Technical Field
[0001] The present invention relates to a refrigerant distributing device that is mountable
to a heat exchanger used in a refrigeration cycle apparatus such as an air-conditioning
apparatus and distributes a refrigerant, a heat exchanger including the refrigerant
distributing device, a refrigeration cycle apparatus, and an air-conditioning apparatus.
Background Art
[0002] Conventionally, there is a heat exchanger in which a pair of headers extends in an
up-down direction so as to be spaced apart from each other in a right-left direction,
a plurality of flattened pipes are disposed in parallel between the pair of headers,
and both end portions of each of a plurality of heat exchange pipes communicate with
the pair of headers. In the case where such a heat exchanger is used as an evaporator,
a refrigerant flows thereinto as a two-phase gas-liquid flow, and thus liquid stays
in the gravitational direction within the header at an inlet side, while gas stays
in an upper portion within the header. Thus, it is not possible to uniformly distribute
the refrigerant to each flattened pipe, resulting in deterioration of the performance
of the heat exchanger.
[0003] Therefore, in the case where the heat exchanger is used as an evaporator, the header
at the inlet side is required to have a function to uniformly distribute the refrigerant.
As such a refrigerant distributing device, conventionally, there is a refrigerant
distributing device in which a loop-shaped flow path is formed within a header so
as to be turned in an up-down direction, a flow of a two-phase refrigerant having
flowed therein is circulated within the header to be made uniform, whereby the refrigerant
is distributed to each of a plurality of heat-transfer pipes (see, e.g., Patent Literature
1).
[0004] In addition, as an evaporator that allows uniform distribution of a refrigerant,
there is an evaporator that has a configuration in which a pair of headers extends
in a right-left direction (the horizontal direction) so as to be spaced apart from
each other and a plurality of flattened pipes are disposed in parallel between the
pair of headers, and in which a plurality of refrigerant inlets are provided in the
header at an inlet side so as to be spaced apart from each other in the right-left
direction, and a refrigerant is jetted and flowed from each refrigerant inlet into
the header via an orifice (see, e.g., Patent Literature 2).
Citation List
Patent Literature
[0005]
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2011-85324 (Abstract, Fig. 1)
Patent Literature 2: Japanese Unexamined Patent Application Publication No. 2000-249428 (Abstract, Fig. 4)
[0006] DE19515527A1 discloses that an evaporator in a flat tube or plate design for the coolant circuit
in a car's air conditioning unit has a feed pipe the internal heat exchanger fluid
leading to a distributer. This spreads the fluid over the inlets to the channels in
the evaporator. The distributer pipes join up together before the feed pipe. The pipes
are joined to a set of intermediate chambers which communicate with the inlets to
the flat tubes, separated by internal walls within a tubular housing. With an even-number
of evaporator inlets per intermediate chamber, the outlet from the distributer pipe
is centrally located on the opposite wall. Moreover,
DE19515527A1 discloses a refrigerant distributing device according to the preamble of claim 1.
[0007] CN102278908A also discloses a refrigerant distributing device according to the preamble of claim
1.
Summary of Invention
Technical Problem
[0008] With the structure of Patent Literature 1, although an effect of refrigerant uniform
distribution is observed at a certain level, all of the plurality of heat-transfer
pipes communicate with each other in the interior of the header and thus are influenced
in the interior of the header by a head difference. Therefore, the refrigerant distribution
effect cannot be sufficient and further improvement thereof is desired.
[0009] In Patent Literature 2, since the header is horizontally mounted, the header is not
influenced by a head difference. However, in the case where the header is mounted
so as to stand in the up-down direction, a liquid is likely to stay in a lower portion
under influence of the head difference.
[0010] The present invention has been made in view of such points, and an object of the
present invention is to provide a refrigerant distributing device that is able to
uniformly distribute a refrigerant by suppressing the influence of a head difference,
a heat exchanger including the refrigerant distributing device, a refrigeration cycle
apparatus, and an air-conditioning apparatus.
Solution to Problem
[0011] A refrigerant distributing device according to the independent claim is provided.
Advantageous Effects of Invention
[0012] According to the present invention, it is possible to obtain a refrigerant distributing
device that is able to uniformly distribute a refrigerant by suppressing the influence
of a head difference. It is possible to obtain an effective effect when the header
is mounted so as to stand in the up-down direction.
