U.S. patent application number 12/644613 was filed with the patent office on 2010-06-24 for combined device including an internal heat exchanger and an accumulator.
Invention is credited to Christophe DENOUAL, Jimmy LEMEE, Alain POURMARIN.
Application Number | 20100155012 12/644613 |
Document ID | / |
Family ID | 40810569 |
Filed Date | 2010-06-24 |
United States Patent
Application |
20100155012 |
Kind Code |
A1 |
LEMEE; Jimmy ; et
al. |
June 24, 2010 |
Combined Device Including An Internal Heat Exchanger And An
Accumulator
Abstract
The invention relates to a combined device 1 that includes a
chamber 2 housing at least one heat exchanger 9 and accumulation
area 11, the chamber 2 extends on a central axis A and the heat
exchanger 9 extends according a secondary central axis B, wherein
the central axis A is offset from the secondary central axis B.
Inventors: |
LEMEE; Jimmy; (Saint Jean
D'Asse, FR) ; DENOUAL; Christophe; (Noyen Sur Sarthe,
FR) ; POURMARIN; Alain; (La Suze Sur Sarthe,
FR) |
Correspondence
Address: |
HOWARD & HOWARD ATTORNEYS PLLC
450 West Fourth Street
Royal Oak
MI
48067
US
|
Family ID: |
40810569 |
Appl. No.: |
12/644613 |
Filed: |
December 22, 2009 |
Current U.S.
Class: |
165/10 ;
165/177 |
Current CPC
Class: |
F25B 40/00 20130101;
F28D 7/0033 20130101; F28F 1/022 20130101; F25B 43/006 20130101;
F28D 7/04 20130101 |
Class at
Publication: |
165/10 ;
165/177 |
International
Class: |
F28D 19/00 20060101
F28D019/00; F28F 1/02 20060101 F28F001/02 |
Foreign Application Data
Date |
Code |
Application Number |
Dec 22, 2008 |
FR |
FR08/07422 |
Claims
1. A combined device (1) including a chamber (2) housing at least
one heat exchanger (9) and an accumulation area (11), in which the
chamber (2) extends according to a primary central axis (A) and the
heat exchanger (9) extends according to a secondary central axis
(B), characterized in that the primary central axis (A) is offset
with respect to the secondary central axis (B).
2. A combined device according to claim 1, in which the offset (d)
between the primary central axis (A) and the secondary central axis
(B) is between one and twenty-five millimeters.
3. A combined device according to claim 1, in which the chamber (2)
and the heat exchanger (9) have a cylindrical shape.
4. A combined device according to claim 1, in which the heat
exchanger (9) includes at least one first flat tube (22) wound on
itself about the secondary central axis (B).
5. A combined device according to claim 4, in which the first flat
tube (22) includes a plurality of channels (23).
6. A combined device according to claim 4, in which the heat
exchanger (9) includes an intake chamber (24) that extends to the
center of the first flat tube (22) wound on itself.
7. A combined device according to claim 1, including a discharge
chamber (25) located at least partially around the heat exchanger
(9), wherein the discharge chamber (25) is at least delimited by an
external wall of the heat exchanger (9) and by an internal wall
(19) of the chamber (2).
8. A combined device according to claim 6, in which the heat
exchanger includes a first circulation path delimited by the
plurality of channels (23) of the first flat tube (22), wherein the
first circulation path is in communication via a first end of the
flat tube (22) with the intake chamber (24) and in communication
with the discharge chamber (25) by means of a second end of the
first flat tube (22).
9. A combined device according to claim 8, in which the first
circulation path is delimited by a second flat tube (26) wound with
the first flat tube (22).
10. A combined device according to claim 3, in which the heat
exchanger (9) includes a second circulation path delimited by a
plurality of channels (23) of a third flat tube (27) wound with the
first flat tube (22).
11. A combined device according to claim 10, characterized in that
the second circulation path is, on the one hand, in communication
with a first channel (12) placed at the periphery of the heat
exchanger (9) and, on the other hand, in communication with a
second channel (13) of which the axis is aligned with the secondary
central axis (B).
12. A combined device according to claim 11, in which the first
flat tube (22) and the second flat tube (26), the third flat tube
(27), the first channel (12) and the second channel (13) form a
unitary assembly.
13. A combined device according to claim 1, in which the chamber
(2) is closed by an upper partition (3) and a lower partition (4)
and the accumulation area (11) comprises a lower wall (20) arranged
at the border between the heat exchanger (9) and said accumulation
area (11).
