[0001] The present invention relates to the domain of the thermal treatment systems adapted
to be received in automotive vehicles. More precisely, the invention relates to heat
exchange units which are part of such thermal treatment systems.
[0002] Traditionally, vehicles comprise at least one thermal treatment system adapted to
thermally treat the propulsion system of the vehicle and/or the passenger compartment
of such vehicle. Such thermal treatment systems usually comprises at least one refrigerant
fluid circuit which comprises at least one heat exchanger adapted to operate a heat
exchange between the refrigerant fluid and an air flow. The refrigerant fluid circuit
can also comprise another heat exchanger adapted to operate a heat exchange between
the air flow and the refrigerant fluid, or between the refrigerant fluid and another
refrigerant fluid. The air flow and/or the other refrigerant fluid can then be used
to thermally treat the propulsion system and/or the passenger compartment.
[0003] Those thermal treatment systems are often arranged in a front part of the vehicle
wherein the available space is limited. As a result, there is a need to reduce as
much as possible the bulk of such thermal treatment system.
[0004] The present invention aims to resolve at least this issue by providing a heat exchange
unit comprising at least two heat exchangers which are part of the same refrigerant
fluid circuit and arranged in order to be the less cumbersome as possible.
[0005] An object of the present invention thus concerns a heat exchange unit for a vehicle,
comprising at least a first heat exchanger adapted to perform a heat exchange between
a refrigerant fluid and an air flow, at least a second heat exchanger adapted to operate
a heat exchange between the refrigerant fluid and the air flow, the first heat exchanger
being arranged downstream of the second heat exchanger along the air flow direction,
the heat exchange unit comprising at least one accumulation device hydraulically connected
to both the first heat exchanger and the second heat exchanger, at least a first connector
and a second connector, the first connector being hydraulically connected to the accumulation
device and to the second connector and the second connector being hydraulically connected
to the first connector and to the second heat exchanger, at least the second connector
being screwed to the first connector. For instance, the first connector can be brazed
on the first heat exchanger and the second connector can be brazed to the second heat
exchanger. In other words, the first connector is formed as a single-piece with, at
least, the first heat exchanger while the second connector is formed as a single-piece
with the second heat exchanger. The second connector being screwed to the first connector,
this second connector and the second heat exchanger can easily be replaced without
damaging the rest of the exchange unit.
[0006] According to the invention, the first connector comprises at least a first channel
and a second channel, the first channel being hydraulically connected to the first
heat exchanger and to the accumulation device and the second channel being hydraulically
connected to the accumulation device and to the second connector. That is to say that
the first channel of the first connector connects an outlet of the first heat exchanger
to an inlet of the accumulation device while the second channel of this first connector
connects an outlet of the accumulation device to an inlet of the second connector.
[0007] According to the invention, the second connector comprises at least one conduit hydraulically
connected on one hand to the second channel of the first connector and on the other
hand to the second heat exchanger. To put it another way, the conduit connects the
second channel of the first connector to an inlet of the second heat exchanger. According
to an embodiment of the invention, this conduit is a unique conduit.
[0008] According to an aspect of the invention, at least one of the connectors is geometrically
interposed between the accumulation device and, at least, the second heat exchanger.
Advantageously, both the first and the second connectors are geometrically interposed
between the accumulation device and, at least, the second heat exchanger. By the words
"geometrically interposed" we here mean that the concerned connector(s) is(are) physically
arranged between the accumulation device and the second heat exchanger. Advantageously,
such an arrangement reduces the global bulk of the heat exchange unit.
[0009] According to the invention, the second connector may comprise a connecting plug adapted
to be received in an orifice arranged in the first connector. Especially, the connecting
plug is adapted to be received in an orifice which comes out on the second channel
of the first connector. If so, the connecting plug is connected to the second channel
arranged in the first connector, that is to say that the connecting plug connects
the second channel of the first connector to the conduit of the second connector.
