TECHNICAL FIELD
[0001] The present invention relates to a heat exchanger comprising a plurality of compensation
plates that will improve the resistance to thermal fatigue of the heat exchanger.
BACKGROUND ART
[0002] Plate heat exchangers are used throughout industry as standard equipment for efficient
heating, cooling, heat recovery, condensation and evaporation. Heat exchangers may
be of different types and designs, depending on the type of medium that is to be heated
or cooled.
[0003] One type of heat exchanger is the plate-and-shell type. This type is well suited
for uses involving high pressures and high temperatures. Such a plate-and-shell heat
exchanger comprises a pack of corrugated, circular metal plates housed in a vessel.
The heat transfer surface of the heat exchanger is formed by thin corrugated discs
stacked and welded on top of each other, which creates a process channel between the
plates. The fluid for the process channel is led into the plate pack via ports welded
into the discs and to an end plate of the vessel, and is distributed into the process
channel between the plates. The corrugated discs are alternately welded at the outer
circumference of the discs and at the port holes, thereby creating alternate fluid
channels. The inlet and outlet ports for the process channel are positioned in the
end plates, either in the same end plate or in both end plates. The inlet and outlet
ports for the shell side of the heat exchanger are welded in the side wall of the
vessel. The flow through the heat exchanger may be of either a counter-current, a
cocurrent or a cross flow type.
[0004] The construction of such a heat transfer core makes the plate-and-shell type plate
pack highly resistant to thermal expansion. This in turn makes them ideal for use
under high-pressure and high-temperature conditions.
[0005] There is however a problem with fast thermal cycling of such heat exchangers, especially
for larger heat exchangers having a large diameter. Since the corrugated discs are
thin and in contact with the fluids, they will respond immediately to temperature
changes. The vessel on the other side, being of a much thicker material, will respond
much slower to temperature changes. This will result in high stresses at the inlet
and outlet port regions for the process channel, where the discs are welded to the
end plate of the heat exchanger. In one example, a stainless steel disc having a diameter
of 1 m will expand almost 2 mm with a temperature rise of 100 degrees centigrade.
Fast thermal cycling should thus be avoided for plate-and-shell type heat exchangers.
[0006] US 7004237 B2 describes a plate-and-shell type heat exchanger for fluids, in which a spring device
compensates for longitudinal thermal expansion of the heat exchanger core.
[0007] US 6474408 B1 and
US 6892797 B2 describe heat exchangers for gas provided with means that allows for thermal expansion
in the longitudinal direction of the heat exchanger.
[0008] These known solutions may work well for thermal expansion in the longitudinal direction
of the heat exchanger, but will not solve the problem with radial expansion. There
is thus room for an improved heat exchanger, in which radial expansion is allowed.
DISCLOSURE OF INVENTION
[0009] An object of the invention is therefore to provide a heat exchanger where stress
due to thermal expansion at the inlet and outlet region is minimized. The solution
to the problem according to the invention is described in the characterizing part
of claim 1. Claims 2 to 11 contain advantageous embodiments of the heat exchanger.
[0010] With a heat exchanger, comprising a housing having a first end plate, a second end
plate and a shell, where the first end plate is provided with an inlet port and the
first or the second end plate is provided with an outlet port, and further comprising
a plurality of corrugated heat exchanger plates having ridges and grooves, where the
heat exchanger plates are fixedly attached to each other, such that a first flow channel
is created between the heat exchanger plates, the object of the invention is achieved
in that the heat exchanger further comprises a plurality of compensation plates positioned
between the heat exchanger plates and at least one of the end plates.
[0011] By this first embodiment of the heat exchanger, a heat exchanger is obtained in which
the stress on the joints between the inlet and outlet ports and the heat exchanger
plates are reduced. This will allow the heat exchanger to be able to withstand a greater
temperature gradient than existing heat exchangers. The heat exchanger can be used
in areas where fast temperature cycling is present. The heat exchanger can also be
used in areas where higher temperature differences are present. The operating range
of the heat exchanger is thus increased.