14. A combined device according to claim 13, including a first
conduit (14) that passes through the upper partition (3) and leads
into a separation area (10) located in the chamber (2) and above
the accumulation area (11).
15. A combined device according to claim 13, including a second
conduit (15) that passes through the lower partition (4).
16. An air conditioning loop incorporating a combined device
according to claim 1.
17. A combined device according to claim 7, in which the chamber
(2) is closed by an upper partition (3) and a lower partition (4)
and the accumulation area (11) comprises a lower wall (20) arranged
at the border between the heat exchanger (9) and said accumulation
area (11).
18. A combined device according to claim 17, including a second
conduit (15) that passes through the lower partition (4) and leads
into the discharge chamber (25).
Description
[0001] This invention relates to the field of air conditioning
loops cooperating with a heating, ventilation and/or air
conditioning system of a motor vehicle. It relates to a combined
device associating an internal heat exchanger with an accumulator
involved in such a loop. It also relates to an air conditioning
loop including such a combined device.
[0002] Motor vehicles are commonly equipped with a heating,
ventilation and/or air conditioning system in order to regulate the
aerothermal parameters of the air contained in the vehicle
interior. Such a system cooperates with an air conditioning loop in
order to cool the air flow before it is discharged from the casing
to the vehicle interior. Said loop includes a plurality of elements
in which a coolant, such as a supercritical fluid, in particular
carbon dioxide known as R744, circulates. These elements include at
least one compressor, a gas cooler, an internal heat exchanger, an
expansion member, an evaporator and an accumulator.
[0003] The coolant circulates from the compressor to the gas
cooler, then through a "high-pressure" branch of the internal heat
exchanger, then to the expansion member, then through the
evaporator, then to the accumulator, and finally through a
"low-pressure" branch of the internal heat exchanger, in order to
return to the compressor.
[0004] The compressor is intended to receive the coolant in the
gaseous state and to compress it in order to bring it to high
pressure. The gas cooler is capable of cooling the compressed
coolant, at a relatively constant pressure, by transferring the
heat to the environment. The expansion member is capable of
reducing the pressure of the coolant leaving the gas cooler by
bringing it at least partially to the liquid state. The evaporator
is suitable for converting the coolant from the gaseous state to
the liquid state coming from the expansion member, at a relatively
constant pressure, by drawing heat in said air flow passing through
the evaporator. The vaporized coolant is then suctioned by the
compressor. These arrangements are such that the coolant is at high
pressure inside the "high-pressure" branch of the internal heat
exchanger while it is at low pressure inside the "low-pressure"
branch of the internal heat exchanger.
[0005] The air conditioning loop includes a "high-pressure" line
that begins at the outlet of the compressor and ends at the inlet
of the expansion member, according to a direction of circulation of
the coolant inside the air conditioning loop, in which the gas
cooler and the "high-pressure" branch of the heat exchanger are
inserted between these two points.
[0006] The air conditioning loop also includes a "low-pressure"
line that beings at the outlet of the expansion member and ends at
the inlet of the compressor, according to the direction of
circulation of the coolant inside the air conditioning loop, in
which the evaporator, the accumulator and the "low-pressure" branch
of the heat exchanger are inserted between these two points.
[0007] The accumulator performs a function of separation between a
gaseous phase and a liquid phase of the coolant. To this end, the
accumulator comprises a separation area dedicated to this function.
The accumulator also performs a function of storing a circulating
load of coolant according to the conditions of use of the air
conditioning loop. For this, the accumulator comprises an area for
accumulation of the coolant in liquid state, which the accumulation
area collects from the evaporator. In general, the accumulator
consists of a chamber housing the separation area and the
accumulation area, and the chamber includes a lower wall that
delimits the accumulation area in the bottom portion of the
chamber. Thus, the coolant in liquid state coming from the
evaporator separates into a gaseous phase and a liquid phase, the
latter of which accumulates by gravity above the lower partition,
inside the accumulation area.
[0008] The heat exchanger is called an internal or exchanger or an
internal heat exchanger because it is configured so that the
coolant circulating inside the "high-pressure" branch can transfer
heat to the coolant circulating inside the "low-pressure" branch.
It is therefore understood that the exchange occurs between the
same fluid circulating in different locations of the air
conditioning loop, without an exchange with air, for example.
[0009] Document JP10019421 (NIPPON SOKEN; DENSO CORP) proposes
combining the internal heat exchanger and the accumulator in a
combined device. In general, the latter includes said chamber,
which is equipped with an opening closed by a lid. The chamber
houses the internal heat exchanger, which hangs over the
accumulation area for the coolant in the liquid state in the
position of use of the combined device on the air conditioning
loop.
