Fig. 19 is a cross sectional view showing an exemplary first entrance/exit plate of
the plate-type heat exchanger according to the third embodiment.
Fig. 20 is a cross sectional view showing an exemplary second entrance/exit plate
of the plate-type heat exchanger according to the third embodiment.
Fig. 21 is a cross sectional view showing another exemplary partition plate of the
plate-type heat exchanger according to the third embodiment.
Fig. 22 is a cross sectional view showing another exemplary first entrance/exit plate
of the plate-type heat exchanger according to the third embodiment.
Fig. 23 is a cross sectional view showing another exemplary second entrance/exit plate
of the plate-type heat exchanger according to the third embodiment.
DESCRIPTION OF EMBODIMENTS
[0012] The following describes embodiments of the present invention with reference to figures.
It should be noted that in the below-described figures, the same or corresponding
portions in the figures are given the same reference characters and are not described
repeatedly.
First Embodiment.
<Plate-Type Heat Exchanger>
[0013] As shown in Fig. 1 to Fig. 3, a plate-type heat exchanger 100 according to a first
embodiment will be described. Plate-type heat exchanger 100 includes: a first heat
exchanging unit 10 and a second heat exchanging unit 20 each having a plurality of
heat transfer plates 1 stacked in a first direction; and a partition plate 2.
[0014] First heat exchanging unit 10 is provided to allow for heat exchange between a first
fluid and a second fluid via heat transfer plates 1. Between heat transfer plates
1 adjacent in the first direction in first heat exchanging unit 10, a first flow path
5 and a second flow path 6 are provided alternately. In first flow path 5, the first
fluid flows in a second direction crossing the first direction, and in second flow
path 6, the second fluid flows in a third direction crossing the first direction.
In first heat exchanging unit 10, first flow path 5 and second flow path 6 are disposed
to be adjacent to each other with one heat transfer plate 1 being interposed therebetween.
A plurality of first flow paths 5 and a plurality of second flow paths 6 may be provided.
When the plurality of first flow paths 5 are provided, the first fluid flows through
below-described passage holes 11, 13 of heat transfer plates 1, flows through a distribution
path 61 extending along the first direction, and is distributed to respective first
flow paths 5. Further, the flows of the first fluid distributed to respective first
flow paths 5 pass through below-described passage holes 12, 15 of heat transfer plates
1, and enter a distribution path 62 extending along the first direction and are therefore
merged. When the plurality of second flow paths 6 are provided, the second fluid flows
through below-described passage holes 11, 13 of heat transfer plates 1, flows through
a distribution path 63 extending along the first direction, and is distributed to
respective second flow paths 6. Further, the flows of the second fluid distributed
to respective second flow paths 6 pass through below-described passage holes 12, 15
of heat transfer plates 1, and enter a distribution path 64 extending along the first
direction and are therefore merged.
[0015] Second heat exchanging unit 20 is provided to allow for heat exchange between the
first fluid and a third fluid via heat transfer plates 1. Between heat transfer plates
1 adjacent in the first direction in second heat exchanging unit 20, a third flow
path 7 and a fourth flow path 8 are provided alternately. In third path 7, the first
fluid flows in a fourth direction crossing the first direction, and in fourth flow
path 8, the third fluid flows in a fifth direction crossing the first direction. In
second heat exchanging unit 20, third flow path 7 and fourth flow path 8 are disposed
to be adjacent to each other with one heat transfer plate 1 being interposed therebetween.
A plurality of third flow paths 7 and a plurality of fourth flow paths 8 may be provided.
When the plurality of third flow paths 7 are provided, the first fluid flows through
below-described passage holes 12, 15 of heat transfer plates 1, flows through a distribution
path 65 extending along the first direction, and is distributed to respective third
flow paths 7. Further, the flows of the first fluid distributed to respective second
flow paths 7 pass through below-described passage holes 11, 13 of heat transfer plates
1, and enter a distribution path 66 extending along the first direction and are therefore
merged. When the plurality of fourth flow paths 8 are provided, the third fluid flows
through below-described passage holes 11, 12, 13, 15 of heat transfer plates 1, flows
through a distribution path 67 extending along the first direction, and is distributed
to respective fourth flow paths 8. Further, the flows of the third fluid distributed
to respective fourth flow paths 8 pass through below-described passage holes 11, 13
of heat transfer plates 1, and enter a distribution path 68 extending along the first
direction and are therefore merged.
[0016] Partition plate 2 is disposed between first heat exchanging unit 10 and second heat
exchanging unit 20 in the first direction. Partition plate 2 has a first side (hereinafter,
referred to as "front side") and a second side (hereinafter, referred to as "back
side") in the first direction, the first side facing heat transfer plates 1 of first
heat exchanging unit 10, the second side facing heat transfer plates 1 of second heat
exchanging unit 20. Partition plate 2 is provided with a flow port 21 (see Fig. 3)
via which the first fluid flows from first flow path 5 in first heat exchanging unit
10 to third flow path 7 in second heat exchanging unit 20.
[0017] First flow path 5 has a first portion 5A located close to partition plate 2 relative
to second flow path 6. First flow path 5 has first portion 5A located close to partition
plate 2 relative to a second portion 6A of second flow path 6 closest to partition
plate 2. In other words, as shown in Fig. 3, first portion 5A of first flow path 5
closest to partition plate 2 is close to partition plate 2 relative to second portion
6A of second flow path 6 closest to partition plate 2.
[0018] Third flow path 7 has a third portion 7A located close to partition plate 2 relative
to fourth flow path 8. Third flow path 7 has third portion 7A located close to partition
plate 2 relative to a fourth portion 8A of fourth flow path 8 closest to partition
plate 2. In other words, third portion 7A of third flow path 7 closest to partition
plate 2 is close to partition plate 2 relative to fourth portion 8A of fourth flow
path 8 closest to partition plate 2.