[0012] The compensation plates are fixedly attached to the heat exchanger plates on one
side and to the inlet and outlet ports on the other side. This is advantageous in
that a heat exchanger that can withstand high pressures is obtained, compared with
heat exchangers having sealing gaskets.
[0013] In an advantageous development of the inventive heat exchanger, the pattern of the
compensation plates comprises concentric ridges and grooves. The advantage of this
is that the radial stiffness of the compensation plates is reduced compared with existing
heat exchanger plate patterns.
[0014] In an advantageous development of the inventive heat exchanger, the flank angle of
the compensation plates is smaller than the flank angle of the heat exchanger plates.
The advantage of this is that the radial stiffness can be reduced further.
[0015] In an advantageous development of the inventive heat exchanger, the flank angle of
the compensation plates is less than 30 degrees. The advantage of this is that the
radial stiffness can be reduced further.
[0016] In an advantageous development of the inventive heat exchanger, the compensation
plate comprises a circular opening in the centre of the compensation plate. The advantage
of this is that the radical stiffness can be reduced further,
[0017] In an advantageous development of the inventive heat exchanger, the compensation
plate comprises a pressure plate in the central opening of the compensation plate.
The advantage of this is that the heat exchanger plates are supported.
[0018] In an advantageous development of the inventive heat exchanger, the compensation
plate and the pressure plate are attached to each other. The advantage of this is
that the handling of the compensation plates and the assembly of the heat exchanger
is facilitated.
BRIEF DESCRIPTION OF DRAWINGS
[0019] The invention will be described in greater detail in the following, with reference
to the embodiments that are shown in the attached drawings, in which
- Fig. 1
- shows a heat exchanger according to the invention,
- Fig. 2
- shows a schematic layout of the plate side flow channel for the heat exchanger according
to a first embodiment of the invention,
- Fig. 3
- shows a schematic layout of the plate side flow channel for the heat exchanger according
to a second embodiment of the invention,
- Fig. 4
- shows a first embodiment of a compensation plate according to the invention,
- Fig. 5
- shows a cross-section of the compensation plate according to the invention,
- Fig. 6
- shows a cross section of an inlet or outlet region of the heat exchanger according
to the invention,
- Fig. 7
- shows a second embodiment of a compensation plate according to the invention, and
- Fig. 8
- shows a second embodiment of a compensation plate with a pressure plate according
to the invention.
MODES FOR CARRYING OUT THE INVENTION
[0020] The embodiments of the invention with further developments described in the following
are to be regarded only as examples and are in no way to limit the scope of the protection
provided by the patent claims.
[0021] Fig. 1 shows a heat exchanger of the plate-and-shell type. Such a heat exchanger
is suitable for most applications, such as general cooling and heating duties, condensation,
evaporation, reboiling and steam heating. It is especially suitable for handling applications
with high temperatures and/or high pressures. The shown heat exchanger is circular,
having a round housing with two fixedly attached endplates.
[0022] The heat exchanger 1 comprises a housing 30 made up of end plates 6, 7 and a shell
8. The shell 8 is in this example circular, but other shapes, e.g. elliptical, are
conceivable. The heat exchanger 1 further comprises four ports 2, 3, 4, 5 that will
constitute either inlet ports or outlet ports to the heat exchanger, depending on
the use and configuration of the heat exchanger. In the shown heat exchanger 1, port
2 is the inlet port and port 3 is the outlet port for the first flow channel, which
in this example is the flow channel on the plate side, i.e. through the heat exchanger
plates. Inlet port 2 and outlet port 3 are in a first embodiment both positioned in
the first end plate 6, close to the outer edge of end plate 6. Port 4 is the inlet
port for the flow channel of the shell side of the heat exchanger and port 5 is the
outlet port for the shell side flow channel. Ports 4 and 5 are positioned in the shell
8 of the heat exchanger. A second end plate 7 closes the heat exchanger. The end plates
6 and 7 are fixed to the shell in a rigid way, allowing for a high pressure in the
heat exchanger. The end plates 6, 7 may either be welded to the housing, or fixed
to the housing with bolts and a flange. The heat exchanger may be provided with more
than one plate side flow channel. The heat exchanger may in this case be divided into
different flow channels, and the end plates will have more than one inlet and outlet
ports.