[0010] The high-pressure coolant coming from the gas cooler
penetrates the interior of the combined device by means of a
"high-pressure" inlet, provided through the chamber in order to
circulate inside the internal heat exchanger and finally be
discharged from the combined device by means of a "high-pressure"
outlet also provided through the chamber.
[0011] The low-pressure coolant coming from the evaporator
penetrates the inside of the combined device by means of a
"low-pressure" inlet, also provided through the chamber. The
low-pressure coolant in the liquid state tends to accumulate by
gravity above the lower wall of the chamber, while the low-pressure
coolant in the gaseous state tends to concentrate in an upper area
of the chamber. The latter houses a bent U-shaped conduit, of which
a first end is arranged in the upper portion of the chamber in
order to admit, into the conduit, the low-pressure coolant in the
gaseous state, and carry it to a second end of the conduit
communicating with the internal heat exchanger. Inside the latter,
the high-pressure coolant transfers heat to the low-pressure
coolant. The low-pressure coolant in the gaseous state is
discharged from the internal heat exchanger and from the combined
device through a "low-pressure" outlet, also provided through a
wall of the chamber.
[0012] However, this combined device according to the prior art has
major disadvantages.
[0013] Indeed, said document JP 10019421 does not take into account
the integration of such a combined device in an engine compartment
of a vehicle. It appears to be restrictive, with regard to the
arrangement of the air conditioning loop, for the "high-pressure"
and "low-pressure" coolant inlets and outlets to all be provided on
the same side, i.e. through the top portion of the chamber.
Moreover, the integration of the device in the vehicle requires
technical solutions to be found so as to minimize the space used by
the component in question.
[0014] The objective of this invention is therefore to solve the
above-mentioned disadvantages primarily by inventively arranging
the heat exchanger in the chamber of the accumulator. To do this,
the heat exchanger is off-centered with respect to the chamber so
as to minimize the external dimensions of the combined device. This
arrangement enables a discharge chamber to be created laterally
with respect to the exchanger without the obligation of increasing
the diameter of the chamber, or extending the chamber in order to
create a discharge chamber under the heat exchanger.
[0015] The invention therefore relates to a combined device
including a chamber housing at least one heat exchanger and an
accumulation area, in which said chamber extends according to a
primary central axis and said heat exchanger extends according to a
secondary central axis, characterized in that the primary central
axis is offset with respect to the secondary central axis.
[0016] According to a first feature of the invention, the offset
between the primary central axis and the secondary central axis is
between one and twenty-five millimeters.
[0017] According to a second feature of the invention, the chamber
and the heat exchanger have a cylindrical shape.
[0018] According to another feature of the invention, the heat
exchanger includes at least one first flat tube wound on itself
about the secondary central axis.
[0019] According to another feature of the invention, the first
flat tube includes a plurality of channels.
[0020] According to another feature of the invention, the heat
exchanger includes an intake chamber that extends to the center of
the first flat tube wound on itself.
[0021] Advantageously, the combined device includes a discharge
chamber located at least partially around the heat exchanger,
wherein said discharge chamber is delimited by an external wall of
the heat exchanger and by an internal wall of the chamber.
[0022] Also advantageously, the heat exchanger includes a first
circulation path delimited by the plurality of channels of the
first flat tube, wherein said first circulation path is in
communication via a first end of the flat tube with the intake
chamber and in communication with the discharge chamber by means of
a second end of the first flat tube.
[0023] According to an advantageous feature of the invention, the
first circulation path is delimited by a second flat tube wound
with the first flat tube.
[0024] The heat exchanger includes a second circulation path
delimited by a plurality of channels of a third flat tube wound
with the first flat tube.
[0025] According to another feature of the invention, the second
circulation path is, on the one hand, in communication with the
first channel placed at the periphery of the heat exchanger and, on
the other hand, in communication with a second channel of which the
axis is aligned with the secondary central axis.
[0026] In addition, the first flat tube and the second flat tube,
the third flat tube, the first channel and the second channel form
a unitary assembly.
[0027] Moreover, the chamber is closed by an upper partition and a
lower partition and the accumulation area comprises a lower wall
arranged at the border between the heat exchanger and said
accumulation area.
[0028] The device according to the invention comprises a first
conduit that passes through the upper partition and leads into a
separation area located in the chamber and above the accumulation
area.