[0019] First portion 5A of first flow path 5 closest to partition plate 2 is connected to
third portion 7A of third flow path 7 closest to partition plate 2, via flow port
21 of partition plate 2.
[0020] In this way, a differential pressure between the first fluid flowing in first flow
path 5 and the first fluid flowing in third flow path 7 is applied to partition plate
2 that partitions between first heat exchanging unit 10 and second heat exchanging
unit 20. The first fluid flowing in third flow path 7 is the first fluid having flowed
in first flow path 5, having passed through flow port 21 of partition plate 2, and
having reached third flow path 7. Therefore, the differential pressure between the
first fluid flowing in first flow path 5 and the first fluid flowing in third flow
path 7 is smaller than a differential pressure between the first fluid and the second
fluid, a differential pressure between the first fluid and the third fluid, and a
differential pressure between the second fluid and the third fluid. Accordingly, partition
plate 2 is suppressed from being broken in plate-type heat exchanger 100 and plate-type
heat exchanger 100 has sufficiently high reliability. It should be noted that the
first direction is a direction along a horizontal direction, for example. Each of
the second direction, the third direction, the fourth direction, and the fifth direction
is a direction along a vertical direction, for example.
<Exemplary Configurations of Plates>
[0021] Next, the following describes an exemplary configuration of each plate of plate-type
heat exchanger 100. As shown in Fig. 3, plate-type heat exchanger 100 includes the
plurality of heat transfer plates 1, partition plate 2, a first entrance/exit plate
3, and a second entrance/exit plate 4. First entrance/exit plate 3 is disposed to
sandwich first heat exchanging unit 10 between first entrance/exit plate 3 and partition
plate 2 in the first direction. Second entrance/exit plate 4 is disposed to sandwich
second heat exchanging unit 20 between second entrance/exit plate 4 and partition
plate 2 in the first direction. The planar shape of each of heat transfer plates 1,
partition plate 2, first entrance/exit plate 3, and second entrance/exit plate 4 is
a substantially rectangular shape, for example.
[0022] As shown in Fig. 3 to Fig. 5, four passage holes 11, 12, 13, 15, in each of which
one of the first to third fluids flows, are provided at an outer peripheral portion
(four corners) of each heat transfer plate 1. Each of passage holes 11, 12, 13, 15
extends through heat transfer plate 1 in the thickness direction (the first direction).
Passage hole 11 and passage hole 12 are provided to face each other with a space therebetween
in the long side direction of heat transfer plate 1, and passage hole 13 and passage
hole 15 are provided to face each other with a space therebetween in the long side
direction of heat transfer plate 1. Further, passage hole 11 and passage hole 15 are
provided to face each other with a space therebetween in the short side direction
of heat transfer plate 1, and passage hole 12 and passage hole 13 are provided to
face each other with a space therebetween in the short side direction of heat transfer
plate 1. Passage holes 13, 15 are provided in top surfaces of protrusions 14, 16 protruding
in the thickness direction relative to surfaces in which passage holes 11, 12 are
provided, respectively. The top surfaces of protrusions 14, 16 in heat transfer plate
1 are in contact with the other heat transfer plate 1, partition plate 2, or first
entrance/exit plate 3, each of which is adjacent thereto at the front side in the
first direction.
[0023] As shown in Fig. 4, in heat transfer plate 1, a heat transfer surface 17 having a
wavelike cross sectional shape is provided internal to passage holes 11, 12, 13, 15,
for example. When heat transfer surface 17 is viewed in a plan view, top portions
18 and bottom portions 19 of the wavelike structure of heat transfer surface 17 form
a herringbone pattern, for example.
[0024] As shown in Fig. 3, first heat exchanging unit 10 includes heat transfer plates 1a,
1b, 1c, 1d in the order from the one closest to partition plate 2. Second heat exchanging
unit 20 includes heat transfer plates 1e, If, 1g, 1h in the order from the one closest
to partition plate 2. Each of heat transfer plates 1a, 1b, 1c, 1d, 1e, If, 1g, 1h
has the same configuration.
[0025] As shown in Fig. 3, in first heat exchanging unit 10, the plurality of heat transfer
plates 1 are stacked with the plurality of heat transfer plates 1 being disposed alternately
upside down, for example. For example, passage hole 11 of certain heat transfer plate
1c is provided to overlap, in the first direction, with each passage hole 13 of heat
transfer plates 1b, 1d adjacent to this heat transfer plate 1c. For example, passage
hole 12 of certain heat transfer plate 1c is provided to overlap, in the first direction,
with each passage hole 15 of heat transfer plates 1b, 1d adjacent to this heat transfer
plate 1c. Similarly, in second heat exchanging unit 20, the plurality of heat transfer
plates 1 are stacked with the plurality of heat transfer plates 1 being disposed alternately
upside down, for example. Passage hole 12 of heat transfer plate 1a is provided to
overlap, in the first direction, passage hole 15 of heat transfer plate 1e and flow
port 21 of partition plate 2.
[0026] As shown in Fig. 3, heat transfer plates 1a, 1b, 1c, 1d are provided such that first
flow path 5 is represented by each of a portion between heat transfer plate 1a and
heat transfer plate 1b and a portion between heat transfer plate 1c and heat transfer
plate 1d and second flow path 6 is represented by a portion between heat transfer
plate 1b and heat transfer plate 1c. Heat transfer plates 1e, 1f, 1g, 1h are provided
such that third flow path 7 is represented by each of a portion between heat transfer
plate 1e and heat transfer plate If and a portion between heat transfer plate 1g and
heat transfer plate 1h and fourth flow path 8 is represented by each of a portion
between heat transfer plate If and heat transfer plate 1g and a portion between heat
transfer plate 1h and heat transfer plate 1i.