[0023] Fig. 2 shows schematically the plate side flow channel for the first embodiment of
the heat exchanger. Such a flow channel can be referred to as a U-type flow pattern.
A fluid enters the heat exchanger through the inlet port 2 and flows through the inlet
flow duct 32. The fluid is distributed from the inlet flow duct 32 through the heat
exchanger plate stack 17, where the heat exchange takes place. Since the pressure
drop in the inlet flow duct is much lower than the pressure drop through the heat
exchanger plate stack, the fluid is distributed in a substantially even way over the
heat transfer surface of the heat exchanger. The fluid leaves the heat exchanger through
the outlet flow duct 33 and the outlet port 3. The flow path is illustrated with arrows
in the figure. The heat exchanger further comprises a compensation plate stack 21
positioned between the first end plate 6 and the heat exchanger plate stack 17. The
compensation plate will be described below.
[0024] Fig. 3 shows schematically the plate side flow channel for a second embodiment of
the heat exchanger, in which the inlet port 2 is positioned in the first end plate
6 and the outset port 3 is positioned in the second end plate 7. Such a flow channel
can be referred to as a Z-type flow pattern. A fluid enters the heat exchanger through
the inlet port 2 and flows through the inlet flow duct 32. The fluid is distributed
from the inlet flow duct 32 through the heat exchanger plate stack 17, where the heat
exchange takes place in the same way as described above. The fluid leaves the heat
exchanger through the outlet flow duct 33 and the outlet port 3. The flow path is
illustrated with arrows in the figure. In this embodiment, a compensation plate stack
21 is positioned between the first end plate 6 and the heat exchanger plate stack
17 and another compensation plate stack 212 is positioned between the second end plate
7 and the heat exchanger plate stack 17.
[0025] In both shown embodiments, the inlet port 2 is arranged along an inlet axis 34 and
the outlet port 3 is arranged along an outlet axis 35. The inlet axis 34 and the outlet
taxis 35 are arranged on opposite sides of the centre axis 36 in a symmetric way.
[0026] The inlet port 2 and the outlet port 3 comprise an outer flange to which the heat
exchanger is connected to the system in which the heat exchanger is used. Each port
further comprises a short pipe that is welded to the end plate and that extends through
the end plate so that it can, in this case, abut the compensation plate. The pipe
is fixedly attached to the compensation plate closest to the port, e.g. by welding,
thereby creating a joint between the port pipe and the compensation plates. An example
of this can be seen in Fig. 6.
[0027] The heat exchanger comprises a number of corrugated heat exchanger plates 10, 11
having a corrugated pattern comprising ridges 12 and grooves 13. The ridges and grooves
enlarge the heat transfer surface of the heat exchanger and create a suitable pressure
drop through the flow channel. The pattern may have different shapes, depending on
the use of the heat exchanger. The heat exchanger plates are stacked on each other
in such a way that a flow channel is created between the plates, referred to as the
plate side flow channel or the first flow channel. Between two adjacent plates 10,
11, the first flow channel 14 is created. In this case, the two plates are welded
at the outer periphery 9 of the heat exchanger plates, making up a heat exchanger
cassette. An enclosed volume is thus created, which is part of the plate side flow
channel. The cassettes are welded to each other at the port openings 16 of the heat
exchanger plates. In this way, a second flow channel 15, also referred to as the shell
side flow channel, is created on the shell side between the cassettes. The number
and size of the cassettes comprised in the heat exchanger is selected depending on
the required heating/cooling capacity of the heat exchanger. The welded heat exchanger
plates make up the heat exchanger core. Such a heat exchanger core is well known in
the art and is not described further. The flow channels in the heat exchanger may
be configured in different ways, known to the skilled person.
