Technical Field
[0001] The present invention relates to laminated headers, heat exchangers, and air-conditioning
apparatuses.
Background Art
[0002] A header in the related art includes, for example, a plate-like body including a
distribution passage configured to distribute and deliver refrigerant inflowing from
an inlet passage to a plurality of outlet passages. In such a header, the distribution
passage includes a plurality of branching passages, each having a branching portion,
an inflow passage communicating with the branching portion, and two outflow passages
communicating with the branching portion. In the distribution passage, the refrigerant
is repeatedly branched off into two paths a plurality of times in the branching passages,
subsequently flows into a plurality of distribution chambers, and is distributed to
the plurality of outlet passages from the distribution chambers (e.g., see Patent
Literature 1).
[0003] US6892805B1 discloses a laminated header having branching passages.
[0004] JPH0611291A, on which the preamble of claim 1 is based, provides an improved header, together
with a method for manufacturing it, for a refrigerant system evaporator where a refrigerant
is evenly distributed to the evaporator from a header inlet for improved efficiency.
[0005] JPH09189463A provides a header chamber which delays the flow of a heat exchanger fluid and a heat
transfer tube mounting area which distributes the exchanger fluid to the header chamber,
a groove area which is connected to this header chamber and each groove hole of the
groove area to improve the distribution function of a heat exchanger fluid.
[0006] JP2004003810A provides a heat exchanger suppressing the increase in a pressure loss in a relatively
simple constitution and positively adjusting the temperature distribution of external
fluid whose heat is exchanged by internal fluid.
[0007] US6892805B1 discloses a fluid flow distribution device is provided for use in a heat exchanger
having multiple heat exchange units that receive a fluid flow from an fluid inlet.
The device includes a plurality of tortuous flow paths to direct distributed portions
of the fluid flow from the inlet to the heat exchange units. Each tortuous flow path
is defined by a pair of flow chamber plates, and an orifice plate sandwiched between
the flow chamber plates. Each tortuous flow path includes a series of orifices extending
through the orifice plate, a first pattern of first flow chambers formed in one of
the flow chamber plates and aligned with sequential pairs of the orifices, and a second
pattern of second flow chambers formed in the other of the flow chamber plates and
offset with respect to the first pattern and the pairs of orifices.
Citation List
Patent Literature
[0008] Patent Literature 1: Japanese Unexamined Patent Application Publication No.
10-267468 (paragraphs [0033] to [0037], Fig. 6)
Summary of Invention
Technical Problem
[0009] In such a header, the number of branching passages through which the refrigerant
passes before flowing into each distribution chamber and the number of branch paths
in each branching passage are the same so that evenness in the refrigerant to be distributed
to the outlet passages is achieved. Thus, the number of outlet passages is limited
to multiples of powers of 2. In other words, in a case where such a header is used
in a device, such as a heat exchanger, there is a problem in that the number of outlet
passages cannot be changed freely in accordance with the number of passages formed
in the device.
[0010] The present invention has been made in view of the problem mentioned above, and an
object thereof is to obtain a laminated header in which the degree of freedom in the
number of outlet passages is increased. Another object of the present invention is
to obtain a heat exchanger equipped with such a laminated header. Another object of
the present invention is to obtain an air-conditioning apparatus equipped with such
a heat exchanger.
Solution to Problem
[0011] A laminated header according an embodiment of the present invention includes a first
plate-like body including a plurality of outlet passages, and also includes a second
plate-like body attached to the first plate-like body and including at least part
of a distribution passage configured to distribute and deliver refrigerant inflowing
from an inlet passage to the plurality of outlet passages. The distribution passage
includes a branching passage having a branching portion, an inflow passage communicating
with the branching portion, and a plurality of outflow passages communicating with
the branching portion. The plurality of outflow passages include a first outflow passage
and a second outflow passage. The number of curves, at which flow separation of the
refrigerant is to occur, in a flow path through which the refrigerant inflowing from
the inflow passage passes via the first outflow passage before reaching the outlet
passages is smaller than the number of curves, at which flow separation of the refrigerant
is to occur, in a flow path through which the refrigerant inflowing from the inflow
passage passes via the second outflow passage before reaching the outlet passages.
The equivalent diameter of at least part of the first outflow passage is smaller than
the equivalent diameter of at least part of the second outflow passage.
Advantageous Effects of Invention
[0012] In the laminated header according to the embodiment of the present invention, the
plurality of outflow passages include the first outflow passage and the second outflow
passage. The number of curves, at which flow separation of the refrigerant is to occur,
in the flow path through which the refrigerant inflowing from the inflow passage passes
via the first outflow passage before reaching the outlet passages is smaller than
the number of curves, at which flow separation of the refrigerant is to occur, in
the flow path through which the refrigerant inflowing from the inflow passage passes
via the second outflow passage before reaching the outlet passages. Moreover, the
equivalent diameter of at least part of the first outflow passage is smaller than
the equivalent diameter of at least part of the second outflow passage. Accordingly,
reduction in the evenness of the distribution of the refrigerant is suppressed, while
the number of outlet passages can be changed to a number other than multiples of powers
of 2, thereby allowing for an increased degree of freedom in the number of outlet
passages in the laminated header.
Brief Description of Drawings
[0013]
[Fig. 1] Fig. 1 illustrates the configuration of a heat exchanger according to Embodiment
1.
[Fig. 2] Fig. 2 is a perspective view illustrating a state where a laminated header
of the heat exchanger according to Embodiment 1 is disassembled.
[Fig. 3] Fig. 3 is a perspective view of a relevant part of a distribution passage,
illustrating a state where the laminated header of the heat exchanger according to
Embodiment 1 is disassembled.
[Fig. 4] Fig. 4 is a diagram illustrating an overlapped state of passages of a branching
passage in the heat exchanger according to Embodiment 1.
[Fig. 5] Fig. 5 is a Baker diagram illustrating the relationship between a flow state
and a flow pattern of refrigerant.
[Fig. 6] Fig. 6 illustrates the configuration of an air-conditioning apparatus to
which the heat exchanger according to Embodiment 1 is applied.
[Fig. 7] Fig. 7 is a perspective view illustrating a state where a laminated header
of a heat exchanger according to Embodiment 2 is disassembled.
[Fig. 8] Fig. 8 is a perspective view of a relevant part of a distribution passage,
illustrating a state where the laminated header of the heat exchanger according to
Embodiment 2 is disassembled.
[Fig. 9] Fig. 9 is a diagram illustrating an overlapped state of passages of a branching
passage in the heat exchanger according to Embodiment 2.
[Fig. 10] Fig. 10 is a perspective view illustrating a state where the laminated header
in a modification of the heat exchanger according to Embodiment 2 is disassembled.
[Fig. 11] Fig. 11 is a perspective view illustrating a state where the laminated header
in a modification of the heat exchanger according to Embodiment 2 is disassembled.
Description of Embodiments
[0014] A laminated header according to the present invention will be described below with
reference to the drawings.
[0015] Although the laminated header according to the present invention is described below
as being configured to distribute refrigerant flowing into a heat exchanger, the laminated
header according to the present invention may alternatively be configured to distribute
refrigerant flowing into another device. Furthermore, for example, the configuration
and the operation to be described below are merely examples, and the laminated header
according to the present invention is not limited to the case of such a configuration
or operation. Moreover, identical reference signs are given to identical or similar
components among the drawings or such reference signs are omitted therefrom. Furthermore,
the illustrations of detailed structures are simplified or omitted, where appropriate.