[0027] As shown in Fig. 3 and Fig. 6, one flow port 21 via which the first fluid flows is
provided at the outer peripheral portion of partition plate 2. As shown in Fig. 3,
Fig. 6, and Fig. 7, a portion of partition plate 2 overlapping with heat transfer
surface 17 of heat transfer plate 1 adjacent thereto in the first direction is provided
as a flat portion 24. Flow port 21 is provided to overlap with each passage hole 12
of heat transfer plates 1a, 1e adjacent to partition plate 2. First flow path 5 of
first heat exchanging unit 10 is connected to third flow path 7 of second heat exchanging
unit 20 via flow port 21.
[0028] In partition plate 2, flow port 21 is provided in the top surface of a protrusion
22 protruding in the thickness direction (the first direction) thereof relative to
flat portion 24. In partition plate 2, as with protrusion 22, a protrusion 23 protruding
in the above-described thickness direction is provided at a side of the outer peripheral
portion opposite to protrusion 22 in the above-described long side direction. Protrusion
23 is disposed at the upper side relative to protrusion 22. The top surface of protrusion
22 is in contact with a portion of heat transfer plate 1a adjacent thereto at the
front side in the first direction, the portion of heat transfer plate 1a being provided
with passage hole 12. The top surface of protrusion 23 is in contact with a portion
of heat transfer plate 1a adjacent thereto at the front side in the first direction,
the portion of heat transfer plate 1a being provided with passage hole 11.
[0029] As shown in Fig. 8, partition plate 2 is fixed to heat transfer plate 1a and heat
transfer plate 1e. Bottom portion 19 of heat transfer plate 1a is fixed, for example,
brazed to a surface of flat portion 24 of partition plate 2 at the front side. Top
portion 18 of heat transfer plate 1e is fixed, for example, brazed to a surface of
flat portion 24 of partition plate 2 at the back side. A space provided between top
portion 18 of heat transfer plate 1a and flat portion 24 of partition plate 2 is closed
and does not constitute first flow path 5 and second flow path 6. A space provided
between bottom portion 19 of heat transfer plate 1e and flat portion 24 of partition
plate 2 is closed and does not constitute third flow path 7 and fourth flow path 8.
[0030] As shown in Fig. 3 and Fig. 8, in first heat exchanging unit 10, the flow path provided
closest to partition plate 2 is provided between heat transfer plate 1a facing partition
plate 2 and heat transfer plate 1b adjacent to heat transfer plate 1a in the first
direction. A portion between heat transfer plate 1a and heat transfer plate 1b is
provided to serve as first portion 5A located closest to partition plate 2 in first
flow path 5. A portion between heat transfer plate 1b and heat transfer plate 1c is
provided to serve as second portion 6A located closest to partition plate 2 in second
flow path 6.
[0031] As shown in Fig. 3 and Fig. 8, the flow path provided closest to partition plate
2 in second heat exchanging unit 20 is provided between heat transfer plate 1e facing
partition plate 2 and heat transfer plate If adjacent to heat transfer plate 1e in
the first direction. A portion between heat transfer plate 1e and heat transfer plate
If is provided to serve as third portion 7A located closest to partition plate 2 in
third flow path 7. A portion between heat transfer plate If and heat transfer plate
1g is provided to serve as fourth portion 8A located closest to partition plate 2
in fourth flow path 8.
[0032] As shown in Fig. 3 and Fig. 9, a first flow inlet 31, a second flow inlet 32, and
a second flow outlet 33, via each of which the first fluid or the second fluid flows,
are provided in the outer peripheral portion of first entrance/exit plate 3. Each
of first flow inlet 31, second flow inlet 32, and second flow outlet 33 extends through
first entrance/exit plate 3 in the thickness direction (the first direction). First
flow inlet 31 and second flow outlet 33 are provided to face each other with a space
interposed therebetween in the short side direction of heat transfer plate 1. Further,
second flow inlet 32 and second flow outlet 33 are provided to face each other with
a space interposed therebetween in the long side direction of heat transfer plate
1. First flow inlet 31 and second flow outlet 33 are preferably disposed at the upper
side relative to second flow inlet 32. First flow inlet 31 is preferably provided
at the upper side relative to flow port 21 of partition plate 2. As shown in Fig.
9 and Fig. 10, when viewed in a side view, the outer peripheral portion provided with
first flow inlet 31, second flow inlet 32, and second flow outlet 33 and the central
portion located internal to first flow inlet 31, second flow inlet 32, and second
flow outlet 33 are provided to be flat in first entrance/exit plate 3. As shown in
Fig. 9 and Fig. 10, a portion of first entrance/exit plate 3 overlapping with heat
transfer surface 17 of heat transfer plate 1 adjacent thereto in the first direction
is provided as a flat portion 34.
[0033] As shown in Fig. 3 and Fig. 11, a first flow outlet 41, a third flow inlet 42, and
a third flow outlet 43, via each of which the first fluid or the third fluid flows,
are provided in the outer peripheral portion of second entrance/exit plate 4. Each
of first flow outlet 41, third flow inlet 42, and third flow outlet 43 extends through
second entrance/exit plate 4 in the thickness direction (the first direction). First
flow outlet 41 and third flow outlet 43 are provided to face each other with a space
interposed therebetween in the short side direction of heat transfer plate 1. Further,
third flow inlet 42 and third flow outlet 43 are provided to face each other with
a space interposed therebetween in the long side direction of heat transfer plate
1. First flow outlet 41 and third flow outlet 43 are preferably disposed at the upper
side relative to third flow inlet 42. First flow outlet 41 is preferably provided
at the upper side relative to flow port 21 of partition plate 2. As shown in Fig.