[0010] Advantageously, the first heat exchanger is arranged upstream of the second heat
exchanger along a direction of circulation of the refrigerant fluid. To put it another
way, the refrigerant fluid that reaches the second heat exchanger has already been
subjected to a heat exchange with the air flow within the first heat exchanger. Arranging
the first heat exchanger upstream the second heat exchanger along the direction of
circulation of the refrigerant fluid but downstream said second heat exchanger along
the air flow direction advantageously results in a maximisation of the temperature
difference between the refrigerant fluid and the air flow with which the heat exchange
is performed, and, thus in an optimization of such heat exchange. According to an
embodiment of the invention, the refrigerant fluid thus reaches the first heat exchanger
in a gaseous state, exits it in a liquid state and is then subcooled in the second
heat exchanger. Advantageously, the efficiency if the refrigerant fluid circuit which
comprises the heat exchange unit of the invention is therefore globally improved.
[0011] According to an aspect of the invention, the first heat exchanger mainly extends
in a first plan, the second heat exchanger mainly extends in a second plan, the first
plan and the second plan being parallel to each other.
[0012] According to the invention, the first heat exchanger and the second heat exchanger
each comprises at least one heat exchange area, at least one entry manifold adapted
to distribute the refrigerant fluid in the heat exchange area and at least one exit
manifold adapted to collect the refrigerant fluid that leaves said heat exchange area,
the entry manifolds and the exit manifolds of the heat exchangers each extending along
a main axis perpendicular to a direction of circulation of the refrigerant fluid in
the heat exchange areas. According to an embodiment of the invention, the first heat
exchanger's exit manifold and the second heat exchanger's entry manifold can be arranged
on a same side of the heat exchange unit. According to this embodiment, the first
heat exchanger's entry manifold and the second heat exchanger's exit manifold are
advantageously arranged on an opposite side of the heat exchange unit.
[0013] For example, the accumulation device can be arranged on the same side of the heat
exchange unit than the first heat exchanger's exit manifold and the second heat exchanger's
entry manifold. The accumulation device advantageously extends along a main direction
parallel to the main axis of extension of the first heat exchanger's exit manifold.
The main direction of extension of the accumulation device can also be parallel to
a main axis of extension of the second heat exchanger's entry manifolds and perpendicular
to the direction of circulation of the refrigerant fluid in the heat exchange areas.
[0014] Optionally, the accumulation device can extend all along a dimension of the first
heat exchanger measured between two ends of this first heat exchanger, along the main
axis of extension of the first heat exchanger's entry manifold.
[0015] According to an embodiment of the invention, the second heat exchanger presents a
smaller height than the first heat exchanger, such heights being measured along a
direction included in a main plan of extension of the first heat exchanger and perpendicular
to the main direction of circulation of the refrigerant fluid in the first heat exchanger's
heat exchange area.. Advantageously, such an arrangement virtually divides the first
heat exchanger, and especially the heat exchanger area of this first heat exchanger,
in an upper part adapted to be crossed by a first air flow and a lower part adapted
to be crossed by a second air flow which also crosses the second heat exchanger. As
mentioned earlier, the second air flow crosses the second heat exchanger before crossing
the lower part of the first heat exchanger.
[0016] The present invention also relates to a thermal treatment system for a vehicle, comprising
at least one refrigerant fluid circuit carrying at least the heat exchange unit such
as the one mentioned above, and at least one circulation device adapted to circulate
the refrigerant fluid.
[0017] According to an aspect of the invention, the refrigerant fluid is adapted to carry
and exchange heat by changing its state. According to this aspect of the invention,
the circulation device is a compression device and the refrigerant fluid circuit also
comprises at least one expansion device, that is to say a device adapted to reduce
the pressure of the refrigerant fluid which goes through it.
[0018] Other features and advantages of the invention are to be described in the detailed
description of the invention given hereunder in relation with different views of the
invention illustrated on the following figures:
[Fig. 1] is a schematic view of a thermal treatment system according to the invention,
such thermal treatment system comprising at least one heat exchange unit according
to the invention ;
[Fig. 2] is a perspective view of a first heat exchanger of a heat exchange unit according
to the invention ;
[Fig. 3] is a cross-section view of a first connector and a second connector of the
heat exchange unit according to the invention, the first connector and the second
connector being hydraulically connected to each other ;
[Fig. 4] illustrates a perspective view of one connector of the heat exchange unit
according to the invention which participate to hydraulically connect the first heat
exchanger to the second heat exchanger.