Moreover, redundant or similar descriptions are simplified or omitted, where appropriate.
Embodiment 1
[0016] A heat exchanger according to Embodiment 1 will be described.
<Configuration of Heat Exchanger>
[0017] The configuration of the heat exchanger according to Embodiment 1 will be described
below.
[0018] Fig. 1 illustrates the configuration of the heat exchanger according to Embodiment
1.
[0019] As shown in Fig. 1, a heat exchanger 1 has a laminated header 2, a header 3, a plurality
of heat-transfer tubes 4, a support member 5, and a plurality of fins 6.
[0020] The laminated header 2 has a refrigerant inflow section 2A and a plurality of refrigerant
outflow sections 2B. The header 3 has a plurality of refrigerant inflow sections 3A
and a refrigerant outflow section 3B. The refrigerant inflow section 2A of the laminated
header 2 and the refrigerant outflow section 3B of the header 3 are connected to a
refrigerant pipe. The heat-transfer tubes 4 are connected between the refrigerant
outflow sections 2B of the laminated header 2 and the refrigerant inflow sections
3A of the header 3.
[0021] A plurality of heat-transfer tubes 4 are flat tubes each having a passages. The heat-transfer
tubes 4 are composed of, for example, aluminum. The laminated-header-2-side ends of
the heat-transfer tubes 4 are connected to the refrigerant outflow sections 2B of
the laminated header 2 in a state where the ends are supported by the support member
5, which is plate-like. The support member 5 is composed of, for example, aluminum.
The heat-transfer tubes 4 are joined to the plurality of fins 6. The fins 6 are composed
of, for example, aluminum. Although Fig. 1 illustrates a case where there are six
heat-transfer tubes 4, the number thereof is not limited to such a case. For example,
the number may be two. Furthermore, the heat-transfer tubes 4 do not have to be flat
tubes.
<Flow of Refrigerant in Heat Exchanger>
[0022] The flow of the refrigerant in the heat exchanger according to Embodiment 1 will
be described below.
[0023] The refrigerant flowing through the refrigerant pipe is distributed by flowing into
the laminated header 2 via the refrigerant inflow section 2A, and outflows to the
plurality of heat-transfer tubes 4 via the corresponding plurality of refrigerant
outflow sections 2B. In the plurality of heat-transfer tubes 4, the refrigerant exchanges
heat with, for example, air supplied from a fan. The refrigerant flowing through the
plurality of heat-transfer tubes 4 merges together by flowing into the header 3 via
the plurality of refrigerant inflow sections 3A, and outflows to the refrigerant pipe
via the refrigerant outflow section 3B. The refrigerant can be flowed backward.
<Configuration of Laminated Header>
[0024] The configuration of the laminated header of the heat exchanger according to Embodiment
1 will be described below.
[0025] Fig. 2 is a perspective view illustrating a state where the laminated header of the
heat exchanger according to Embodiment 1 is disassembled.
[0026] As shown in Fig. 2, the laminated header 2 includes a first plate-like body 11 and
a second plate-like body 12. The first plate-like body 11 is laminated at the outflow
side of the refrigerant. The second plate-like body 12 is laminated at the inflow
side of the refrigerant.
[0027] The first plate-like body 11 has a first plate-like member 21 and a cladding member
24_5. The second plate-like body 12 has a second plate-like member 22, a plurality
of third plate-like members 23_1 to 23_3, and a plurality of cladding members 24_1
to 24_4. A brazing material is applied to both surfaces or one surface of each of
the cladding members 24_1 to 24_5. The first plate-like member 21 is laminated on
the support member 5 with the cladding member 24_5 interposed therebetween. The plurality
of third plate-like members 23_1 to 23_3 respectively intervened by the cladding members
24_2 to 24_4 are laminated on the first plate-like member 21. The second plate-like
member 22 is laminated on the third plate-like member 23_1 with the cladding member
24_1 interposed therebetween. For example, the first plate-like member 21, the second
plate-like member 22, and the third plate-like members 23_1 to 23_3 each have a thickness
of 1 mm to 10 mm and are composed of aluminum.
[0028] In the following description, the support member 5, the first plate-like member 21,
the second plate-like member 22, the third plate-like members 23_1 to 23_3, and the
cladding members 24_1 to 24_5 are sometimes collectively referred to as plate-like
members. Furthermore, the third plate-like members 23_1 to 23_3 are sometimes collectively
referred to as third plate-like members 23. Moreover, the cladding members 24_1 to
24_5 are sometimes collectively referred to as cladding members 24.
[0029] By joining the first plate-like member 21 to the cladding member 24_5, passages 21A
formed in the first plate-like member 21 and passages 24_5A formed in the cladding
member 24_5 communicate with each other, whereby a plurality of outlet passages 11A
are formed. The passages 21A and the passages 24_5A are through-holes whose inner
peripheral surfaces conform in shape to the outer peripheral surfaces of the heat-transfer
tubes 4. The ends of the heat-transfer tubes 4 are supported by being joined to the
support member 5 by brazing. When the first plate-like body 11 and the support member
5 are joined to each other, the ends of the heat-transfer tubes 4 and the outlet passages
11A are connected to each other. Alternatively, the outlet passages 11A and the heat-transfer
tubes 4 may be directly joined to each other without providing the support member
5. In that case, for example, the component cost is reduced. The plurality of outlet
passages 11A correspond to the plurality of refrigerant outflow sections 2B in Fig.
1.
[0030] By joining the second plate-like member 22, the third plate-like members 23_1 to
23_3, and the cladding members 24_1 to 24_4, a passage 22A formed in the second plate-like
member 22, passages 23_1 A to 23_3A, 23_2B, and 23_3B formed in the third plate-like
members 23_1 to 23_3, and passages 24_1 A to 24_4A and 24_2B to 24_4B formed in the
cladding members 24_1 to 24_4 communicate with one another, whereby a distribution
passage 12A is formed.
[0031] The distribution passage 12A has an inlet passage 12a, branching passages 12b_11
to 12b_14, and a through-passage 12c. The number and the order of the branching passages
12b_11 to 12b_14 and the through-passage 12c are changed, where appropriate, in accordance
with, for example, the number of heat-transfer tubes 4. In the following description,
the branching passages 12b_11 to 12b_14 are sometimes collectively referred to as
branching passages 12b.
[0032] By joining the second plate-like member 22 to the cladding member 24_1, the passage
22A formed in the second plate-like member 22 and the passage 24_1 A formed in the
cladding member 24_1 communicate with each other, whereby the inlet passage 12a is
formed. The passage 22A and the passage 24_1 A are circular through-holes. The inlet
passage 12a is connected to the refrigerant pipe. The inlet passage 12a corresponds
to the refrigerant inflow section 2A in Fig. 1.
[0033] By joining the third plate-like member 23_1 to the cladding members 24_1 and 24_2,
the passage 24_1 A formed in the cladding member 24_1, the passage 23_1 A formed in
the third plate-like member 23_1, and the one passage 24_2A and the one passage 24_2B
formed in the cladding member 24_2 communicate with one another, whereby the branching
passage 12b_11 is formed. The passage 23_1A is a linear through-groove. The passages
24_2A and 24_2B are circular through-holes.