Brief Description of Drawings
[0013]
[Fig. 1] Fig. 1 is a schematic perspective view of a heat exchanger including a refrigerant
distributing device according to one embodiment of the present invention.
[Fig. 2] Fig. 2 is a schematic cross-sectional view of a portion of the refrigerant
distributing device in Fig. 1.
[Fig. 3] Fig. 3 is a perspective view showing a flattened pipe in Fig. 1.
[Fig. 4] Fig. 4 is a diagram showing a refrigerant circuit of a refrigeration cycle
apparatus to which the heat exchanger in Fig. 1 is applied.
[Fig. 5] Fig. 5 is a diagram showing another configuration example of the refrigerant
distributing device.
[Fig. 6] Fig. 6 is a diagram illustrating the principle of determining the height
of each chamber in accordance with a wind speed distribution.
Description of Embodiments
[0014] Fig. 1 is a schematic perspective view of a heat exchanger including a refrigerant
distributing device according to one embodiment of the present invention. Fig. 2 is
a schematic cross-sectional view of a portion of the refrigerant distributing device
in Fig. 1. In Figs. 1 and 2 and the figures described below, portions designated by
the same reference signs are the same or equivalent portions, and the same applies
to the entire specification. In addition, the forms of constituent elements described
in the entire specification are merely illustrative and not limited to these descriptions.
[0015] A heat exchanger 1 is a parallel-flow type heat exchanger which flows a refrigerant
in parallel, and includes a pair of headers 10 (10a, 10b) each header is spaced apart
from each other in a right-left direction and stands in an up-down direction; and
a plurality of flattened pipes (heat-transfer pipes) 20 that are disposed in parallel
in the up-down direction between the pair of headers 10 and both ends of each of which
are connected to the pair of headers 10. The heat exchanger 1 further includes a plurality
of fins 30 and a distributor 40. The pair of headers 10, the flattened pipes 20, and
the fins 30 is formed of aluminum or an aluminum alloy. The distributor 40 is connected
to the header 10a via capillary tubes 50 and forms a refrigerant distributing device
with the header 10a.
[0016] The fins 30 are plate-shaped fins that are stacked between the pair of headers 10
so as to be spaced apart from each other and between which air passes. The plurality
of flattened pipes 20 extend through the fins 30. The fins 30 may not necessarily
be plate-shaped fins. For example, the fins 30 may be, for example, wave-shaped fins
that are stacked in the up-down direction alternately with the flattened pipes 20,
and in short, may be fins that are disposed so as to allow air to pass therethrough
in an air passing direction.
[0017] As shown in Fig. 3, each flattened pipe 20 has a plurality of through holes 20a serving
as refrigerant flow paths.
[0018] The interior of the header 10a is divided by one or more division plates 11 in the
up-down direction into a plurality of chambers 12. Here, eight chambers 12 are formed
by seven division plates 11. At each chamber 12, a plurality of through holes 13 are
formed so as to be aligned in the up-down direction. The flattened pipe 20 is connected
to each through hole 13. In addition, each chamber 12 is connected to the distributor
40 via the capillary tube 50.
[0019] The distributor 40 includes therein an orifice (not shown) that reduces a flow of
the refrigerant. In the case where the heat exchanger 1 is used as an evaporator,
the distributor 40 causes a two-phase gas-liquid flow entering thereinto to be a spray
flow (uniform flow) by passing the refrigerant through the orifice, thereby making
the refrigerant into a state where uniform distribution of the refrigerant is easy.
The refrigerant made into a spray flow is uniformly distributed to the respective
capillary tubes 50 and flows thereinto, and flows into the respective chambers 12
through the capillary tubes 50.
[0020] Each capillary tube 50 adjusts the pressure loss therein with its specifications
(length, inner diameter), thereby adjusting a distribution ratio to each chamber 12
of the header 10a. Here, the specifications of all of the capillary tubes 50 are the
same, and thus the refrigerant is flowed into each chamber 12 in the same amount.