[0019] In the following specification, the orientations given are related to the orientation
of a heat exchange unit 200 according to the invention. On the figures, an L, V, T
coordinate system is illustrated in which a longitudinal direction is parallel to
a longitudinal axis L, a vertical direction is parallel to a vertical axis V and a
transversal direction is parallel to a transversal axis T. According to the examples
given, the longitudinal axis L is perpendicular to both the vertical axis V ant to
the transversal axis T, the vertical axis V is perpendicular to both the longitudinal
axis L and to the transversal axis T and the transversal axis T is perpendicular to
both the longitudinal axis L and to the vertical axis V. For instance, once the heat
exchange unit 200 of the invention is implemented in a vehicle, the vertical axis
V corresponds to a direction perpendicular to the road on which such vehicle is adapted
to run.
[0020] Figure 1 illustrates, schematically, a thermal treatment system 100 according to
the invention. As shown, such thermal treatment system 100 comprises at least one
refrigerant fluid circuit 110 which carries at least one heat exchange unit 200 according
to the invention, at least one circulation device 111 adapted to circulates the refrigerant
fluid and at least one evaporator 112. According to the illustrated example, a refrigerant
fluid RF is adapted to carry and to exchange heat by changing its state. For instance,
the refrigerant fluid RF can be chosen among 1234YF, R134a or CO2.
[0021] As a result, the circulation device 111 adapted to circulate the refrigerant fluid
is a compression device and the refrigerant fluid circuit 110 also comprises at least
one expansion device 113. The compression device 111 is adapted to compress the refrigerant
fluid RF before it reaches the heat exchange unit 200. Within the heat exchanger unit
200, the refrigerant fluid RF is adapted to exchange heat with an air flow AF which,
as schematically illustrated, crosses the heat exchange unit 200. According to the
illustrated embodiment, the heat exchange unit 200 works as a condenser with respect
to the refrigerant fluid, that is to say that the refrigerant fluid is cooled and
liquified by passing through such heat exchange unit. In other words, the refrigerant
fluid is adapted to give calories to the air flow AF which crosses said heat exchange
unit 200. The cooled refrigerant fluid can then be used to thermally treat another
part of the vehicle, such as the passenger compartment or the propulsion system of
the vehicle.
[0022] The refrigerant fluid RF thus exits the heat exchange unit 200 in a liquid state
and goes through the expansion device 112 in which its pressure is reduced. The cooled
liquid refrigerant fluid RF then reaches the evaporator 112 in which its temperature
is raised until the refrigerant fluid evaporates. The refrigerant fluid RF exits the
evaporator 112 in a gaseous state and then reaches again the compression device 111
to start a new thermodynamic cycle. The evaporator 112 can be adapted to perform a
heat exchange between the refrigerant fluid and an air flow or between the refrigerant
fluid and another fluid without departing from the scope of the invention.
[0023] It is understood that this is only an example of carrying the invention which does
not restrict it. For instance, the heat exchange unit according to the invention can
be used as an evaporator.
[0024] The heat exchange unit 200 according to the invention can for instance be arranged
in a front part of a vehicle and the air flow AF which crosses it can be generated
by the movement of the vehicle which carries such heat exchange unit 200. Alternately,
or additionally, the thermal treatment system 100 of the invention can comprise at
least one ventilation device adapted to generate the air flow, for instance when the
vehicle is stopped or in dense traffic.
[0025] Figure 2 is a perspective view of the heat exchange unit 200 adapted to be crossed
by the air flow AF. As shown, the heat exchange unit 200 comprises at least a first
heat exchanger 210, at least a second heat exchanger 220 and at least one accumulation
device 230. Especially, the air flow AF is adapted to cross both the first heat exchanger
210 and the second heat exchanger 220.
[0026] The first heat exchanger 210 and the second heat exchanger 220 have similar shapes.
First of all, the first heat exchanger 210 mainly extends in a first plan PI and the
second heat exchanger 220 mainly extends in a second plan P2 parallel to the first
plan PI. According to the orientation given on the figures, the first plan PI and
the second plan P2 are both vertical and longitudinal plans, that is to say plans
in which the vertical axis V and the longitudinal axis L extend.