[0034] By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3,
the passage 24_2A formed in the cladding member 24_2, the passage 23_2A formed in
the third plate-like member 23_2, and the two passages 24_3A formed in the cladding
member 24_3 communicate with one another, whereby the branching passage 12b_12 is
formed. The passage 23_2A is a linear through-groove. The passages 24_3A are circular
through-holes.
[0035] By joining the third plate-like member 23_3 to the cladding members 24_3 and 24_4,
the passages 24_3A formed in the cladding member 24_3, the passages 23_3A formed in
the third plate-like member 23_3, and the two pairs of passages 24_4A formed in the
cladding member 24_4 communicate with one another, whereby the branching passages
12b_13 are formed. The passages 23_3A are linear through-grooves. The passages 24_4A
are circular through-holes.
[0036] By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3,
the passage 24_2B formed in the cladding member 24_2, the passage 23_2B formed in
the third plate-like member 23_2, and the one passage 24_3B formed in the cladding
member 24_3 communicate with one another, whereby the through-passage 12c is formed.
The passage 23_2B and the passage 24_3B are circular through-holes.
[0037] By joining the third plate-like member 23_3 to the cladding members 24_3 and 24_4,
the passage 24_3B formed in the cladding member 24_3, the passage 23_3B formed in
the third plate-like member 23_3, and the two passages 24_4B formed in the cladding
member 24_4 communicate with one another, whereby the branching passage 12b_14 is
formed. The passage 23_3B is a linear through-groove. The passages 24_4B are circular
through-holes.
[0038] Parts located between ends of the passages 23_1 A to 23_3A and 23_3B being linear
through-grooves formed in the third plate-like members 23 and the passages 24_1A to
24_3A and 24_3B being circular through-holes formed in the cladding members 24 laminated
on the refrigerant inflow surfaces of the third plate-like members 23 are formed at
positions facing each other. Therefore, the passages 23_1 A to 23_3A and 23_3B being
linear through-grooves formed in the third plate-like members 23 are blocked, except
for the parts between the ends, by the cladding members 24 laminated on the refrigerant
inflow surfaces of the third plate-like members 23.
[0039] The ends of the passages 23_1 A to 23_3A and 23_3B being linear through-grooves formed
in the third plate-like members 23 and the passages 24_2A to 24_4A and 24_4B being
circular through-holes formed in the cladding members 24 laminated on the refrigerant
outflow surfaces of the third plate-like members 23 are formed at positions facing
each other. Therefore, the passages 23_1 A to 23_3A and 23_3B being linear through-grooves
formed in the third plate-like members 23 are blocked, except for the ends, by the
cladding members 24 laminated on the refrigerant outflow surfaces of the third plate-like
members 23.
[0040] The laminated header 2 may include a plurality of combinations of outlet passages
11A and distribution passages 12A. Furthermore, the inlet passage 12a may be formed
in a plate-like member other than the second plate-like member 22. In other words,
the inlet passage 12a may be formed in, for example, the first plate-like member 21
or the third plate-like member 23.
<Flow of Refrigerant in Laminated Header>
[0041] The flow of the refrigerant in the laminated header of the heat exchanger according
to Embodiment 1 will be described below.
[0042] As shown in Fig. 2, the refrigerant passing through the inlet passage 12a flows into
the branching passage 12b_11. In the branching passage 12b_11, the refrigerant passing
through the passage 24_1 A flows into the part between the ends of the passage 23_1A,
branches off into two paths by hitting against the surface of the cladding member
24_2, reaches the opposite ends of the passage 23_1A, and flows into the branching
passage 12b_12 and the through-passage 12c.
[0043] In the branching passage 12b_12, the refrigerant passing through the passage 24_2A
flows into the part between the ends of the passage 23_2A, branches off into two paths
by hitting against the surface of the cladding member 24_3, reaches the opposite ends
of the passage 23_2A, and flows into the two branching passages 12b_13.
[0044] In each branching passage 12b_13, the refrigerant passing through the passage 24_3A
flows into the part between the ends of the passage 23_3A, branches off into two paths
by hitting against the surface of the cladding member 24_4, reaches the opposite ends
of the passage 23_3A, and flows into the heat-transfer tubes 4 via the outlet passages
11A.
[0045] In the through-passage 12c, the refrigerant passing through the passage 24_2B passes
through the passage 23_2B and flows into the branching passage 12b_14.
[0046] In the branching passage 12b_14, the refrigerant passing through the passage 24_3B
flows into the part between the ends of the passage 23_3B, branches off into two paths
by hitting against the surface of the cladding member 24_4, reaches the opposite ends
of the passage 23_3B, and flows into the heat-transfer tubes 4 via the outlet passages
11A.
<Detailed Description of Branching Passages and Through-Passage>
[0047] The branching passages and the through-passage in the laminated header of the heat
exchanger according to Embodiment 1 will be described in detail below.
[0048] Fig. 3 is a perspective view of a relevant part of the distribution passage, illustrating
a state where the laminated header of the heat exchanger according to Embodiment 1
is disassembled. Fig. 4 is a diagram illustrating an overlapped state of the passages
of a branching passage in the heat exchanger according to Embodiment 1.
[0049] As shown in Fig. 3, in the branching passage 12b_11, the equivalent diameter of the
passage 24_2B communicating with the passage 23_2B being a circular through-hole of
the through-passage 12c is smaller than the equivalent diameter of the passage 24_2A
communicating with the passage 23_2A being a linear through-groove of the branching
passage 12b_12.
[0050] In other words, as shown in Fig. 4, assuming that an intersection portion 31 where
the passage 23_1A intersects the passage 24_1A is defined as a branching portion 41
of the branching passage 12b, the passage 24_1A is defined as an inflow passage 42
of the branching passage 12b, a connecting portion 33, connecting the intersection
portion 31 and an upper end 32 of the passage 23_1A, and the passage 24_2B are defined
as a first outflow passage 43 of the branching passage 12b, a connecting portion 35,
connecting the intersection portion 31 and a lower end 34 of the passage 23_1A, and
the passage 24_2A are defined as a second outflow passage 44 of the branching passage
12b, the equivalent diameter of at least part of the first outflow passage 43 is smaller
than the equivalent diameter of at least part of the second outflow passage 44. In
the branching portion 41 of the branching passage 12b, separation occurs in the flow
of the refrigerant. Furthermore, the connecting portions 33 and 35 being linear through-grooves
of the branching passage 12b each have a bent portion 36. At each bent portion 36,
separation occurs in the flow of the refrigerant. Moreover, separation occurs in the
flow of the refrigerant at the upper end 32 and the lower end 34 being linear through-grooves
of the branching passage 12b. In other words, the branching portion 41, the bent portions
36, the upper end 32, and the lower end 34 correspond to "curves at which flow separation
of the refrigerant is to occur".
[0051] Specifically, in the first outflow passage 43 of the branching passage 12b_11, the
refrigerant outflowing from the end not communicating with the branching portion 41
passes through the through-passage 12c and the branching passage 12b_14 before reaching
the outlet passages 11A. Therefore, the number of times the refrigerant passes through
the curves at which separation occurs in the flow of the refrigerant is small. In
contrast, in the second outflow passage 44 of the branching passage 12b_11, the refrigerant
outflowing from the end not communicating with the branching portion 41 passes through
the branching passage 12b_12 and the branching passages 12b_13 before reaching the
outlet passages 11A. Therefore, the number of times the refrigerant passes through
the curves at which separation occurs in the flow of the refrigerant is large. Thus,
if the equivalent diameter of the first outflow passage 43 and the equivalent diameter
of the second outflow passage 44 are equal to each other, a difference occurs between
pressure loss in the refrigerant outflowing from the first outflow passage 43 and
pressure loss in the refrigerant outflowing from the second outflow passage 44, causing
the refrigerant distributed to the outlet passages 11A to become uneven. In contrast,
when the equivalent diameter of at least part of the first outflow passage 43 is smaller
than the equivalent diameter of at least part of the second outflow passage 44, unevenness
in the refrigerant distributed to the outlet passages 11A is suppressed.