[0021] In manufacturing the heat exchanger 1 configured as described above, the flattened
pipes 20, the fins 30, and the pair of headers 10 are simultaneously joined by means
of brazing in a furnace in an assembled state, and then the distributor 40 and each
respective capillary tube 50 are connected to each other.
[0022] Fig. 4 is a diagram showing a refrigerant circuit of a refrigeration cycle apparatus
to which the heat exchanger in Fig. 1 is applied.
[0023] A refrigeration cycle apparatus 60 includes a compressor 61, a condenser 62, an expansion
valve 63 as a pressure reducing device, and an evaporator 64. The heat exchanger 1
is used in at least one of the condenser 62 and the evaporator 64. A gas refrigerant
discharged from the compressor 61 flows into the condenser 62, exchanges heat with
air passing through the condenser 62, to become a high-pressure liquid refrigerant,
and flows out therefrom. The high-pressure liquid refrigerant having flowed out of
the condenser 62 is reduced in pressure by the expansion valve 63 to become a low-pressure
two-phase gas-liquid refrigerant, and flows into the evaporator 64. The low-pressure
two-phase gas-liquid refrigerant having flowed into the evaporator 64 exchanges heat
with air passing through the evaporator 64, to become a low-pressure gas refrigerant,
and is sucked into the compressor 61 again.
[0024] Hereinafter, a flow of the refrigerant in the case where the heat exchanger 1 is
used as an evaporator will be described with reference to Figs. 1 to 4. In Fig. 1,
a solid arrow indicates the flow of the refrigerant in the case where the heat exchanger
1 is used as an evaporator.
[0025] The flow of the two-phase gas-liquid refrigerant having flowed out of the expansion
valve 63 first enters into the distributor 40 and is made into a spray flow. The refrigerant
made into a spray flow is uniformly distributed to the respective capillary tubes
50 and flows thereinto. The refrigerant having passed through the respective capillary
tubes 50 flows into the respective chambers 12 of the header 10a.
[0026] Here, in the case with a configuration of the related art in which no division plate
is provided in a header, since the entire interior of the header is a single space,
a head difference due to the gravity is great, and thus a drift is likely to occur.
However, in the present embodiment, the division plates 11 are provided to divide
the interior of the header 10a, and the refrigerant is flowed into each chamber 12
at which the head difference is small. Thus, the effect of the head difference on
the refrigerant having flowed into each chamber 12 is reduced, and the refrigerant
in each chamber 12 is uniformly distributed to each flattened pipe 20 connected to
the chamber 12 and flows thereinto.
[0027] The refrigerant having flowed into each flattened pipe 20 flows through the through
holes 20a of the flattened pipe 20 toward the header 10b, joins each other in the
header 10b, and flows out of the heat exchanger 1 through an external connection pipe
14.
[0028] Hereinafter, a flow of the refrigerant in the case where the heat exchanger 1 is
used as a condenser will be described with reference to Figs. 1 and 4. In Fig. 1,
a dotted arrow indicates the flow of the refrigerant in the case where the heat exchanger
1 is used as a condenser.
[0029] The flow of the gas refrigerant having flowed out of the compressor 61 enters into
the header 10b, is uniformly distributed therein, and flows into each flattened pipe
20. When the refrigerant is in a gas state, uniform distribution of the refrigerant
is easy. Thus, a refrigerant distributing device such as a distributor is unnecessary,
and a configuration is provided in which the flow of the gas refrigerant having flowed
out of the compressor 61 is directly flowed into the header 10b.
[0030] Then, the refrigerant having flowed into each flattened pipe 20 flows through the
through holes 20a of the flattened pipe 20 toward the header 10a and flows into each
chamber 12 of the header 10a. The refrigerant having flowed into each chamber 12 flows
into the distributor 40 via each capillary tube 50, joins each other therein, and
flows out of the heat exchanger 1.
[0031] According to the embodiment described above, in the case where the heat exchanger
1 is used as an evaporator, a two-phase refrigerant flow having entered thereinto
is uniformly distributed by the distributor 40, and the uniformly distributed refrigerant
is flowed into each chamber 12 at which the head difference is reduced. Thus, the
effect of the head difference on the refrigerant having flowed into each chamber 12
is reduced, thereby allowing the refrigerant to be uniformly distributed and flowed
into each flattened pipe 20 to suppress a drift. Therefore, use of the refrigerant
distributing device including the distributor 40 and the header 10a allows the capacity
of the evaporator to be maximized to increase the heat exchange efficiency of the
heat exchanger 1 as an evaporator.