[0029] Finally, the combined device includes a second conduit that
passes through the lower partition and leads into the discharge
chamber.
[0030] The invention also relates to an air conditioning loop in
which a combined device is incorporated, including at least one of
the features indicated above.
[0031] A very first advantage of the invention lies in the fact
that it is possible to preserve a component with low external bulk
without increasing the internal head losses, in particular on the
first circulation path. This enables the component to be more
easily integrated according to the invention in an engine
compartment in which the space is increasingly reduced.
[0032] Other features, details and advantages of the invention will
become clearer in view of the following description provided for
illustrative purposes, in association with the drawings, in
which:
[0033] FIG. 1 is a longitudinal cross-section view of the combined
device according to the invention,
[0034] FIG. 2 is a transverse cross-section view at the level of
the heat exchanger of a combined device according to the
invention.
[0035] The above-mentioned figures will be used to describe an
implementation of the invention, and can also help to define it
better, as the case may be.
[0036] FIG. 1 shows a combined device 1 according to the invention,
including a chamber 2 closed by an upper partition 3, also called
an upper lid, and a lower partition 4, or a lower lid.
[0037] The chamber 2 extends according to a primary central axis A
in a longitudinal direction. The chamber 2 has a cylindrical
cross-section, but can also be parallelepiped (square, rectangular,
etc.). The length of the chamber 2 measured in the direction of the
primary central axis A is greater than the external diameter
measured perpendicularly to the primary central axis A.
[0038] The combined device 1 also comprises a "high-pressure" inlet
5 through which a coolant 16 combing from a gas cooler is admitted
into the combined device 1. This "high-pressure" inlet 5 consists
of a first tubular channel 12 that passes through the lower
partition 4 in order to be connected to a heat exchanger 9. The
combined device 1 also comprises a "high-pressure" outlet 6 through
which the high-pressure coolant is discharged from the combined
device 1 to the expansion member. This "high-pressure" outlet 6 is
in the form of a second tubular channel 13, which starts at the
level of the heat exchanger 9 in order to pass through the internal
volume of the chamber 2 and lead through the upper partition 3.
[0039] The combined device 1 also comprises a "low-pressure" inlet
7 through which the coolant coming from the evaporator is admitted
into the combined device 1. The "low-pressure" inlet 7 is in the
form of a first conduit 14 that passes through the upper partition
3. The combined device 1 finally comprises a "low-pressure" outlet
8 through which the low-pressure coolant is discharged from the
combined device 1 to the compressor. This "low-pressure" outlet 8
is, in this case, also in the form of a second tubular conduit 15
that passes through the lower partition 4.
[0040] The combined device 1 includes the chamber 2, which is
sealed with respect to the outside, which houses the heat exchanger
9, a separation area 10 between the gaseous phase 16a and the
liquid phase 16b of the coolant leaving the evaporator, as well as
an accumulation area 11 for the coolant in the liquid state coming
from the evaporator, or more specifically coming from the
separation area 10.
[0041] Said separation area 10 preferably has a cyclone structure
in the sense that the first conduit 14 is offset with respect to
the primary central axis A of the chamber 2 of the combined device
1 in order to enable tangential intake of the coolant coming from
the evaporator inside said separation area 10. The tangential
intake is implemented by means of a hole 17 provided through the
cylindrical wall of the first conduit 14. These arrangements are
intended to promote the mutual separation of said gaseous phase 16a
and said liquid phase 16b. An end of the first conduit 14 located
inside the internal volume of the chamber 2 is closed off by a
plate 18. This plate extends perpendicularly to the primary central
axis A of the chamber 2. A small clearance is maintained between
the periphery of said plate 18 and the internal wall 19 of the
chamber 2 so as to allow the liquid phase 16b of the coolant 16 to
descend by gravity toward the accumulation area 11. The
accumulation area 11 begins below the plate 18.
[0042] This accumulation area is delimited by a lower wall 20,
against which the coolant in the liquid state coming from the
evaporator accumulates by gravity. As the "low-pressure" inlet 7
is, in the use position of the combined device 1 on the air
conditioning loop and/or in the operating position of the combined
device 1 alone, placed above the lower wall 20, the coolant 16 in
the liquid state naturally falls by gravity from the "low-pressure"
inlet 7 toward the lower wall 20 so as to finally rest against the
latter. The lower wall 20 is tightly mounted against the internal
wall 19 of the chamber 2.