11 and Fig. 12, when viewed in a side view, the outer peripheral portion provided
with first flow outlet 41, third flow inlet 42, and third flow outlet 43 and the central
portion located internal to first flow outlet 41, third flow inlet 42, and third flow
outlet 43 are provided to be flat in second entrance/exit plate 4. As shown in Fig.
11 and Fig. 12, a portion of second entrance/exit plate 4 overlapping with heat transfer
surface 17 of heat transfer plate 1 adjacent thereto in the first direction is provided
as a flat portion 44.
[0034] In plate-type heat exchanger 100 described above, first entrance/exit plate 3 is
preferably provided with: first flow inlet 31 via which the first fluid flows into
first flow path 5; second flow inlet 32 via which the second fluid flows into second
flow path 6; and second flow outlet 33 via which the second fluid flows out of second
flow path 6. Second flow inlet 32 is preferably provided at the lower side relative
to second flow outlet 33. In other words, in plate-type heat exchanger 100, the second
direction is preferably a direction from the upper side toward the lower side, whereas
the third direction is preferably a direction from the lower side toward the upper
side.
[0035] In plate-type heat exchanger 100, the first fluid flowing in first flow path 5 exchanges
heat with the second fluid flowing in second flow path 6 and is accordingly condensed
(details will be described later). On this occasion, the first fluid having sufficiently
exchanged heat with the second fluid has a higher density than that of the first fluid
not having sufficiently exchanged heat with the second fluid yet. Hence, if the first
fluid flows from the lower side to the upper side in first flow path 5, a flow (downward
flow) of the first fluid having sufficiently exchanged heat with the second fluid
is generated against this flow of the first fluid in first flow path 5. As a result,
the flow of the first fluid in first flow path 5 is hindered by the downward flow,
with the result that heat exchanging efficiency of the plate-type heat exchanger is
decreased.
[0036] To address this, according to plate-type heat exchanger 100 described above, the
first fluid is condensed when flowing from the upper side to the lower side in first
flow path 5, whereby the flow of the first fluid in first flow path 5 is not hindered
by the downward flow. As a result, the heat exchanging efficiency of plate-type heat
exchanger 100 is suppressed from being decreased.
[0037] In plate-type heat exchanger 100 described above, second entrance/exit plate 4 is
provided with: first flow outlet 41 via which the first fluid flows out of third flow
path 7; third flow inlet 42 via which the third fluid flows into fourth flow path
8; and third flow outlet 43 via which the third fluid flows out of fourth flow path
8. Third flow inlet 42 is preferably provided at the lower side relative to third
flow outlet 43. In other words, in plate-type heat exchanger 100, the fifth direction
is preferably a direction from the lower side toward the upper side.
[0038] In plate-type heat exchanger 100, the third fluid flowing into each fourth flow path
8 is in a gas-liquid two-phase state (details will be described below). If the third
fluid flows from the upper side to the lower side in fourth flow path 8, the third
fluid is distributed, at the upper side relative to heat transfer surfaces 17 of heat
transfer plates 1, to the portions located between the plurality of heat transfer
surfaces 17 and constituting fourth flow paths 8. However, the refrigerant in the
liquid phase in the third fluid has a density higher than that of the refrigerant
in the gas phase and therefore is likely to flow to the lower side, with the result
that the third fluid is unlikely to be equally distributed to the portions located
between the plurality of heat transfer surfaces 17 and constituting fourth flow paths
8. In this case, in order to compensate heat transfer performance decreased because
the third fluid is unlikely to be equally distributed to the portions located between
the plurality of heat transfer surfaces 17, it may be considered to increase the number
of heat transfer plates 1 so as to increase a heat transfer area.
[0039] To address this, according to plate-type heat exchanger 100, the third fluid having
flowed into each fourth flow path 8 in the gas-liquid two-phase state flows from the
lower side to the upper side in fourth flow path 8, whereby the third fluid can be
equally distributed to the portions located between the plurality of heat transfer
surfaces 17. Hence, according to plate-type heat exchanger 100, high heat transfer
performance can be realized without increasing the number of heat transfer plates
1.
<Exemplary Configuration of Refrigeration Cycle Apparatus>
[0040] Plate-type heat exchanger 100 may be applied to a refrigeration cycle apparatus 200
shown in Fig. 13. Refrigeration cycle apparatus 200 includes: plate-type heat exchanger
100 configured as a condenser; a compressor 51; an expansion valve 52; an evaporator
53; an injection expansion valve 54; a pump 55; and a fan 56. Refrigeration cycle
apparatus 200 includes a refrigerant circuit in which compressor 51, first flow path
5, third flow path 7, and fourth flow path 8 of plate-type heat exchanger 100, expansion
valve 52, and evaporator 53 are connected in this order. Further, refrigeration cycle
apparatus 200 includes an injection circuit, which is branched from the refrigerant
circuit at a downstream relative to third flow path 7 and in which injection expansion
valve 54, fourth flow path 8, and an intermediate pressure portion of compressor 51
are connected in this order. Further, refrigeration cycle apparatus 200 includes a
heat medium circuit in which pump 55 and second flow path 6 are connected in this
order. That is, in refrigeration cycle apparatus 200, each of the first fluid and
the third fluid is refrigerant whereas the second fluid is a heat medium such as water
or brine. The first fluid is a high-pressure gas refrigerant, and the third fluid
is a low-pressure gas-liquid two-phase refrigerant.
[0041] As shown in Fig. 3, first flow inlet 31 of first entrance/exit plate 3 is provided
as a flow inlet for the first fluid. Second flow inlet 32 of first entrance/exit plate
3 is provided as a flow inlet for the second fluid. Second flow outlet 33 of first
entrance/exit plate 3 is provided as a flow outlet for the second fluid. First flow
outlet 41 of second entrance/exit plate 4 is provided as a flow outlet for the first
fluid. Third flow inlet 42 of second entrance/exit plate 4 is provided as a flow inlet
for the third fluid. Third flow outlet 43 of second entrance/exit plate 4 is provided
as a flow outlet for the third fluid.