[0052] An equivalent diameter is calculated based on Expression 1 below.
[0053] For example, the equivalent diameters of the passages 24_2A and 24_2B are set such
that the flow pattern of the refrigerant is the same before and after passing through
the passages 24_2A and 24_2B. If the flow pattern of the refrigerant changes before
and after passing through the passages 24_2A and 24_2B, the pressure loss occurring
in the refrigerant is dependent on the flow rate and fluctuates significantly. Thus,
the balance in pressure loss in each of the passages 24_2A and 24_2B changes in accordance
with fluctuations in the flow rate of the refrigerant flowing into the distribution
passage 12A, causing the refrigerant distributed to the outlet passages 11A to become
uneven. In the case where, for example, the equivalent diameters of the passages 24_2A
and 24_2B are set such that the flow pattern of the refrigerant is the same, unevenness
in the refrigerant distributed to the outlet passages 11A is suppressed.
[0054] For example, the hole diameters of the passages 24_2A and 24_2B may be set such that
the flow pattern of the refrigerant does not change before and after passing through
the passages 24_2A and 24_2B under a condition in which the refrigerant flows into
the distribution passage 12A at the maximum flow rate and is uniformly distributed
to the outlet passages 11A.
[0055] In particular, for example, the equivalent diameters of the passages 24_2A and 24_2B
may be set such that the flow pattern of the refrigerant becomes an annular flow pattern
or an annular spray flow pattern before and after passing through the passages 24_2A
and 24_2B. With this configuration, the flow state of the refrigerant after passing
through the passages 24_2A and 24_2B is made uniform, thereby achieving improved evenness
in the branching process in the subsequent branching passage 12b.
[0056] Fig. 5 is a Baker diagram illustrating the relationship between the flow state and
the flow pattern of the refrigerant.
[0057] The flow pattern of the refrigerant before and after passing through the passages
24_2A and 24_2B can be calculated by using the Baker diagram shown in Fig. 5. The
Baker diagram is a characteristic diagram showing the flow pattern of the refrigerant
in a two-phase gas-liquid state. The ordinate axis and the abscissa axis indicate
values expressing the flow state of the refrigerant. The ordinate axis is Gg/λ, whereas
the abscissa axis is λ×φ×Gl/Gg. The ordinate axis corresponds to the magnitude of
the mass flow rate of the gaseous phase of the refrigerant. In Fig. 5, the mass flow
rate of the gaseous phase of the refrigerant increases toward the upper side. The
abscissa axis corresponds to the ratio of the mass flow rate between the gaseous phase
and the liquid phase of the refrigerant, that is, the quality. In Fig. 5, the quality
decreases toward the right side.
[0058] In detail, for example, the equivalent diameters of the passages 24_2A and 24_2B
may be set such that the flow state of the refrigerant before and after passing through
the passages 24_2A and 24_2B satisfies the relationship indicated by expression 2
or 3 below.
[0059] In expression 2 and expression 3 below, the mass velocity of the gaseous phase of
the refrigerant is defined as Gg [kg/(m
2·h)], the mass velocity of the liquid phase of the refrigerant is defined as Gl [kg/(m
2·h)], the density of the gaseous phase of the refrigerant is defined as pg [kg/m
3], the density of the liquid phase of the refrigerant is defined as ρl [kg/m
3], the density of air is defined as pa [kg/m
3], the density of water is defined as ρw [kg/m
3], the surface tension of the liquid phase of the refrigerant is defined as σl [N/m],
the surface tension of water is defined as σw [N/m], the viscosity coefficient of
the liquid phase of the refrigerant is defined as µl [µPa·s], and the viscosity coefficient
of water is defined as µw [µPa·s].
[0060] When calculating the flow pattern by using the Baker diagram, the maximum flow rate
of the refrigerant flowing into the distribution passage 12A may be used as the flow
rate, the equivalent diameter of the passage 23_1A may be used as the equivalent diameter
of a passage before the refrigerant passes through the passage 24_2A or 24_2B, and
the equivalent diameter of the passage 24_2A or 24_2B may be used as the equivalent
diameter of a passage before the refrigerant passes through the passage 24_2A or 24_2B.
[0061] Furthermore, in order to achieve evenness in the flow rate of the refrigerant distributed
to the outlet passages 11A to improve the heat exchanging efficiency of the heat exchanger
1, other passages constituting the distribution passage 12A may similarly be set to
equivalent diameters with which the pressure loss occurring in the refrigerant becomes
even. For example, as shown in Fig. 3, the equivalent diameter of the passage 24_3B
may be smaller than the equivalent diameter of each passage 24_3A. Furthermore, for
example, the equivalent diameters of the passage 23_3B and the passages 24_4B may
be smaller than the equivalent diameters of the passages 23_3A and the passages 24_4A.
If there are a plurality of branching passages 12b similar to the branching passage
12b_11, the above-described configuration may be employed in all of the branching
passages, or the above-described configuration may be employed in one or more of the
branching passages.
[0062] When the flow rate of the refrigerant flowing through a passage decreases, the pressure
loss occurring in the refrigerant decreases, so that the effect on the evenness in
the refrigerant as a result of changing the equivalent diameter is reduced. Thus,
the branching passage 12b in which the equivalent diameter of at least part of the
first outflow passage 43 is smaller than the equivalent diameter of at least part
of the second outflow passage 44 may be the branching passage 12b at the upstream
side of the distribution passage 12A. In other words, the refrigerant outflowing from
at least one of the first outflow passage 43 and the second outflow passage 44 in
the branching passage 12b in which the equivalent diameter of at least part of the
first outflow passage 43 is smaller than the equivalent diameter of at least part
of the second outflow passage 44 may be further branched off at another branching
passage 12b.
[0063] Although the above description relates to a case where each branching passage 12b
has different heights, in the direction of gravitational force, at the ends not communicating
with the branching portion 41 between the first outflow passage 43 and the second
outflow passage 44, the branching passage 12b is not limited to such a case. In the
case where the branching passage 12b has different heights, in the direction of gravitational
force, at the ends not communicating with the branching portion 41 between the first
outflow passage 43 and the second outflow passage 44, the advantage of employing the
above-described configuration is noteworthy since it is particularly difficult to
evenly distribute the refrigerant.
[0064] Furthermore, although the above description relates to a case where the branching
passages 12b each have the branching portion 41 in a linear region not parallel to
the direction of gravitational force of the passages 23_1 A to 23_3A and 23_3B, the
branching passages 12b are not limited to such a case. In the case where the branching
passages 12b each have the branching portion 41 in a linear region not parallel to
the direction of gravitational force of the passages 23_1 A to 23_3A and 23_3B, the
refrigerant is evenly branched off at the branching portion 41. Moreover, in a case
where the linear region is substantially orthogonal to the direction of gravitational
force, the angles of branching directions relative to the direction of gravitational
force are made even at the branching portion 41, so that unevenness in the distribution
of the refrigerant due to the effect of gravitational force is suppressed. In particular,
this advantage is noteworthy in the case where each branching passage 12b has different
heights, in the direction of gravitational force, at the ends not communicating with
the branching portion 41 between the first outflow passage 43 and the second outflow
passage 44.