[0032] The position of each division plate 11 may be determined in consideration of the
head difference that allows uniform distribution. Provision of only a minimum necessary
number of division plates 11 allows cost reduction.
[0033] In addition, the refrigerant distributing device and the heat exchanger according
to the present invention are not limited to the structure shown in Fig. 1, and various
changes such as (1) to (4) below may be made without departing from the scope of the
present invention.
- (1) A drift suppression member for suppressing a distribution drift, with an orifice
70 as shown in fig. 5, is further provided at a refrigerant inflow portion of each
chamber 12. The orifice 70 is provided at a connection port, at each chamber 12, connected
to the capillary tube 50 and has a through hole 71 with a smaller inner diameter than
that of the capillary tube 50. The orifice 70 further reduces the flow of the refrigerant
having flowed thereinto from the capillary tube 50, by means of the through hole 71,
thereby promoting making the refrigerant into a spray flow. The promotion of making
the refrigerant into a spray flow makes distribution of the refrigerant to each flattened
pipe 20 in the chamber 12 to be more uniform, thereby allowing a distribution drift
to be further suppressed.
- (2) The height (the length in a direction in which the plurality of flattened pipes
20 are disposed in parallel) of each chamber 12 may be determined in accordance with
a wind speed distribution at the heat exchanger 1.
The wind speed of air blown from a fan to the heat exchanger 1 is not necessarily
uniform over the entire surface of the heat exchanger 1, and a wind speed distribution
exists therein. For example, in the case of a multi-air-conditioning apparatus for
a building, since a fan is provided at an upper portion of the heat exchanger 1, the
wind speed is higher at the upper portion of the heat exchanger 1 than at a lower
portion thereof. In the case where the heat exchanger 1 is used as an evaporator,
the refrigerant passing through a portion where the wind speed is high progresses
in gasification further than the refrigerant passing through a portion where the wind
speed is low, and is easily dried. Thus, in the case where the amount of the refrigerant
flowing into each chamber 12 is the same, the refrigerant having passed through the
portion where the wind speed is high has higher quality than that of the refrigerant
having passed through the portion where the wind speed is low, and the state of the
refrigerant flowing into the header 10b is varied.
When the state of the refrigerant is varied as described above, the state of the refrigerant
flowing out of the external connection pipe 14 is not stable. Thus, for a portion
of the header 10a to which the flattened pipes 20 located at the portion where the
wind speed is high are connected, the heights of the chambers 12 are decreased such
that a heat-exchange region per chamber is reduced in size, whereby the number of
flattened pipes connected to the chamber 12 is decreased. This will be specifically
described below with reference to Fig. 6.
Fig. 6 is a diagram illustrating the principle of determining the height of each chamber
in accordance with a wind speed distribution and shows here a case where a wind speed
at the upper side is high and a wind speed at the lower side is low.
As shown in Fig. 6, the height of each chamber 12A at the upper side at which the
wind speed is high is made smaller than the height of each chamber 12B at the lower
side at which the wind speed is low, so that the number of the flattened pipes connected
to each chamber 12A is made smaller than the number of the flattened pipes connected
to each chamber 12B. Thus, a heat-exchange region A at the chamber 12A side is smaller
than a heat-exchange region B at the chamber 12B side, and the heat transfer area
is small, so to speak. Therefore, the substantial heat exchange amount is substantially
the same in the heat-exchange region A and the heat-exchange region B, and it is possible
to make the refrigerant state at an outlet to be uniform.
The case has been described in which the amount of the refrigerant flowing into each
chamber 12 is the same and the refrigerant state at the outlet is made uniform by
changing the heights of the chambers 12. However, the following case may be employed.