[0027] Each of these heat exchangers 210, 220 comprises at least one heat exchange area
211, 221 wherein the heat exchange between the refrigerant fluid and the air flow
AF is performed, and at least one manifold 212, 222 adapted to distribute and/or to
collect the refrigerant fluid in and from the respective heat exchange areas 211,
221. According to the illustrated embodiment, each heat exchanger 210, 220 comprises
two manifolds 212, 222, among which one entry manifold 212a, 222a adapted to distribute
the refrigerant fluid in the heat exchange areas 211, 221 and one exit manifold 212b,
222b adapted to collect the refrigerant fluid from those heat exchange areas 211,
221 once the heat exchange has been performed. According to this embodiment, each
of the manifolds 212, 222 extends along a main axis A, A' parallel to the vertical
axis V and the manifolds 212, 222 of one of the heat exchangers 210, 220 are arranged
at two sides of the concerned heat exchanger 210, 220 opposed to one another along
the longitudinal axis L. Especially, the first heat exchanger's exit manifold 212b
and the second heat exchanger's entry manifold 222a extend parallel to a main axis
A while the first heat exchanger's entry manifold 212a and the second heat exchanger's
exit manifold 222b extend parallel to another main axis A'. According to the illustrated
embodiment, the main axis A and the other main axis A' are parallel to each other.
In other words, the manifolds 212, 222 extend perpendicularly to a main direction
of circulation of the refrigerant fluid along the heat exchange areas 211, 221. Advantageously,
the air flow AF also circulates perpendicularly to a main plan of circulation of the
refrigerant fluid along the heat exchange areas 211, 221.
[0028] The first heat exchanger 210 presents a greater height than the second heat exchanger
220. The "height" of a heat exchanger 210, 220 is a dimension measured along the vertical
axis V, between two ends of the concerned heat exchanger, opposed along such vertical
axis V. As a consequence, the air flow AF can be virtually separated in a first air
flow AF1 which crosses only an upper part 213 of the first heat exchanger 210 and
in a second air flow AF2 which crosses a lower part 214 of the first heat exchanger
210 and the entire heat exchange are 221 of the second heat exchanger 220. The first
air flow AF1 thus exchanges heat only with the refrigerant fluid circulating in the
upper part 213 of the first heat exchanger 210 while the second air flow AF2 exchanges
heat with the refrigerant fluid that circulates in the lower part 214 of the first
heat exchanger 210 and with the refrigerant fluid which circulates in the second heat
exchanger 220.
[0029] According to the illustrated embodiment, the second heat exchanger 220 is arranged
upstream of the first heat exchanger 210 along the air flow AF, AF1, AF2 direction,
and especially along the second air flow AF2 direction. As a result, the second air
flow AF2 presents a cooler temperature when it enters the second heat exchanger 220
than when it enters the lower part 214 of the first heat exchanger 210.
[0030] Advantageously, the first heat exchanger 210 is arranged upstream of the second heat
exchanger 220 along a direction of circulation of the refrigerant fluid in the heat
exchange areas 211, 221. In other words, the refrigerant fluid enters the heat exchange
unit 200 through the first heat exchanger's entry manifold 212a, circulates along
the first heat exchanger's heat exchange area 211 until it reaches the first heat
exchanger's exit manifold 212b. As detailed below the first heat exchanger's exit
manifold 212b is hydraulically connected to the second heat exchanger's entry manifold
222a thanks to, at least, the accumulation device 230. The refrigerant fluid exiting
the first heat exchanger's exit manifold 212b thus reaches the second heat exchanger's
entry manifold 222a, then circulates along the second heat exchanger's heat exchange
area 221 and finally reaches the second heat exchanger's exit manifold 222b. It is
thus understood that the first heat exchanger's entry manifold 212a and the second
heat exchanger's exit manifold 222b are both hydraulically connected to the refrigerant
fluid circuit of the thermal treatment system earlier described.
[0031] As a result, the refrigerant fluid which circulates in the first heat exchanger 210
is warmer than the refrigerant fluid which circulates in the second heat exchanger
220. Advantageously, such an arrangement permits to maximise the temperature difference
between the refrigerant fluid which circulates in the heat exchange areas 211, 221
and the air flow which crosses such heat exchange areas 211, 221, and especially between
the second air flow AF2 and the refrigerant fluid which circulates in the lower part
214 of the first heat exchanger 210.