[0065] Furthermore, although the above description relates to a case where, in each branching
passage 12b, the end of the first outflow passage 43 not communicating with the branching
portion 41 is positioned at the upper side of the branching portion 41 in the direction
of gravitational force and the end of the second outflow passage 44 not communicating
with the branching portion 41 is positioned at the lower side of the branching portion
41 in the direction of gravitational force, the branching passages 12b are not limited
to such a case. In the case where, in each branching passage 12b, the end of the first
outflow passage 43 not communicating with the branching portion 41 is positioned at
the upper side of the branching portion 41 in the direction of gravitational force
and the end of the second outflow passage 44 not communicating with the branching
portion 41 is positioned at the lower side of the branching portion 41 in the direction
of gravitational force, the difference in passage length between the first outflow
passage 43 and the second outflow passage 44 can be reduced, thereby achieving even
distribution of the refrigerant without making the passage shapes of the first outflow
passage 43 and the second outflow passage 44 complex.
[0066] Furthermore, although the above description relates to a case where, in each branching
passage 12b, a line connecting the end of the first outflow passage 43 not communicating
with the branching portion 41 and the end of the second outflow passage 44 not communicating
with the branching portion 41 is parallel to the longitudinal direction of the plate-like
member, the branching passages 12b are not limited to such a case. In the case where,
in each branching passage 12b, the line connecting the end of the first outflow passage
43 not communicating with the branching portion 41 and the end of the second outflow
passage 44 not communicating with the branching portion 41 is parallel to the longitudinal
direction of the plate-like member, the plate-like member can be reduced in size in
the lateral direction so that, for example, the component cost and the weight are
reduced. Moreover, in a case where, in each branching passage 12b, the line connecting
the end of the first outflow passage 43 not communicating with the branching portion
41 and the end of the second outflow passage 44 not communicating with the branching
portion 41 is parallel to the direction in which the heat-transfer tubes 4 are arranged,
a space-saving heat exchanger 1 can be achieved. The line connecting the end of the
first outflow passage 43 not communicating with the branching portion 41 and the end
of the second outflow passage 44 not communicating with the branching portion 41,
the longitudinal direction of the plate-like member, and the direction in which the
heat-transfer tubes 4 are arranged do not have to be parallel to the direction of
gravitational force.
<Application of Heat Exchanger>
[0067] An application example of the heat exchanger according to Embodiment 1 will be described
below.
[0068] Although the following description relates to a case where the heat exchanger according
to Embodiment 1 is applied to an air-conditioning apparatus, the application is not
limited thereto. For example, the heat exchanger according to Embodiment 1 may be
applied to another refrigeration cycle apparatus having a refrigerant circuit. Furthermore,
although the following description relates to a case where the air-conditioning apparatus
is configured to switch between the cooling operation and the heating operation, the
air-conditioning apparatus may alternatively be configured to only perform the cooling
operation or the heating operation.
[0069] Fig. 6 illustrates the configuration of the air-conditioning apparatus to which the
heat exchanger according to Embodiment 1 is applied. In Fig. 6, the flow of the refrigerant
during the cooling operation is indicated by a solid arrow, whereas the flow of the
refrigerant during the heating operation is indicated by a dotted arrow.
[0070] As shown in Fig. 6, an air-conditioning apparatus 91 has a compressor 92, a four-way
valve 93, an outdoor heat exchanger (heat-source-side heat exchanger) 94, an expansion
device 95, an indoor heat exchanger (load-side heat exchanger) 96, an outdoor fan
(heat-source-side fan) 97, an indoor fan (load-side fan) 98, and a controller 99.
The compressor 92, the four-way valve 93, the outdoor heat exchanger 94, the expansion
device 95, and the indoor heat exchanger 96 are connected by a refrigerant pipe, so
that a refrigerant circuit is formed.
[0071] The controller 99 is connected to, for example, the compressor 92, the four-way valve
93, the expansion device 95, the outdoor fan 97, the indoor fan 98, and various types
of sensors. The controller 99 changes the passage of the four-way valve 93 to switch
between the cooling operation and the heating operation.
[0072] The flow of the refrigerant during the cooling operation will be described.
[0073] The refrigerant in a high-pressure high-temperature gas state discharged from the
compressor 92 flows into the outdoor heat exchanger 94 via the four-way valve 93 and
condenses by exchanging heat with air supplied by the outdoor fan 97. The condensed
refrigerant turns into a high-pressure liquid state, outflows from the outdoor heat
exchanger 94, and is turned into a low-pressure two-phase gas-liquid state by the
expansion device 95. The refrigerant in the low-pressure two-phase gas-liquid state
flows into the indoor heat exchanger 96 and evaporates by exchanging heat with air
supplied by the indoor fan 98, thereby cooling the interior. The evaporated refrigerant
turns into a low-pressure gas state, outflows from the indoor heat exchanger 96, and
is suctioned into the compressor 92 via the four-way valve 93.
[0074] The flow of the refrigerant during the heating operation will be described.
[0075] The refrigerant in a high-pressure high-temperature gas state discharged from the
compressor 92 flows into the indoor heat exchanger 96 via the four-way valve 93 and
condenses by exchanging heat with air supplied by the indoor fan 98, thereby heating
the interior. The condensed refrigerant turns into a high-pressure liquid state, outflows
from the indoor heat exchanger 96, and is turned into refrigerant in a low-pressure
two-phase gas-liquid state by the expansion device 95. The refrigerant in the low-pressure
two-phase gas-liquid state flows into the outdoor heat exchanger 94 and evaporates
by exchanging heat with air supplied by the outdoor fan 97. The evaporated refrigerant
turns into a low-pressure gas state, outflows from the outdoor heat exchanger 94,
and is suctioned into the compressor 92 via the four-way valve 93.
[0076] The heat exchanger 1 is used as at least one of the outdoor heat exchanger 94 and
the indoor heat exchanger 96. When functioning as an evaporator, the heat exchanger
1 is connected such that the refrigerant inflows from the laminated header 2 and the
refrigerant outflows to the header 3. In other words, when the heat exchanger 1 functions
as an evaporator, the refrigerant in a two-phase gas-liquid state flows into the laminated
header 2 from the refrigerant pipe. When the heat exchanger 1 functions as a condenser,
the refrigerant flows backward through the laminated header 2.
[0077] Since the laminated header 2 achieves improved evenness in the distribution of the
refrigerant owing to the above-described configuration, evenness in the flow rate
and the quality of the refrigerant outflowing to the plurality of heat-transfer tubes
4 can be achieved even when refrigerant in a two-phase gas-liquid state, which is
relatively difficult to distribute evenly, flows in. In other words, the laminated
header 2 is suitable for a refrigeration cycle apparatus, such as the air-conditioning
apparatus 91.
<Advantageous Effects of Heat Exchanger>
[0078] The advantageous effects of the heat exchanger according to Embodiment 1 will be
described below.