Specifically, the height of each chamber 12 is made the same, and the distribution
amount of the refrigerant flowing into each chamber 12 is changed. In this case, the
distribution amount of the refrigerant flowing into each chamber 12 may be determined
in accordance with a wind speed distribution, and the specifications (length, inner
diameter) of each capillary tube 50 may be determined such that the determined distribution
amount is achieved. Specifically, the capillary tubes 50 are selected such that the
distribution amount for each chamber 12 to which the flattened pipes 20 located at
the portion where the wind speed is high are connected is large and the distribution
amount for each chamber 12 to which the flattened pipes 20 at the portion where the
wind speed is low are connected is small.
- (3) In the present embodiment, the case has been described in which the entire heat
exchanger 1 has substantially an I shape. However, the entire heat exchanger 1 may
have substantially an L shape, substantially a U shape, or substantially a rectangular
shape. Which shape the heat exchanger 1 has may be determined in accordance with a
mounting space, within a housing, for the heat exchanger 1 in which the heat exchanger
1 is mounted. The heat exchanger 1 may have a shape that maximizes use of the mounting
space to allow the heat exchanger 1 to be densely mounted.
- (4) In the present embodiment, each heat-transfer pipe is a flattened pipe, but may
not necessarily be a flattened pipe and may be a circular pipe.
Reference Signs List
[0034] 1 heat exchanger 10 header 10a header 10b header 11 division plate 12 chamber 12A
chamber 12B chamber 13 through hole 14 external connection pipe 20 flattened pipe
(heat-transfer pipe) 30 fin 40 distributor 50 capillary tube 60 refrigeration cycle
apparatus 61 compressor 62 condenser 63 expansion valve 64 evaporator 70 orifice 71
through hole A heat-exchange region B heat-exchange region.
1. A refrigerant distributing device comprising:
a header (10a) having a configuration in which the header (10a) is connectable to
one end of each of a plurality of heat-transfer pipes (20) of a heat exchanger (1)
through which a refrigerant flows in parallel to the plurality of heat-transfer pipes
(20) disposed in parallel and an interior of the header (10a) is divided, by one or
more division plates (11), in a parallel direction in which the plurality of heat-transfer
pipes (20) to be disposed, the header (10a) being mounted so as to stand in an up-down
direction;
a plurality of capillary tubes (50) that allow a flow rate of the refrigerant to be
adjusted; and
a distributor (40) configured to distribute the refrigerant to each chamber (12) within
the header (10a) divided by the one or more division plates (11) and flow the refrigerant
into each chamber (12),
wherein the distributor (40) is connected to each of the respective chambers (12)
via one of the plurality of capillary tubes (50),
characterised in that a drift suppression member (70) for suppressing a distribution drift is provided
at a connection port of each chamber (12) with an orifice (70) having a through hole
(71) with a smaller inner diameter than that of the capillary tube (50) provided at
the connection port of the capillary tube (50) in each chamber (12).
2. The refrigerant distributing device of claim 1, wherein a position of the division
plates (11) is set in accordance with a wind speed distribution at the heat exchanger
(1), and the position of the division plates (11) is set such that a length, in the
parallel direction, of the chamber (12) to which the heat-transfer pipes (20) passing
through a portion where a wind speed is high are connectable is shorter than a length,
in the parallel direction, of the chamber (12) to which the heat-transfer pipes (20)
passing through a portion where the wind speed is low are connectable.
3. The refrigerant distributing device of claim 1 or 2, wherein a distribution amount
of the refrigerant flowed into each chamber (12) is set in accordance with a wind
speed distribution at the heat exchanger (1), the plurality of capillary tubes (50)
are selected such that a distribution amount for the chamber (12) to which the heat-transfer
pipes (20) located at a portion where a wind speed is high are connectable is larger
than a distribution amount for the chamber (12) to which the heat-transfer pipes (20)
located at the portion where the wind speed is low are connectable.
4. A heat exchanger (1) comprising the refrigerant distributing device of any one of
claims 1 to 3.
5. The heat exchanger (1) of claim 4, wherein the parallel direction in which the plurality
of heat-transfer pipes (20) are disposed is the up-down direction, the header (10a)
is mounted so as to stand in the up-down direction, and each heat-transfer pipe (20)
is a flattened pipe having a plurality of through holes (20a) that are refrigerant
flow paths.
6. A refrigeration cycle apparatus (60) comprising the heat exchanger (1) of claim 4
or 5.
7. An air-conditioning apparatus comprising the refrigeration cycle apparatus (60) of
claim 6.