[0042] The first fluid flows from first flow inlet 31 of first entrance/exit plate 3 into
first heat exchanging unit 10, and flows from the upper side to the lower side between
heat transfer plates 1a, 1b and between heat transfer plates 1c, 1d. The second fluid
flows from second flow inlet 32 of first entrance/exit plate 3 into first heat exchanging
unit 10, and flows from the lower side to the upper side between heat transfer plates
1b, 1c. Accordingly, in first heat exchanging unit 10, heat is exchanged between the
first fluid and the second fluid via heat transfer plates 1b, 1c. The second fluid
thus having exchanged heat with the first fluid flows out of first heat exchanging
unit 10 via second flow outlet 33 of first entrance/exit plate 3. The first fluid
having exchanged heat with the second fluid flows into second heat exchanging unit
20 via flow port 21 of partition plate 2.
[0043] The first fluid having flowed into second heat exchanging unit 20 flows from the
lower side to the upper side between heat transfer plates 1e, If and between heat
transfer plates 1g, 1h. The third fluid flows from third flow inlet 42 of second entrance/exit
plate 4 into second heat exchanging unit 20 and flows from the lower side to the upper
side between heat transfer plates 1f, 1g and between heat transfer plates 1h, 1i.
Accordingly, in second heat exchanging unit 20, heat is exchanged between the first
fluid and the third fluid via heat transfer plates 1f, 1g, 1g, 1i.
[0044] In such a refrigeration cycle apparatus 200, the refrigerant serving as the first
fluid discharged from compressor 51 flows in first flow path 5 in first heat exchanging
unit 10 of plate-type heat exchanger 100, whereby the refrigerant exchanges heat with
the heat medium serving as the second fluid flowing in second flow path 6 and is accordingly
condensed. The condensed refrigerant flows in third flow path 7 in second heat exchanging
unit 20, whereby the refrigerant exchanges heat with the refrigerant serving as the
third fluid flowing in fourth flow path 8 and is accordingly supercooled. Part of
the supercooled refrigerant is decompressed by expansion valve 52. The decompressed
refrigerant exchanges heat with gas supplied by fan 56 in evaporator 53 and is accordingly
evaporated. The evaporated refrigerant is suctioned by compressor 51.
[0045] Moreover, in refrigeration cycle apparatus 200, the remainder of the refrigerant
supercooled by flowing in third flow path 7, i.e., the other part of the refrigerant
than the foregoing part flows into the above-described injection circuit. The refrigerant
having flowed into the injection circuit is decompressed by injection expansion valve
54. The decompressed refrigerant flows in fourth flow path 8 in second heat exchanging
unit 20 and is heated due to heat exchange with the refrigerant flowing in third flow
path 7.
[0046] Since such a refrigeration cycle apparatus 200 includes the injection circuit, the
temperature of the refrigerant discharged from compressor 51 can be suppressed from
being increased. Moreover, refrigeration cycle apparatus 200 includes the refrigerant
circuit for the heat exchange between the first fluid and the second fluid and the
heat exchange between the first fluid and the third fluid; however, since the refrigerant
circuit is constructed using plate-type heat exchanger 100, refrigeration cycle apparatus
200 can be downsized as compared with a conventional refrigeration cycle apparatus
in which the refrigerant circuit is constituted of two heat exchangers. As a result,
refrigeration cycle apparatus 200 can be manufactured readily with a reduced cost
as compared with the conventional refrigeration cycle apparatus.
[0047] It should be noted that in plate-type heat exchanger 100 according to the first embodiment,
the thickness of partition plate 2 in the first direction may be thinner than the
thickness of heat transfer plate 1 in the first direction. Heat transfer plate 1 is
fed with a differential pressure between the first fluid flowing in first flow path
5 and the second fluid flowing in second flow path 6. On the other hand, partition
plate 2 is fed with a differential pressure between the first fluid flowing in first
flow path 5 and the first fluid flowing in third flow path 7. Accordingly, the differential
pressure applied to partition plate 2 is smaller than the differential pressure applied
to heat transfer plate 1. As a result, even when the thickness of partition plate
2 in the first direction is thinner than the thickness of heat transfer plate 1 in
the first direction, partition plate 2 can be suppressed from being broken, whereby
plate-type heat exchanger 100 can have high reliability.
[0048] Moreover, in plate-type heat exchanger 100, when first heat exchanging unit 10 has
only heat transfer plates 1a, 1b, 1c, first flow path 5 is formed only between heat
transfer plates 1a, 1b. In this case, the whole of first flow path 5 is located at
a location close to partition plate 2 relative to second flow path 6 formed between
heat transfer plates 1b, 1c.
Second Embodiment.
[0049] Next, with reference to Fig. 14 to Fig. 16, a plate-type heat exchanger 101 according
to a second embodiment will be described. Although plate-type heat exchanger 101 according
to the second embodiment basically includes the same configuration as that of plate-type
heat exchanger 100 according to the first embodiment, at least a portion of second
flow path 6 is located at a location close to first entrance/exit plate 3 relative
to first flow path 5 and at least a portion of fourth flow path 8 is located at a
location close to second entrance/exit plate 4 relative to third flow path 7. In other
words, second flow path 6 has a sixth portion 6B located close to first entrance/exit
plate 3 relative to a fifth portion 5B of first flow path 5 located closest to first
entrance/exit plate 3. Fourth flow path 8 has an eighth portion 8B located close to
second entrance/exit plate 4 relative to a seventh portion 7B of third flow path 7
located closest to second entrance/exit plate 4.