[0032] Especially, the refrigerant fluid enters the first heat exchanger's entry manifold
212a in a gaseous state and at high pressure. The refrigerant fluid then circulates
along the first heat exchanger's heat exchange area 211 wherein it exchanges heat
with the airflow AF. More particularly, the gaseous refrigerant fluid first circulates
in the upper part 213 of the first heat exchanger 210 wherein it exchanges heat with
the first airflow AF1, then it reaches the lower part 214 of the first heat exchanger
210 wherein it exchanges heat with the second airflow AF2. As a result of the heat
exchange operated within the upper part 21 of the first heat exchanger 210, the refrigerant
fluid may reach the lower part 214 of the first heat exchanger 210 in a biphasic state.
Advantageously, the refrigerant fluid finishes its condensation within the lower part
214 of the first heat exchanger 210, that is to say by exchanging heat with the second
airflow AF2 in order to be in a liquid state when it reaches the second heat exchanger
220. In this second heat exchanger 220, the refrigerant fluid keeps exchanging heat
with the second air flow AF2. As mentioned earlier, the second heat exchanger 220
is arranged upstream the first heat exchanger 210 along the main direction of circulation
of the air flow AF, and particularly along the direction of circulation of the second
air flow AF2. As a consequence, the heat exchange between the refrigerant fluid which
circulates in the second heat exchanger 220 results in a subcooling of the refrigerant
fluid. Especially, the second heat exchanger 220 of heat exchange unit 200 according
to the invention is adapted to make the refrigerant fluid's temperature drop under
its liquefaction temperature. Advantageously, such subcooling permits to improve the
global efficiency of the refrigerant fluid circuit which comprises the heat exchange
unit 200 of the invention. Between the first heat exchanger 210 and the second heat
exchanger 220, the refrigerant fluid is temporarily stocked in the accumulation device
230. Advantageously, this accumulation device 230 is adapted to contain the circulating
refrigerant fluid in order to compensate the refrigerant fluid leaks which are unavoidable
during the vehicle's life cycle.
[0033] As illustrated, this accumulation device 230 extends along a main direction Y parallel
to the vertical axis V, that is to say parallel to the main axis of extension A, A'
of the manifolds of both the first heat exchanger 210 and the second heat exchanger
220. This accumulation device 230 is hydraulically connected to the first heat exchanger
210, and particularly to the exit manifold 212b of this first heat exchanger 210,
and to the second heat exchanger 220, and particularly to the entry manifold 222a
of this second heat exchanger 220.
[0034] According to the invention, a first connector 240 hydraulically connects the first
heat exchanger's exit manifold 212b to the accumulation device 230 and a second connector
250 hydraulically connects the first connector 240 to the second heat exchanger's
entry manifold 222a.
[0035] According the illustrated embodiment of the invention, the first connector 240 can
be brazed on the heat exchange unit 200, and especially to, at least, the first heat
exchanger's exit manifold 212b, while the second connector 250 is brazed only to the
second heat exchanger's entry manifold 222a and screwed to the first connector 240.
Advantageously, when needed, the second connector 250 and the second heat exchanger
220 can be replaced without having to also replace the rest of the heat exchange unit
200.
[0036] As schematically represented on figure 2, the first connector 240 comprises at least
a first channel 241 and at least a second channel 242. Those channels 241, 242 are
schematically represented in dotted lines. As shown, the first channel 241 is hydraulically
connected to the first heat exchanger's exit manifold 212b on one hand and to the
accumulation device 230 on the other hand while the second channel 242 is hydraulically
connected to the accumulation device 230 on one hand and to the second connector 250
on the other hand. In other words, the first channel 241 is connected to an inlet
of the accumulation device 230 while the second channel 242 is connected to an outlet
of this accumulation device 230.
[0037] The second connector 250 comprises one conduit 251, especially a single conduit 251,
also represented with dotted lines on figure 2. As illustrated, this conduit 251 is
hydraulically connected to the second channel 242 of the first connector 240 and to
the second heat exchanger's entry manifold 222a.
[0038] As shown, the accumulation device 230 is arranged on a side of the heat exchangers
210, 220 and extends parallel to the vertical axis V of the illustrated coordinate
system. Particularly, the accumulation device 230 extends on the same side of the
heat exchangers 210, 220 than the first heat exchanger's exit manifold 212b and the
second heat exchanger's entry manifold 222a. Advantageously, the second channel 242
of the first connector 240 is connected to a lower part 231 of the accumulation device
230, that is to say to a part of this accumulation device 230 which faces the second
heat exchanger 220. Once mounted on the intended vehicle, the second heat exchanger
220 is closer to the road on which said vehicle runs than the first heat exchanger
210. In other words, the invention uses the gravity to ensure that the second channel
242 of the first connector 240 is always arranged under the level of refrigerant fluid
in a liquid state contained in the accumulation device 230. Advantageously, this arrangement
ensures the continuous supplying of the second heat exchanger 220 with refrigerant
fluid in a liquid state.