1. Kältemittelverteilungseinrichtung, umfassend:
ein Kopfstück (10a), eine Konfiguration aufweisend, in der das Kopfstück (10a) mit
einem Ende jeder einer Vielzahl von Wärmeübertragungsleitungen (20) eines Wärmetauschers
(1), durch die ein Kältemittel parallel zu der Vielzahl von parallel angeordneten
Wärmeübertragungsleitungen (20) strömt, verbindbar ist, und ein Inneres des Kopfstücks
(10a) durch eine oder mehrere Unterteilungsplatten (11) in einer parallelen Richtung,
in der die Vielzahl von Wärmeübertragungsleitungen (20) angeordnet sind, unterteilt
ist, wobei das Kopfstück (10a) so befestigt ist, dass es in einer Aufwärts-Abwärts-Richtung
steht;
eine Vielzahl von Kapillarrohren (50), die es ermöglichen, eine Strömungsrate des
Kältemittels anzupassen; und
einen Verteiler (40), der eingerichtet ist, das Kältemittel an jede Kammer (12) innerhalb
des Kopfstücks (10a), das durch eine oder mehrere Unterteilungsplatten (11) unterteilt
ist, zu verteilen und das Kältemittel in jede Kammer (12) strömen zu lassen,
wobei der Verteiler (40) mit jeder der jeweiligen Kammern (12) über eine der Vielzahl
von Kapillarrohren (50) verbunden ist,
dadurch gekennzeichnet, dass ein Driftunterdrückungselement (70) zum Unterdrücken einer Verteilungsdrift an einer
Verbindungsöffnung jeder Kammer (12) mit einem Durchlass (70) vorgesehen ist, der
ein Durchgangsloch (71) mit einem kleineren Innendurchmesser als der des Kapillarrohrs
(50) aufweist, vorgesehen an der Verbindungsöffnung des Kapillarrohrs (50) in jeder
Kammer (12).
2. Kältemittelverteilungseinrichtung nach Anspruch 1, wobei eine Position der Unterteilungsplatten
(11) entsprechend einer Windgeschwindigkeitsverteilung am Wärmetauscher (1) eingestellt
ist und die Position der Unterteilungsplatten (11) so eingestellt ist, dass in der
parallelen Richtung eine Länge der Kammer (12), mit der die Wärmeübertragungsleitungen
(20), die durch einen Abschnitt mit hoher Windgeschwindigkeit hindurchgehen, verbindbar
sind, kürzer ist als eine Länge in der parallelen Richtung der Kammer (12), mit der
die Wärmeübertragungsleitungen (20), die durch einen Abschnitt mit niedriger Windgeschwindigkeit
hindurchgehen, verbindbar sind.
3. Kältemittelverteilungseinrichtung nach Anspruch 1 oder 2, wobei eine Verteilungsmenge
des in jede Kammer (12) geströmten Kältemittels gemäß einer Windgeschwindigkeitsverteilung
am Wärmetauscher (1) eingestellt ist, wobei die Vielzahl der Kapillarrohre (50) so
ausgewählt sind, dass eine Verteilungsmenge für die Kammer (12), mit der die an einem
Abschnitt mit hoher Windgeschwindigkeit angeordneten Wärmeübertragungsleitungen (20)
verbindbar sind, größer ist als eine Verteilungsmenge für die Kammer (12), mit der
die an dem Abschnitt mit niedriger Windgeschwindigkeit angeordneten Wärmeübertragungsleitungen
(20) verbindbar sind.
4. Wärmetauscher (1), umfassend die Kältemittelverteilungseinrichtung nach einem der
Ansprüche 1 bis 3.
5. Wärmetauscher (1) nach Anspruch 4, wobei die parallele Richtung, in der die Vielzahl
von Wärmeübertragungsleitungen (20) angeordnet sind, die Aufwärts-Abwärts-Richtung
ist, das Kopfstück (10a) so befestigt ist, dass es in der Aufwärts-Abwärts-Richtung
steht, und jede Wärmeübertragungsleitung (20) eine abgeflachte Leitung ist, die eine
Vielzahl von Durchgangslöchern (20a) aufweist, die Kältemittelströmungspfade sind.