[0050] As shown in Fig. 14 and Fig. 15, first entrance/exit plate 3 is fixed to a heat transfer
plate 1j. Top portion 18 of heat transfer plate 1j is fixed, for example, brazed to
a surface of flat portion 34 of first entrance/exit plate 3 at the back side. A space
provided between flat portion 34 of first entrance/exit plate 3 and bottom portion
19 of heat transfer plate 1j is closed and does not constitute first flow path 5 and
second flow path 6.
[0051] As shown in Fig. 14 and Fig. 16, second entrance/exit plate 4 is fixed to a heat
transfer plate 1i. Bottom portion 19 of heat transfer plate 1i is fixed, for example,
brazed to a surface of flat portion 44 of second entrance/exit plate 4 at the front
side. A space provided between flat portion 44 of second entrance/exit plate 4 and
top portion 18 of heat transfer plate 1i is closed and does not constitute third flow
path 7 and fourth flow path 8.
[0052] As shown in Fig. 14 and Fig. 15, in first heat exchanging unit 10, the flow path
provided closest to first entrance/exit plate 3 is provided between heat transfer
plate 1j and heat transfer plate 1d. A portion between heat transfer plate 1j and
heat transfer plate 1d is provided to serve as sixth portion 6B of second flow path
6 located closest to first entrance/exit plate 3. A portion between heat transfer
plate 1d and heat transfer plate 1c is provided to serve as fifth portion 5B of first
flow path 5 located closest to first entrance/exit plate 3.
[0053] As shown in Fig. 14 and Fig. 15, in second heat exchanging unit 20, the flow path
provided closest to second entrance/exit plate 4 is provided between heat transfer
plate 1h and heat transfer plate 1i. A portion between heat transfer plate 1h and
heat transfer plate 1i is provided to serve as eighth portion 8B of fourth flow path
8 located closest to second entrance/exit plate 4. A portion between heat transfer
plate 1g and heat transfer plate 1h is provided to serve as seventh portion 7B of
third flow path 7 located closest to second entrance/exit plate 4.
[0054] Since plate-type heat exchanger 101 thus configured according to the second embodiment
includes basically the same configuration as that of plate-type heat exchanger 100
according to the first embodiment, plate-type heat exchanger 101 can exhibit the same
effect as that of plate-type heat exchanger 100.
[0055] Further, plate-type heat exchanger 101 further includes: first entrance/exit plate
3 disposed to sandwich first heat exchanging unit 10 between first entrance/exit plate
3 and partition plate 2 in the first direction; and second entrance/exit plate 4 disposed
to sandwich second heat exchanging unit 20 between second entrance/exit plate 4 and
partition plate 2 in the first direction. Second flow path 6 has a sixth portion 6B
located close to first entrance/exit plate 3 relative to a fifth portion 5B of first
flow path 5 located closest to first entrance/exit plate 3. Fourth flow path 8 has
an eighth portion 8B located close to second entrance/exit plate 4 relative to a seventh
portion 7B of third flow path 7 located closest to second entrance/exit plate 4.
[0056] Therefore, first entrance/exit plate 3 of plate-type heat exchanger 101 is fed with
a differential pressure between the pressure of the second fluid flowing in second
flow path 6 and the pressure (for example, atmospheric pressure) of surrounding gas
outside plate-type heat exchanger 101. When plate-type heat exchanger 101 is included
in refrigeration cycle apparatus 200 shown in Fig. 13, the pressure of the second
fluid flowing in second flow path 6 is lower than the pressure of the first fluid
flowing in first flow path 5. Hence, according to plate-type heat exchanger 101, the
differential pressure applied to first entrance/exit plate 3 can be reduced as compared
with a case where first entrance/exit plate 3 is fed with the differential pressure
between the pressure of the first fluid flowing in first flow path 5 and the pressure
(for example, atmospheric pressure) of the surrounding gas outside plate-type heat
exchanger 101. As a result, since a risk of first entrance/exit plate 3 being damaged
is reduced in plate-type heat exchanger 101, plate-type heat exchanger 101 has high
reliability.
[0057] Moreover, second entrance/exit plate 4 of plate-type heat exchanger 101 is fed with
a differential pressure between the pressure of the third fluid flowing in fourth
flow path 8 and the pressure (for example, atmospheric pressure) of the surrounding
gas outside plate-type heat exchanger 101. When plate-type heat exchanger 101 is included
in refrigeration cycle apparatus 200 shown in Fig. 13, the pressure of the third fluid
flowing in fourth flow path 8 is lower than the pressure of the first fluid flowing
in third flow path 7. Hence, according to plate-type heat exchanger 101, the differential
pressure applied to second entrance/exit plate 4 can be reduced as compared with a
case where second entrance/exit plate 4 is fed with the differential pressure between
the pressure of the first fluid flowing in third flow path 7 and the pressure (for
example, atmospheric pressure) of the surrounding gas outside plate-type heat exchanger
101. As a result, since a risk of second entrance/exit plate 4 being damaged is reduced
in plate-type heat exchanger 101, plate-type heat exchanger 101 has high reliability.