[0079] In the laminated header 2, each branching passage 12b has the first outflow passage
43 having a small number of curves, at which flow separation of the refrigerant is
to occur, in a flow path through which the refrigerant inflowing from the inflow passage
42 passes before reaching the outlet passages 11A, and also has the second outflow
passage 44 having a large number of curves, at which flow separation of the refrigerant
is to occur, in a flow path through which the refrigerant inflowing from the inflow
passage 42 passes before reaching the outlet passages 11A. The equivalent diameter
of at least part of the first outflow passage 43 is smaller than the equivalent diameter
of at least part of the second outflow passage 44. Therefore, reduction in the evenness
of the distribution of the refrigerant is suppressed, while the number of outlet passages
11A can be changed to a number other than multiples of powers of 2, thereby allowing
for an increased degree of freedom in the number of outlet passages 11A in the laminated
header 2.
[0080] Furthermore, in the laminated header 2, the distribution passage 12A is formed by
laminating plate-like members. Therefore, regardless of the fact that the laminated
header 2 is capable of suppressing reduction in the evenness of the distribution of
the refrigerant while also allowing for a change in the number of outlet passages
11A to a number other than multiples of powers of 2, for example, the equivalent diameter
of each passage, the shape of each passage, the number of distributions, and the number
of branch paths in the branching portion 41 can be easily changed by changing, for
example, the hole diameter of each plate-like member, the groove width of each plate-like
member, the hole shape or the groove shape of each plate-like member, the number of
plate-like members, and the thickness of each plate-like member.
Embodiment 2
[0081] A heat exchanger according to Embodiment 2 will now be described.
[0082] Redundant or similar descriptions as those in Embodiment 1 are simplified, where
appropriate, or are omitted.
<Configuration of Laminated Header>
[0083] The configuration of a laminated header of the heat exchanger according to Embodiment
2 will be described below.
[0084] Fig. 7 is a perspective view illustrating a state where the laminated header of the
heat exchanger according to Embodiment 2 is disassembled.
[0085] As shown in Fig. 7, by joining a second plate-like member 22, third plate-like members
23_1 and 23_2, and cladding members 24_1 to 24_3, a passage 22A formed in the second
plate-like member 22, passages 23_1A, 23_2A, and 23_2B formed in the third plate-like
members 23_1 and 23_2, and passages 24_1A to 24_3A and 24_2B and 24_3B formed in the
cladding members 24_1 to 24_3 communicate with one another, whereby a distribution
passage 12A is formed.
[0086] The distribution passage 12A has an inlet passage 12a and branching passages 12b_21
to 12b_23. The number and the order of the branching passages 12b_21 to 12b_23 are
changed, where appropriate, in accordance with, for example, the number of heat-transfer
tubes 4. In the following description, the branching passages 12b_21 to 12b_23 are
sometimes collectively referred to as branching passages 12b.
[0087] By joining the third plate-like member 23_1 to the cladding members 24_1 and 24_2,
the passage 24_1 A formed in the cladding member 24_1, the passage 23_1 A formed in
the third plate-like member 23_1, and the two passages 24_2A and the one passage 24_2B
formed in the cladding member 24_2 communicate with one another, whereby a branching
passage 12b_21 is formed. The passage 23_1A is a linear through-groove. The passages
24_2A and 24_2B are circular through-holes.
[0088] By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3,
the passages 24_2A formed in the cladding member 24_2, the passages 23_2A formed in
the third plate-like member 23_2, and the two pairs of passages 24_3A formed in the
cladding member 24_3 communicate with one another, whereby branching passages 12b_22
are formed. The passages 23_2A are linear through-grooves. The passages 24_3A are
circular through-holes.
[0089] By joining the third plate-like member 23_2 to the cladding members 24_2 and 24_3,
the passage 24_2B formed in the cladding member 24_2, the passage 23_2B formed in
the third plate-like member 23_2, and the two passages 24_3B formed in the cladding
member 24_3 communicate with one another, whereby a branching passage 12b_23 is formed.
The passage 23_2B is a linear through-groove. The passages 24_3B are circular through-holes.
[0090] Parts located between ends of the passages 23_1A, 23_2A, and 23_2B being linear through-grooves
formed in the third plate-like members 23 and the passages 24_1A, 24_2A, and 24_2B
being circular through-holes formed in the cladding members 24 laminated on the refrigerant
inflow surfaces of the third plate-like members 23 are formed at positions facing
each other. Therefore, the passages 23_1A, 23_2A, and 23_2B being linear through-grooves
formed in the third plate-like members 23 are blocked, except for the parts between
the ends, by the cladding members 24 laminated on the refrigerant inflow surfaces
of the third plate-like members 23.
[0091] The ends of the passages 23_1A, 23_2A, and 23_2B being linear through-grooves formed
in the third plate-like members 23 and the passages 24_2A, 24_3A, and 24_3B being
circular through-holes formed in the cladding members 24 laminated on the refrigerant
outflow surfaces of the third plate-like members 23 are formed at positions facing
each other. Moreover, the passage 24_1 A being a circular through-hole formed in the
cladding member 24_1 laminated on the refrigerant inflow surface of the third plate-like
member 23_1 and the passage 24_2B being a circular through-hole formed in the cladding
member 24_2 laminated on the refrigerant outflow surface of the third plate-like member
23_1 are formed at positions facing each other. Therefore, the passages 23_2A and
23_2B being linear through-grooves formed in the third plate-like members 23 excluding
the third plate-like member 23_1 are blocked, except for the ends, by the cladding
members 24 laminated on the refrigerant outflow surfaces of the relevant third plate-like
members 23. Moreover, the passage 23_1A being a linear through-groove formed in the
third plate-like member 23_1 is blocked, except for the part between the ends and
the ends, by the cladding member 24_2 laminated on the refrigerant outflow surface
of the third plate-like member 23_1.
<Flow of Refrigerant in Laminated Header>
[0092] The flow of the refrigerant in the laminated header of the heat exchanger according
to Embodiment 2 will be described below.
[0093] As shown in Fig. 7, the refrigerant passing through the inlet passage 12a flows into
the branching passage 12b_21. In the branching passage 12b_21, the refrigerant passing
through the passage 24_1 A passes through the part between the ends of the passage
23_1A, reaches the opposite ends of the passage 23_1A, and flows into the two branching
passages 12b_22 and the one branching passage 12b_23.
[0094] In each branching passage 12b_22, the refrigerant passing through the passage 24_2A
flows into the part between the ends of the passage 23_2A, branches off into two paths
by hitting against the surface of the cladding member 24_3, reaches the opposite ends
of the passage 23_2A, and flows into the heat-transfer tubes 4 via the outlet passages
11A.
[0095] In the branching passage 12b_23, the refrigerant passing through the passage 24_2B
flows into the part between the ends of the passage 23_2B, branches off into two paths
by hitting against the surface of the cladding member 24_3, reaches the opposite ends
of the passage 23_2B, and flows into the heat-transfer tubes 4 via the outlet passages
11A.
<Detailed Description of Branching Passages and Through-Passage>
[0096] The branching passages and the through-passage in the laminated header of the heat
exchanger according to Embodiment 2 will be described in detail below.
[0097] Fig. 8 is a perspective view of a relevant part of the distribution passage, illustrating
a state where the laminated header of the heat exchanger according to Embodiment 2
is disassembled. Fig. 9 is a diagram illustrating an overlapped state of the passages
of a branching passage in the heat exchanger according to Embodiment 2.
[0098] As shown in Fig. 8, in the branching passage 12b_21, the equivalent diameter of the
passage 24_2B facing the part between the ends of the passage 23_1A and also facing
the passage 24_1A is smaller than the equivalent diameter of each of the passages
24_2A facing the ends of the passage 23_1A.