[0039] The channels 241, 242 and the conduit 251 are for instance also represented on figure
3 which is a cross-section view of the first connector 240 and the second connector
250, this cross-section view being realized thanks to a vertical and transversal plan,
that is to say a plan in which both the vertical axis V and the transversal axis T
are included.
[0040] As illustrated on figure 3, the second connector 250 is screwed to the first connector
240. In order to screw these connectors 240, 250, at least one hole 243, 257 is arranged
in both the first connector 240 and the second connector 250, each of those holes
243, 257 being adapted to receive one screw 260. In other words, the hole 243 arranged
in the first connector 243 and the hole 257 arranged in the second connector 257 face
each other and receive the same screw 260 once the connectors 240, 250 are assembled.
As shown, the hole 243 arranged in the first connector 240 is a blind hole while the
hole 257 arranged in the second connector 250 traverses said second connector 250.
[0041] As illustrated, the second connector 250 also comprises at least one connecting plug
258 which at least partially extends in an orifice 244 arranged in the first connector
240. Especially, this connecting plug 258 extends parallel to the transversal axis
T and comes out on the second channel 242 of the first connector 240 on one hand and
on the conduit 251 of the second connector 250 on another hand. To put it another
way, this connecting plug 258 hydraulically connects the first connector 240 to the
second connector 250 by connecting the first connector's second channel 242 to the
second connector's conduit 251.
[0042] Now referring to figure 4, we are going to describe the second connector 250 which
is adapted to be screwed on the first connector 240.
[0043] As illustrated, the second connector 250 has a general parallelepipedic shape, thus
comprising at least one front face 252, one rear face 253 linked together thanks to
one first side face 254 and one second side face 255. At least one cut 256 is formed
in the front face 252 in such a way that second connector 250 presents an upper part
250a and a lower part 250b, the upper part 250a presenting a width w1 smaller than
a width w2 of the lower part 250b. Those width w1, w2 are both measured along the
transversal axis T, between the front face 252 and the rear face 253 of the second
connector 250.
[0044] As earlier described, a hole 257 adapted to receive the screw is arranged in the
second connector 250. Especially, this through-hole 257 is arranged in the upper part
250a of the second connector 250, and the cut 256 is advantageously adapted to receive
the screw head.
[0045] The rear face 253 of this second connector 250 carries the connecting plug 258 adapted
to be received in the orifice formed in the first connector. According to the illustrated
embodiment, the connecting plug 258 extends parallel to the transversal axis T but
it is understood that it is only an example of how to execute the invention and that
this connecting plug 258 could present another orientation without departing from
the scope of the invention.
[0046] This connecting plug 258 is thus connected to the second channel of the first connector
on one hand and to the conduit previously described on the other hand. Although it
is not shown on figure 4, this conduit comes out on the second side face 255 of the
second connector 250. As partially illustrated, this second side face 255 comprises
at least one rail 255a adapted to encompass the second heat exchanger's entry manifold,
said second side face 255 being in contact with said second heat exchanger's entry
manifold.
[0047] The present invention therefore provides a new architecture of a heat exchange unit
adapted to be received in a front part of a vehicle, such heat exchange unit being
less bulky than the heat exchange units known from prior art.
[0048] However, the invention cannot be limited to the means and configurations described
and illustrated herein, and it also extends to any equivalent means or configurations
and to any technically operative combination of such means. In particular, the shape
and arrangement of the connectors and of the heat exchangers can be modified insofar
as they fulfil the functionalities described in the present document.