[0058] From a different viewpoint, it can be said that plate-type heat exchanger 101 is
provided to minimize a total of the differential pressure applied to partition plate
2, the differential pressure applied to first entrance/exit plate 3, and the differential
pressure applied to second entrance/exit plate 4. As described above, in plate-type
heat exchanger 101, the differential pressure applied to partition plate 2 is a differential
pressure between the first fluid and the first fluid, which is smaller than the differential
pressure between the first fluid and the second fluid, the differential pressure between
the first fluid and the third fluid, and the differential pressure between the second
fluid and the third fluid. Moreover, in plate-type heat exchanger 101, the differential
pressure applied to first entrance/exit plate 3 is a differential pressure between
the second fluid and the surrounding gas outside plate-type heat exchanger 101, which
is smaller than the differential pressure between the first fluid and the surrounding
gas outside plate-type heat exchanger 101. Moreover, in plate-type heat exchanger
101, the differential pressure applied to second entrance/exit plate 4 is a differential
pressure between the third fluid and the surrounding gas outside plate-type heat exchanger
101, which is smaller than the differential pressure between the first fluid and the
surrounding gas outside plate-type heat exchanger 101. Hence, according to plate-type
heat exchanger 101, since partition plate 2, first entrance/exit plate 3, and second
entrance/exit plate 4 are suppressed from being broken as described above, plate-type
heat exchanger 101 has sufficiently high reliability.
Third Embodiment.
[0059] Next, with reference to Fig. 17 to Fig. 20, a plate-type heat exchanger according
to a third embodiment will be described. The plate-type heat exchanger according to
the third embodiment includes basically the same configuration as that of plate-type
heat exchanger 100 according to the first embodiment, but is specified to be different
therefrom in that the thickness of at least one of partition plate 2, first entrance/exit
plate 3, and second entrance/exit plate 4 is thicker than that of heat transfer plate
1 in the first direction. For example, the thickness of each of partition plate 2,
first entrance/exit plate 3, and second entrance/exit plate 4 is thicker than that
of heat transfer plate 1 in the first direction.
[0060] Here, it is assumed that the thickness of heat transfer plate 1 represents a thickness
T1 (see Fig. 18) of heat transfer surface 17 of heat transfer plate 1. It should be
noted that heat transfer plate 1 is formed by, for example, performing press-forming
to a plate-like member and the thickness of heat transfer surface 17 is equal to the
thickness of each of protrusions 14, 16. Similarly, it is assumed that the thickness
of partition plate 2 represents a thickness T2 (see Fig. 17) of flat portion 24 of
partition plate 2. It should be noted that partition plate 2 is formed by, for example,
performing press-forming to a plate-like member and the thickness of flat portion
24 is equal to the thickness of each of protrusions 22, 23. It is assumed that the
thickness of first entrance/exit plate 3 represents a thickness T3 (see Fig. 19) of
flat portion 34 of first entrance/exit plate 3. It is assumed that the thickness of
second entrance/exit plate 4 represents a thickness T4 (see Fig. 20) of flat portion
44 of second entrance/exit plate 4. It should be noted that each of first entrance/exit
plate 3 and second entrance/exit plate 4 is formed by, for example, performing press-forming
to a plate-like member. Thickness T1 of heat transfer plate 1 is provided so as not
to hinder the heat exchange between the first fluid and the second fluid and so as
to endure the differential pressure between the first fluid and the second fluid.
[0061] As shown in Fig. 17 and Fig. 18, thickness T2 of partition plate 2 in the first direction
is thicker than thickness T1 of heat transfer plate 1 in the first direction. In this
way, partition plate 2 has a sufficiently high strength for the differential pressure,
which may be applied to partition plate 2, between the pressure of the first fluid
flowing in first flow path 5 and the pressure of the first fluid flowing in third
flow path 7. Hence, since partition plate 2 is suppressed from being broken in the
plate-type heat exchanger according to the third embodiment, the plate-type heat exchanger
has high reliability.
[0062] As shown in Fig. 19 to Fig. 21, thickness T3 of first entrance/exit plate 3 in the
first direction and thickness T4 of second entrance/exit plate 4 in the first direction
are thicker than thickness T1 of heat transfer plate 1 in the first direction. In
this way, first entrance/exit plate 3 has a sufficiently high strength for the differential
pressure that may be applied to first entrance/exit plate 3, i.e., the differential
pressure between the first fluid flowing in first flow path 5 and the surrounding
gas outside the plate-type heat exchanger or the differential pressure between the
second fluid flowing in second flow path 6 and the surrounding gas outside the plate-type
heat exchanger. Second entrance/exit plate 4 has a sufficiently high strength for
the differential pressure that may be applied to second entrance/exit plate 4, i.e.,
the differential pressure between the first fluid flowing in third flow path 7 and
the surrounding gas outside the plate-type heat exchanger or the differential pressure
between the third fluid flowing in fourth flow path 8 and the surrounding gas outside
the plate-type heat exchanger. Hence, since first entrance/exit plate 3 and second
entrance/exit plate 4 are suppressed from being broken in the plate-type heat exchanger
according to the third embodiment, the plate-type heat exchanger has high reliability.
[0063] As shown in Fig. 17, partition plate 2 may be constituted of one member. Alternatively,
as shown in Fig. 21, partition plate 2 may be constituted of a plurality of members.
Partition plate 2 may be formed by adhering a first member 25 to a second member 26.
A material of second member 26 has a higher strength than a material of heat transfer
plate 1, for example. For example, the material of heat transfer plate 1 is stainless
steel, copper (Cu), aluminum (Al) or the like, whereas the material of second member
26 is titanium (Ti) or an alloy such as stainless steel or duralumin, for example.
Thickness T2 of partition plate 2 in the first direction corresponds to a total of
thickness T5 of first member 25 in the first direction and thickness T6 of second
member 26 in the first direction. Thickness T6 of second member 26 in the first direction
may be thinner than thickness T1 of heat transfer plate 1.
[0064] Also in this way, partition plate 2 has a sufficiently high strength for the differential
pressure, which may be applied to partition plate 2, between the pressure of the first
fluid flowing in first flow path 5 and the pressure of the first fluid flowing in
third flow path 7.
[0065] As shown in Fig. 19 and Fig. 20, each of first entrance/exit plate 3 and second entrance/exit
plate 4 may be constituted of one member. Alternatively, as shown in Fig. 22 and Fig.