[0099] In other words, as shown in Fig. 9, assuming that an intersection portion 31 where
the passage 23_1A intersects the passage 24_1A is defined as a branching portion 41
of the branching passage 12b, the passage 24_1A is defined as an inflow passage 42
of the branching passage 12b, the passage 24_2B is defined as a first outflow passage
43 of the branching passage 12b, connecting portions 33 and 35, connecting the intersection
portion 31 and an upper end 32 or a lower end 34 of the passage 23_1A, and the passage
24_2A are defined as a second outflow passage 44 of the branching passage 12b, the
equivalent diameter of at least part of the first outflow passage 43 is smaller than
the equivalent diameter of at least part of the second outflow passage 44. The refrigerant
flowing into the branching portion 41 from the inflow passage 42 flows easily into
the first outflow passage 43 but is unlikely to flow into the second outflow passage
44. In other words, in a passage connecting the inflow passage 42 and the second outflow
passage 44, the branching portion 41 corresponds to "a curve at which flow separation
of the refrigerant is to occur".
[0100] Specifically, in the first outflow passage 43 of the branching passage 12b_21, the
refrigerant inflows from the inflow passage 42 without being bent at the branching
portion 41 and flows into the subsequent branching passage 12b_23 without traveling
through the bent portion 36 of the passage 23_1A and the upper end 32 or the lower
end 34 of the passage 23_1 A. Therefore, the number of times the refrigerant inflowing
from the inflow passage 42 passes through curves at which separation occurs in the
flow of the refrigerant before reaching the outlet passages 11A is small. In contrast,
in the second outflow passage 44 of the branching passage 12b_21, the refrigerant
inflowing from the inflow passage 42 is bent at the branching portion 41, travels
through the bent portion 36 of the passage 23_1A and the upper end 32 or the lower
end 34 of the passage 23_1A, and subsequently flows into the subsequent branching
passage 12b_22. Therefore, the number of times the refrigerant inflowing from the
inflow passage 42 passes through curves at which separation occurs in the flow of
the refrigerant before reaching the outlet passages 11A is large. Thus, if the equivalent
diameter of the first outflow passage 43 and the equivalent diameter of the second
outflow passage 44 are equal to each other, a difference occurs between pressure loss
in the refrigerant passing through the first outflow passage 43 and pressure loss
in the refrigerant passing through the second outflow passage 44, causing the refrigerant
distributed to the outlet passages 11A to become uneven. In contrast, when the equivalent
diameter of at least part of the first outflow passage 43 is smaller than the equivalent
diameter of at least part of the second outflow passage 44, unevenness in the refrigerant
distributed to the outlet passages 11A is suppressed.
[0101] Furthermore, in order to achieve evenness in the flow rate of the refrigerant distributed
to the outlet passages 11A to improve the heat exchanging efficiency of the heat exchanger
1, other passages constituting the distribution passage 12A preferably similarly be
set to equivalent diameters with which the pressure loss occurring in the refrigerant
becomes even. For example, as shown in Fig. 8, the equivalent diameter of each of
the passage 23_2B and the passages 24_3B may be smaller than the equivalent diameter
of each of the passages 23_2A and the passages 24_3A, respectively. If there are a
plurality of branching passages 12b similar to the branching passage 12b_21, the above-described
configuration may be employed in all of the branching passages, or the above-described
configuration may be employed in one or more of the branching passages.
<Advantageous Effects of Heat Exchanger>
[0102] The advantageous effects of the heat exchanger according to Embodiment 2 will be
described below.
[0103] In the laminated header 2, each branching passage 12b has the first outflow passage
43 having a small number of curves, at which flow separation of the refrigerant is
to occur, in a flow path through which the refrigerant inflowing from the inflow passage
42 passes before reaching the outlet passages 11A, and also has the second outflow
passage 44 having a large number of curves, at which flow separation of the refrigerant
is to occur, in a flow path through which the refrigerant inflowing from the inflow
passage 42 passes before reaching the outlet passages 11A. The equivalent diameter
of at least part of the first outflow passage 43 is smaller than the equivalent diameter
of at least part of the second outflow passage 44. Therefore, reduction in the evenness
of the distribution of the refrigerant is suppressed, while the number of outlet passages
11A can be changed to a number other than multiples of powers of 2, thereby allowing
for an increased degree of freedom in the number of outlet passages 11A in the laminated
header 2.
[0104] Furthermore, in the laminated header 2, the distribution passage 12A has the branching
passage 12b_21 that causes the inflowing refrigerant to branch off into three paths,
that is, causes the inflowing refrigerant to branch off into a large number of branch
paths. Therefore, the laminated header 2 can be reduced in thickness, so that the
laminated header 2 is reduced in size and cost. Moreover, the number of plate-like
members constituting the laminated header 2 can be reduced, thereby reducing, for
example, the manufacturing costs.
<Modifications>
[0105] Figs. 10 and 11 are perspective views illustrating a state where the laminated header
in modifications of the heat exchanger according to Embodiment 2 is disassembled.
[0106] As shown in Fig. 10, the refrigerant outflowing from the first outflow passage 43
of the branching passage 12b_21 may flow into the through-passage 12c. In other words,
the configuration of the heat exchanger according to Embodiment 1 and the configuration
of the heat exchanger according to Embodiment 2 may be combined. In that case, the
degree of freedom in the number of outlet passages 11A in the laminated header 2 is
further increased.
[0107] Furthermore, as shown in Fig. 11, for example, the refrigerant outflowing from the
first outflow passage 43 of the branching passage 12b_21 may flow into the branching
passage 12b_22, and the refrigerant outflowing from the second outflow passage 44
of the branching passage 12b_21 may flow into the through-passage 12c. In that case,
in order to achieve evenness in the refrigerant distributed to the outlet passages
11A, the equivalent diameter of at least part of the first outflow passage 43 may
possibly be set to be larger than the equivalent diameter of at least part of the
second outflow passage 44. In that case, the first outflow passage 43 corresponds
to a "second outflow passage" according to the present invention, and the second outflow
passage 44 corresponds to a "first outflow passage" according to the present invention.
[0108] Although Embodiment 1 and Embodiment 2 have been described above, the present invention
is not to be limited to Embodiment 1 and Embodiment 2. For example, Embodiment 1 and
Embodiment 2 may be entirely or partially combined, or may be combined with the modifications.