1. Heat exchange unit (200) for a vehicle, comprising at least a first heat exchanger
(210) adapted to perform a heat exchange between a refrigerant fluid (RF) and an air
flow (AF, AF1, AF2), at least a second heat exchanger (220) adapted to operate a heat
exchange between the refrigerant fluid (RF) and the air flow (AF, AF1, AF2), the first
heat exchanger (210) being arranged downstream of the second heat exchanger (220)
along the air flow (AF, AF1, AF2) direction, the heat exchange unit (200) comprising
at least one accumulation device (230) hydraulically connected to both the first heat
exchanger (210) and the second heat exchanger (220), at least a first connector (240)
and a second connector (250), the first connector (240) being hydraulically connected
to the accumulation device (230) and to the second connector (250) and the second
connector (250) being hydraulically connected to the first connector (240) and to
the second heat exchanger (220), at least the second connector (250) being screwed
to the first connector (240).
2. Heat exchange unit (200) according to the preceding claim, wherein the first connector
(240) comprises at least a first channel (241) and a second channel (242), the first
channel (241) being hydraulically connected to the first heat exchanger (210) and
to the accumulation device (230) and the second channel (242) being hydraulically
connected to the accumulation device (230) and to the second connector (250).
3. Heat exchange unit (200) according to the preceding claim, wherein the second connector
(250) comprises at least one conduit (251) hydraulically connected on one hand to
the second channel (242) of the first connector (240), and on the other hand to the
second heat exchanger (220).
4. Heat exchange unit (200) according to any of the preceding claims, wherein at least
one of the connectors (240, 250) is geometrically interposed between the accumulation
device (230) and, at least, the second heat exchanger (220).
5. Heat exchange unit (200) according to any of the preceding claims, wherein the second
connector (250) comprises a connecting plug (258) adapted to be received in an orifice
(244) arranged in the first connector (240).
6. Heat exchange unit (200) according to any of the preceding claims, wherein the first
heat exchanger (210) is arranged upstream of the second heat exchanger (220) along
a direction of circulation of the refrigerant fluid (RF).
7. Heat exchange unit (200) according to any of the preceding claims, wherein the first
heat exchanger (210) mainly extend in a first plan (P1), wherein the second heat exchanger
(220) mainly extends in a second plan (P2) and wherein the first plan (P1) and the
second plan (P2) are parallel to each other.
8. Heat exchange unit (200) according to any of the preceding claims, wherein the first
heat exchanger (210) and the second heat exchanger (220) each comprises at least one
heat exchange area (211, 221), at least one entry manifold (212a, 222a) adapted to
distribute the refrigerant fluid (RF) in the heat exchange area (211, 221) and at
least one exit manifold (212b, 222b) adapted to collect the refrigerant fluid (RF)
that leaves said heat exchange area (211, 221), wherein the entry manifolds (212a,
222a) and the exit manifolds (212b, 222b) of the heat exchangers (210, 220) each extends
along a main axis (A, A') perpendicular to a direction of circulation of the refrigerant
fluid (RF) in the heat exchange areas (211, 221).
9. Heat exchange unit (200) according to the preceding claim, wherein the first heat
exchanger's exit manifold (212b) and the second heat exchanger's entry manifold (222a)
are arranged on a same side of the heat exchange unit (200).
10. Heat exchange unit (200) according to the preceding claim, wherein the accumulation
device (230) is arranged on the same side of the heat exchange unit (200) than the
first heat exchanger's exit manifold (212b) and the second heat exchanger's entry
manifold (222a).
11. Heat exchange unit (200) according to any of claims 8 to 10, wherein the accumulation
device (230) extends along a main direction (Y) parallel to the main axis (A) of extension
of the first heat exchanger's exit manifold (212b).
12. Heat exchange unit (200) according to the preceding claim, wherein the accumulation
device (230) extends all along a dimension of the first heat exchanger (210) measured
between two ends of this first heat exchanger (210), along the main axis (A) of extension
of the first heat exchanger's exit manifold (212b).
13. Heat exchange unit (200) according to any of claims 8 to 12, wherein the second heat
exchanger (220) presents a smaller height than the first heat exchanger (210), such
heights being measured along a direction included in a main plan (P1) of extension
of the first heat exchanger (210) and perpendicular to the main direction of circulation
of the refrigerant fluid (RF) in the first heat exchanger's heat exchange area (211).
14. Thermal treatment system (100) for a vehicle, comprising at least one refrigerant
fluid circuit (110) carrying at least the heat exchange unit (200) according to any
of the preceding claims, and at least one circulation device (111) adapted to circulate
the refrigerant fluid (RF).