23, each of first entrance/exit plate 3 and second entrance/exit plate 4 may be constituted
of a plurality of members. First entrance/exit plate 3 may be formed by adhering a
third member 35 to a fourth member 36. Second entrance/exit plate 4 may be formed
by adhering a fifth member 45 to a sixth member 46. The material of each of fourth
member 36 and sixth member 46 has a higher strength than the material of heat transfer
plate 1, for example. The material of heat transfer plate 1 may be any material having
high thermal conductivity, such as stainless steel, copper (Cu), or aluminum (Al).
On the other hand, the material of each of fourth member 36 and sixth member 46 is,
for example, titanium (Ti) or an alloy such as stainless steel or duralumin. Thickness
T3 of first entrance/exit plate 3 in the first direction corresponds to a total of
thickness T7 of third member 35 in the first direction and thickness T8 of fourth
member 36 in the first direction. Thickness T4 of second entrance/exit plate 4 in
the first direction corresponds to a total of thickness T9 of fifth member 45 in the
first direction and thickness T10 of sixth member 46 in the first direction. Respective
thicknesses T8, T10 of fourth member 36 and sixth member 46 in the first direction
may be thinner than thickness T1 of heat transfer plate 1.
[0066] Also in this way, first entrance/exit plate 3 has a sufficient high strength for
the differential pressure that may be applied to first entrance/exit plate 3. Second
entrance/exit plate 4 has a sufficiently high strength for the differential pressure
that may be applied to second entrance/exit plate 4.
[0067] It should be noted that in the plate-type heat exchanger according to the third embodiment,
the thickness of one of partition plate 2, first entrance/exit plate 3 and second
entrance/exit plate 4 may be thicker than that of heat transfer plate 1 in the first
direction. In the plate-type heat exchanger thus configured, since the plate having
a thicker thickness than that of heat transfer plate 1 in the first direction is suppressed
from being broken, the plate-type heat exchanger has high reliability.
Fourth Embodiment.
[0068] Next, a plate-type heat exchanger according to a fourth embodiment will be described.
The plate-type heat exchanger according to the fourth embodiment includes basically
the same configuration as that of plate-type heat exchanger 100 according to the first
embodiment, but is specified to be different therefrom in that at least one of partition
plate 2, first entrance/exit plate 3, and second entrance/exit plate 4 contains a
material having a higher strength than that of the material of heat transfer plate
1. For example, each of partition plate 2, first entrance/exit plate 3, and second
entrance/exit plate 4 contains a material having a higher strength than that of the
material of heat transfer plate 1.
[0069] The material of heat transfer plate 1 may be any material having high thermal conductivity,
such as stainless steel, copper (Cu), or aluminum (Al). The material of partition
plate 2 may be any material having a higher strength than that of the material of
heat transfer plate 1, such as titanium (Ti) or an alloy such as stainless steel or
duralumin, for example. The material of each of first entrance/exit plate 3 and second
entrance/exit plate 4 may be any material having a higher strength than that of the
material of heat transfer plate 1, such as titanium (Ti) or an alloy such as stainless
steel or duralumin, for example.
[0070] In this way, partition plate 2 has a sufficiently high strength for the differential
pressure, which may be applied to partition plate 2, between the pressure of the first
fluid flowing in first flow path 5 and the pressure of the first fluid flowing in
third flow path 7. First entrance/exit plate 3 has a sufficiently high strength for
the differential pressure that may be applied to first entrance/exit plate 3. Second
entrance/exit plate 4 has a sufficiently high strength for the differential pressure
that may be applied to second entrance/exit plate 4. Accordingly, in the plate-type
heat exchanger according to the fourth embodiment, since partition plate 2, first
entrance/exit plate 3, and second entrance/exit plate 4 are suppressed from being
broken, the plate-type heat exchanger has high reliability.
[0071] It should be noted that in the above-described embodiment, heat transfer plate 1a
and heat transfer plate 1e are fixed to partition plate 2; however, the configuration
is not limited to this. Partition plate 2 may be provided such that partition plate
2 and heat transfer plate 1 adjacent thereto in the first direction form the flow
path for the first fluid. From a different viewpoint, it can be said that the partition
plate according to the present embodiment may be configured as a complex body in which
a plate having a configuration similar to that of the heat transfer plate and a flat
plate are joined.
[0072] The embodiments disclosed herein are illustrative and non-restrictive in any respect.
The scope of the present invention is defined by the terms of the claims, rather than
the embodiments described above, and is intended to include any modifications within
the scope and meaning equivalent to the terms of the claims.
INDUSTRIAL APPLICABILITY
[0073] The present invention is applied particularly advantageously to a plate-type heat
exchanger in which heat exchange can be performed among three fluids.
REFERENCE SIGNS LIST
[0074] 1, 1a, 1b, 1c, 1d, 1e, If, 1g, 1h, 1i, 1j: heat transfer plate; 2: partition plate;
3: first entrance/exit plate; 4: second entrance/exit plate; 5: first flow path; 6:
second flow path; 7: third flow path; 8: fourth flow path; 10: first heat exchanging
unit; 17: heat transfer surface; 18: top portion; 19: bottom portion; 20: second heat
exchanging unit; 21: flow port; 24, 34, 44: flat portion; 25: first member; 26: second
member; 31: first flow inlet; 32: second flow inlet; 33: second flow outlet; 35: third
member; 36: fourth member; 41: first flow outlet; 42: third flow inlet; 43: third
flow outlet; 45: fifth member; 46: sixth member; 51: compressor; 52: expansion valve;
53: evaporator; 54: injection expansion valve; 55: pump; 56: fan; 100, 101: plate-type
heat exchanger; 200: refrigeration cycle apparatus.