[0043] The accumulation area 11 is passed through by the second
channel 13, but it is also passed through by an intermediate
conduit 21, of which a first end 21a leads into the separation area
10, several millimeters above a plane defined by the plate 19. This
arrangement makes it possible to ensure that the liquid phase 16b
of the coolant does not return to the intermediate conduit 21 so
that only the gaseous phase 16a of the coolant 16 can penetrate it.
The intermediate conduit 21 passes through the lower wall 20 and
has a second end 21b that is in communication with the heat
exchanger 9. In a first configuration shown in FIG. 1, the
intermediate conduit 21 has a diameter greater than the second
channel 6 and is mounted coaxially with respect to the latter. It
is therefore noted that both the axis of the intermediate conduit
21 and the axis of the second channel 6 are offset with respect to
the primary central axis A of the chamber 2. In a second
configuration not shown, the intermediate conduit 21 always has a
diameter greater than the second channel 6. However, the central
axis of the intermediate conduit 21 merges with or is coaxial to
the primary central axis A. It is therefore understood that the
intermediate conduit is at the center of the cylinder formed by the
chamber 2. In this configuration, the heat exchanger 9 is however
always offset as required by the invention. Thus, the second
channel 6 is offset in the intermediate conduit 21; in other words
the central axis of the second channel 6 is not coaxial to or does
not merge with the central axis of the intermediate conduit 21, as
the latter merges with the primary central axis A.
[0044] It is noted that the coolant 16 in the gaseous state
descends toward the internal exchanger 9 while the coolant carried
in the second channel 6 rises in the direction of the upper
partition 3. The circulation in this portion of the combined device
is said to be "counter-current".
[0045] The lower wall 20 is preferably perpendicular to the primary
central axis A of the chamber 2 of the combined device 1.
[0046] The separation area 10 is contiguous to said upper partition
3, by being positioned directly below the latter. Thus the
accumulation area 11 is placed between the separation area 10 and
the lower wall 20, and the plate 18 is inserted between the
separation area 10 and the accumulation area 11.
[0047] The lower wall 20, which delimits, in the bottom portion,
the accumulation area 11, is arranged above the heat exchanger 9.
It is noted that the accumulation area 11 is arranged above the
heat exchanger 9 according to the gravity axis.
[0048] The cross-section of the chamber 2 and the cross-second of
the heat exchanger 9 are both cylindrical, thereby providing
perfect shape cooperation.
[0049] The accumulation area 11 overhanging or placed above the
heat exchanger 9 is higher than the heat exchanger 9, according to
the primary central axis A of the chamber 2.
[0050] The heat exchanger 9 consists of a first flat tube 22 wound
on itself, preferably about a secondary central axis B of the heat
exchanger, in which said secondary central axis B is distinct from,
i.e. non-coaxial to, the primary central axis A of the chamber 2 of
the combined device 1. It is noted that this offset d, formed by
the distance that separates the primary central axis A from the
secondary central axis B, enables an area of the lower partition 4
to be freed, into which it is then easier to lead the second
channel 15 without increasing the external dimensions of the
chamber 2, and therefore of the combined device as a whole. It is
noted that the primary central axis A and the secondary central
axis B are parallel.
[0051] The first flat tube 22 houses a plurality of channels 23,
also called micro-channels, for the passage of the low-pressure
coolant. This plurality of channels consists of a first circulation
path for the low-pressure coolant. This first circulation path is
in communication, on the one hand, with an intake chamber 24 and,
on the other hand, with a discharge chamber 25. The intake chamber
24 is delimited by the end 21b of the intermediate conduit 21, by
the first turn of the first flat tube 22 wound on itself and by the
lower partition 4.
[0052] The discharge chamber 25 is delimited by a peripheral turn
of the winding of the first flat tube 22 and/or a third flat tube
27 (which will be described below in greater detail), thus defining
the external wall of the heat exchanger 9, by the lower wall 20, by
the lower partition 4 and finally by the internal wall 19 of the
chamber 2 plumb over the heat exchanger 9. The consequence of the
offset d between the primary central axis A and the secondary
central axis is the ovoid shape of the cross-section of the
discharge chamber.
[0053] The first circulation path includes a second flat tube 26
equipped with a plurality of channels 23. This second flat tube 26
is wound with the first flat tube 22 and together they form the
first circulation path for the "low-pressure" coolant 16.
[0054] The heat exchanger 9 also includes a third flat tube of
which the plurality of channels 23 delimits a second circulation
path, wherein the latter is adopted by the "high-pressure" coolant.