6. Kühlkreislaufvorrichtung (60), umfassend den Wärmetauscher (1) nach Anspruch 4 oder
5.
7. Klimaanlage, umfassend die Kühlkreislaufvorrichtung (60) nach Anspruch 6.
1. Distributeur de fluide réfrigérant comprenant :
un collecteur (10a) ayant une configuration dans laquelle le collecteur (10a) peut
être relié à une extrémité de chacun d'une pluralité de conduits de transfert de chaleur
(20) d'un échangeur de chaleur (1) par lequel un fluide réfrigérant circule parallèlement
à la pluralité de conduits de transfert de chaleur (20) disposés en parallèle, et
un intérieur du collecteur (10a) est divisé, par une ou plusieurs plaques de séparation
(11), dans une direction parallèle dans laquelle la pluralité de conduits de transfert
de chaleur (20) est disposée, le collecteur (10a) étant monté de façon à se trouver
dans une direction haut/bas ;
une pluralité de tubes capillaires (50) qui permettent d'ajuster un débit du fluide
réfrigérant ;
et
un distributeur (40) configuré pour distribuer le fluide réfrigérant à chaque chambre
(12) du collecteur (10a) divisé par la ou les plaques de séparation (11) et pour faire
circuler le fluide réfrigérant dans chaque chambre (12),
dans lequel le distributeur (40) est relié à chacune des chambres respectives (12)
via l'un de la pluralité de tubes capillaires (50),
caractérisé en ce qu'un élément de suppression de dérive (70) destiné à supprimer une dérive de distribution
est muni, au niveau d'un point de raccordement de chaque chambre (12), d'un orifice
(70) ayant un trou traversant (71) avec un diamètre intérieur plus petit que celui
du tube capillaire (50) prévu au niveau du point de raccordement du tube capillaire
(50) dans chaque chambre (12).
2. Dispositif de distribution de fluide réfrigérant selon la revendication 1, dans lequel
une position des plaques de séparation (11) est définie selon une répartition de la
vitesse du vent au niveau de l'échangeur de chaleur (1), et la position des plaques
de séparation (11) est définie de sorte qu'une longueur, dans la direction parallèle,
de la chambre (12) à laquelle les conduits de transfert de chaleur (20) qui passent
par une partie au niveau de laquelle une vitesse du vent est élevée peuvent être reliés
soit plus courte qu'une longueur, dans la direction parallèle, de la chambre (12)
à laquelle les conduits de transfert de chaleur (20) qui passent par une partie au
niveau de laquelle la vitesse du vent est faible peuvent être reliés.
3. Dispositif de distribution de fluide réfrigérant selon la revendication 1 ou 2, dans
lequel une quantité de distribution du fluide réfrigérant qui circule dans chaque
chambre (12) est définie selon une répartition de la vitesse du vent au niveau de
l'échangeur de chaleur (1), et la pluralité de tubes capillaires (50) est choisie
de sorte qu'une quantité de distribution pour la chambre (12) à laquelle les conduits
de transfert de chaleur (20) situés au niveau d'une partie au niveau de laquelle la
vitesse du vent est élevée peuvent être reliés soit supérieure à une quantité de distribution
pour la chambre (12) à laquelle les conduits de transfert de chaleur (20) situés au
niveau de la partie au niveau de laquelle la vitesse du vent est faible peuvent être
reliés.
4. Dispositif de distribution de fluide réfrigérant selon l'une quelconque des revendications
1 à 3.
5. Dispositif de distribution de fluide réfrigérant selon la revendication 4, dans lequel
la direction parallèle dans laquelle la pluralité de conduits de transfert de chaleur
(20) est disposée est la direction haut/bas, le collecteur (10a) est monté de façon
à se trouver dans la direction haut/bas, et chaque conduit de transfert de chaleur
(20) est un conduit aplati ayant une pluralité d'orifices traversants (20a) qui sont
des trajets de circulation de fluide réfrigérant.
6. Appareil à cycle de réfrigération (60) comprenant l'échangeur de chaleur (1) selon
la revendication 4 ou 5.
7. Appareil de climatisation comprenant l'appareil à cycle de réfrigération (60) selon
la revendication 6.