Reference Signs List
[0109] 1 heat exchanger 2 laminated header 2A refrigerant inflow section 2B refrigerant
outflow section 3 header 3A refrigerant inflow section 3B refrigerant outflow section
4 heat-transfer tube 5 support member 6 fin 11 first plate-like body 11A outlet passage
12 second plate-like body 12A distribution passage 12a inlet passage 12b, 12b_11 to
12b_14, 12b_21 to 12b_23 branching passage 12c through-passage 21 first plate-like
member 21A passage 22 second plate-like member 22A passage 23, 23_1 to 23_3 third
plate-like member 23_1 A to 23_3A, 23_2B, 23_3B passage 24, 24_1 to 24_5 cladding
member 24_1Ato 24_5A, 24_2B to 24_4B passage 31 intersection portion 32 upper end
33 connecting portion 34 lower end 35 connecting portion 36 bent portion 41 branching
portion 42 inflow passage 43 first outflow passage 44 second outflow passage 91 air-conditioning
apparatus 92 compressor 93 four-way valve 94 outdoor heat exchanger 95 expansion device
96 indoor heat exchanger 97 outdoor fan 98 indoor fan 99 controller
1. Laminiertes Kopfstück (2), umfassend:
einen ersten plattenähnlichen Körper (11), aufweisend eine Vielzahl von Auslassdurchgängen
(11A); und
einen zweiten plattenähnlichen Körper (12), der am ersten plattenähnlichen Körper
(11) befestigt ist und einen Einlassdurchgang (12a) und zumindest ein Teil eines Verteilungsdurchgangs
(12A) aufweist, der eingerichtet ist, Kältemittel, das von einem Einlassdurchgang
(12a) einströmt, an die Vielzahl von Auslassdurchgängen (11A) zu verteilen und abzugeben,
wobei der Verteilungsdurchgang (12A) einen Abzweigungsdurchgang (12b), aufweisend
einen Einströmungsdurchgang (42), einen Abzweigungsabschnitt (41), kommunizierend
mit dem Einströmungsdurchgang (42), und eine Vielzahl von Ausströmungsdurchgängen
(43, 44), kommunizierend mit dem Abzweigungsabschnitt (41), aufweist,
wobei die Vielzahl von Ausströmungsdurchgängen (43, 44) einen ersten Ausströmungsdurchgang
(43) und einen zweiten Ausströmungsdurchgang (44) aufweisen,
wobei ein äquivalenter Durchmesser von zumindest einem Teil des ersten Ausströmungsdurchgangs
(43) kleiner ist als ein äquivalenter Durchmesser von zumindest einem Teil des zweiten
Ausströmungsdurchgangs (44),
dadurch gekennzeichnet, dass eine Anzahl von Abzweigungsdurchgängen, an denen Trennung des Kältemittels durch
Abzweigen auftritt, in einem Strömungspfad, den das aus dem Einströmungsdurchgang
(42) einströmende Kältemittel über den ersten Ausströmungsdurchgang (43) vor Erreichen
der Ausströmungsdurchgänge (11A) passiert, kleiner ist als eine Anzahl von Kurven
in einem Strömungspfad, den das aus dem Einströmungsdurchgang (42) einströmende Kältemittel
über den zweiten Ausströmungsdurchgang (44) vor Erreichen der Ausströmungsdurchgänge
(11A) passiert.
2. Laminiertes Kopfstück (2) nach Anspruch 1,
wobei der Verteilungsdurchgang (12A) neben dem Abzweigungsdurchgang (12b) einen weiteren
Abzweigungsdurchgang (12b) aufweist, und
wobei das Kältemittel, das aus zumindest einem von dem ersten Ausströmungsdurchgang
(43) und dem zweiten Ausströmungsdurchgang (44) herausströmt, an dem anderen Abzweigungsdurchgang
(12b) weiter abgezweigt wird.
3. Laminiertes Kopfstück (2) nach Anspruch 1 oder 2,
wobei zumindest einer von dem ersten Ausströmungsdurchgang (43) und dem zweiten Ausströmungsdurchgang
(44) ein mit dem Abzweigungsabschnitt kommunizierendes Ende (41), aufweist, wobei
das einem Ende des Einströmungsdurchgangs (42) zugewandte Ende mit dem Abzweigungsabschnitt
(41) kommuniziert.
4. Laminiertes Kopfstück (2) nach einem der Ansprüche 1 bis 3,
wobei die Vielzahl von Ausströmungsdurchgängen (43, 44) jeweils Enden aufweisen, die
mit dem Abzweigungsabschnitt (41) nicht kommunizieren, wobei die Enden auf unterschiedlichen
Höhen in einer Richtung der Schwerkraft positioniert sind.
5. Laminiertes Kopfstück (2) nach einem der Ansprüche 1 bis 4,
wobei ein Strömungsmuster des Kältemittels vor und nach Passieren zumindest eines
Teils der Vielzahl von Ausströmungsdurchgängen (43, 44) identisch ist.
6. Laminiertes Kopfstück (2) nach Anspruch 5,
wobei ein Strömungsmuster des Kältemittels vor und nach Passieren zumindest eines
Teils der Vielzahl von Ausströmungsdurchgängen (43, 44) ein ringförmiges Strömungsmuster
ist, und
wobei ein Strömungszustand des Kältemittels eine Beziehung aufweist, die durch einen
unten aufgeführten Ausdruck angezeigt wird:
wobei Gg [kgj(m
2·h)] eine Massengeschwindigkeit einer gasförmigen Phase des Kältemittels bezeichnet,
Gl [kgj(m
2·h)] eine Massengeschwindigkeit einer flüssigen Phase des Kältemittels bezeichnet,
pg [kg/m
3] eine Dichte der gasförmigen Phase des Kältemittels bezeichnet, ρl [kg/m
3] eine Dichte der flüssigen Phase des Kältemittels bezeichnet, pa [kg/m
3] eine Dichte von Luft bezeichnet, ρw [kg/m
3] eine Dichte von Wasser bezeichnet, σl [N/m] eine Oberflächenspannung der flüssigen
Phase des Kältemittels bezeichnet, σw [N/m] eine Oberflächenspannung von Wasser bezeichnet,
µl [µPa·s] einen Viskositätskoeffizienten der flüssigen Phase des Kältemittels bezeichnet
und µw [µPa·s] einen Viskositätskoeffizienten von Wasser bezeichnet.
7. Laminiertes Kopfstück (2) nach Anspruch 5,
wobei ein Strömungsmuster des Kältemittels vor und nach Passieren zumindest eines
Teils der Vielzahl von Ausströmungsdurchgängen (43, 44) ein ringförmiges Sprühströmungsmuster
ist, und
wobei ein Strömungszustand des Kältemittels eine Beziehung aufweist, die durch einen
unten aufgeführten Ausdruck angezeigt wird:
wobei Gg [kgj(m
2·h)] eine Massengeschwindigkeit einer gasförmigen Phase des Kältemittels bezeichnet,
Gl [kgj(m
2·h)] eine Massengeschwindigkeit einer flüssigen Phase des Kältemittels bezeichnet,
ρg [kg/m
3] eine Dichte der gasförmigen Phase des Kältemittels bezeichnet, ρl [kg/m
3] eine Dichte der flüssigen Phase des Kältemittels bezeichnet, ρa [kg/m
3] eine Dichte von Luft bezeichnet, ρw [kg/m
3] eine Dichte von Wasser bezeichnet, σl [N/m] eine Oberflächenspannung der flüssigen
Phase des Kältemittels bezeichnet, σw [N/m] eine Oberflächenspannung von Wasser bezeichnet,
µl [µPa·s] einen Viskositätskoeffizienten der flüssigen Phase des Kältemittels bezeichnet
und µw [µPa·s] einen Viskositätskoeffizienten von Wasser bezeichnet.
8. Wärmetauscher (1), umfassend:
das laminierte Kopfstück (2) nach einem der Ansprüche 1 bis 7; und
eine Vielzahl von Wärmeübertragungsleitungen (4), die mit der Vielzahl von Auslassdurchgängen
(11A) jeweils verbunden sind.
9. Klimaanlage (91), umfassend:
den Wärmetauscher (1) nach Anspruch 8,
wobei der Verteilungsdurchgang (12A) das Kältemittel an die Vielzahl von Auslassdurchgängen
(11A) abgibt, wenn der Wärmetauscher (1) als ein Verdampfer dient.