This third flat tube 27 is, on the one hand, in communication with
the first channel 12 placed at the periphery of the heat exchanger
and, on the other hand, in communication with the second channel of
which the axis is aligned or merges with the secondary central axis
B of the heat exchanger 9. The first channel 12 is then tightly
connected (for example, welded, brazed, etc.) to the end of the
third flat tube 27 and the plurality of channels 23 communicate
fluidly with the inside of the first channel 12. The same is true
of the other end of the third flat tube 27, which communicates with
the second channel 13.
[0055] If the heat exchanger 9 does not include a second flat tube
26, it then consists of a first flat tube 22 and a third flat tube
27 jointly wound so as to form the first circulation path and the
second circulation path, respectively.
[0056] In an alternative in which the first circulation path is
equipped with a first and a second flat tube 22, 26, the third flat
tube 27 is then inserted or sandwiched between the first and second
flat tubes.
[0057] In these cases, the three flat tubes (first, third and
second) are wound about the secondary central axis B of the heat
exchanger 9 so that the respective turns formed by said tubes are
interleaved one in the other.
[0058] An intermediate subassembly consists of the first flat tube
22 and the second flat tube 26, the third flat tube 27, the first
channel 12 and the second channel 13 so as to form a unitary
assembly. This assembly is constructed insofar as the
aforementioned elements are unremovably connected without
destroying the unitary assembly. It advantageously involves a solid
and tight connection (ensured, for example, by brazing, welding,
etc.), which enables all of said elements to be connected to one
another.
[0059] FIG. 2 shows the invention according to a cross-section view
perpendicular to the primary central axis A of the chamber 2. The
intersection between the interrupted line C-C and the interrupted
line F-F shows the primary central axis A of the chamber 2, more
specifically the central axis of the volume delimited by the
internal wall 19. The thickness of the chamber 2 has been presented
only in part so as not to complicate FIG. 2.
[0060] The intersection between the interrupted line E-E and the
interrupted line F-F shows the secondary central axis B of the heat
exchanger 9. The offset d is the distance that separates the
primary central axis A of the chamber 2 and the secondary central
axis B of the heat exchanger 9, wherein said offset is a minimum
value of one millimeter below which the gain in space lateral to
the heat exchanger 9 becomes marginal. The maximum value of the
offset d is twenty-five millimeters because it is the maximum value
to maintain a satisfactory compromise between the external diameter
of the heat exchanger and the external diameter of the chamber
2.
[0061] Between these two values, the invention frees a space
lateral to the heat exchanger 9, and this space then constitutes
the discharge chamber 25. It is noted that the second conduit 15
can then be placed more easily without requiring an increase in the
diameter of the chamber 2, with a constant diameter of the heat
exchanger 9, diameter of the chamber 2 and diameter of the second
conduit 15.
[0062] The third flat tube 27 is connected by one end to the first
channel 12 located at the periphery of the heat exchanger 9, while
the other end of the third flat tube 27 is connected to the second
channel 13 of which the axis merges with the secondary central axis
B of the heat exchanger 9.
[0063] The first flat tube 22 and the second flat tube 26 collect
the coolant in the gaseous state at "low pressure" in the intake
chamber via the end of the flat tubes. The coolant at "low
pressure" goes into the first and second flat tubes 22, 26 at a
counter-current to the circulation of the coolant at "high
pressure", which goes into the third flat tube 27. The
"low-pressure" fluid leaves through the ends of the first and
second flat tubes 22 and 26 so as to spread into the discharge
chamber 26 and leave the combined device 1 via the second conduit
15.
[0064] The provisions described above are such that the combined
device 1 is capable of being fluidly connected to the air
conditioning loop by means of upper 3 and lower 4 partitions.
Therefore, the connections between the combined device 1 and, on
the one hand, the compressor and, on the other hand, the gas
cooler, are produced by means of conduits connected over the lower
partition 4, while the connections between the combined device 1
and, on the one hand, the evaporator and, on the other hand, the
expansion member, are produced by means of conduits connected over
the upper partition 3. Such arrangements facilitate the integration
of the combined device 1 on the air conditioning loop and
consequently the integration thereof in the engine compartment of
the motor vehicle.
[0065] The terms "above", "below", "overhanging", "lower" and
"upper" should be understood according to the position of use of
the combined device 1. This position of use can easily be
determined by the installation of the combined device 1 according
to the invention in the air conditioning loop of the vehicle. This
position of use can nevertheless also easily be determined with the
combined device 1 alone, i.e. independently of its installation in
the air conditioning loop, insofar as its operation appears to be
realistic.
* * * * *