[0028] In known heat exchangers, the inlet port pipe and the outlet port pipe is welded
directly to the heat exchanger plate pack, i.e. to the heat exchanger plate closest
to the inlet and outlet ports in order to obtain a pressure tight plate side flow
channel. The inlet port pipe and the outlet port pipe are also welded to the end plate
of the heat exchanger in order to obtain a pressure tight flow channel on the shell
side of the heat exchanger. In this way, the ports opening of the heat exchanger plate
will be fixedly attached to the end plate. Since the heat exchanger plate will react
to thermal changes much faster than the end plate, there will be stress imposed on
the joint between the inlet and outlet pipe and the heat exchanger plate. If the connection
is exposed to thermal cycling, the connection will, depending e.g. on the distance
between the inlet and outlet pipe, deteriorate and may eventually break.
[0029] The inventive heat exchanger is thus provided with a number of compensation plates
20 disposed between the first end plate 6 and the heat exchanger plate stack 17. The
purpose of the compensation plates is to allow the heat exchanger plates to expand
or shrink due to a fast temperature change without imposing thermal fatigue to the
joints between the heat exchanger plate pack and the end plate. Fig. 4 shows a side
view of a compensation plate 20, Fig. 5 shows a cross-section of a compensation plate
and Fig. 6 shows a cross-section of the inlet region of a heat exchanger.
[0030] The compensation plate 20 is provided with a concentric corrugated pattern comprising
ridges 18 and grooves 19. The pattern is pressed such that the height distance between
the ridges and the grooves corresponds to the pressing depth of the plate. The compensation
plate has a reference level denoted a, with the pressing depth corresponding to the
height h. In the shown example, the grooves are at the reference level a The outer
periphery 22 of the compensation plate is also at the reference level a. The circumference
31 of each port opening 23 in the compensation plate will have the same height as
the ridges, i.e. the height h. When the compensation plates are assembled into a compensation
plate stack 21, 212, every other compensation plate is turned so that the outer periphery
of two adjacent compensation plates bear on each other, and so that the circumference
of the port openings of two other adjacent compensation plates bear on each other.
At the same time, the ridges of two adjacent compensation plates bear on each other,
and the grooves of two other adjacent compensation plates bear on each other.
[0031] The compensation plates in a compensation plate stack 21, 212 are fixedly attached
to each other, e.g. by welding or brazing, only at the outer periphery 22 and at the
circumference 31 of the port openings 23. The ridges or grooves of respective adjacent
compensation plates will also bear on each other, but will not be fixedly attached
to each other.
[0032] The flank angle α of the compensation plate may be smaller than the flank angle β
of the heat exchanger plates. Normally, the flank angle β of a heat exchanger plate
is around 45 degrees in order to provide a large heat transfer surface and at the
same time a relatively stiff plate. By choosing a concentric pattern for the compensation
plates, a relatively low radial stiffness is obtained. With a small flank angle α,
the radial stiffness is further decreased. A flank angle α of between 10 and 30 degrees
is preferred. A low radial stiffness of the compensation plate is of advantage.
[0033] In Fig. 6, the inlet port region of a heat exchanger is sown. In this example, seven
compensation plates are used in the compensation plate stack 21. The first compensation
plate is fixedly attached, e.g. by welding or brazing, to the inlet pipe 24, which
in turn is welded to the end plate 6. The consecutive compensation plates are fixedly
attached to each other at either the outer periphery 22 or the circumference 31 of
the port openings 23. The last compensation plate is fixedly attached to the heat
exchanger plate stack 17 at the outer periphery 22 of the compensation plate 20 and
the outer periphery 9 of a heat exchanger plate. There will be a very limited flow
between the compensation plates, both in the plate side flow channel and in the shell
side flow channel, since the corrugated pattern is symmetric and is not laid out for
heat transfer. The ridges of one plate bears on the ridges of an adjacent plate, and
for every other plate, the grooves of one plate bear on the grooves of another adjacent
plate. There are no cross-corrugations in the compensation plate stack due to the
concentric pattern of the compensation plates. The outlet port region will resemble
the inlet port region.
[0034] The compensation plate stack 21, 212 functions in the following way. When a quick
and high temperature rise occurs in the heat exchanger, the heat exchanger plates
in the heat exchanger plate stack 17 will immediately expand. The end plate 6 will
expand much slower, partly because the end plate is much thicker than the heat exchanger
plates and partly because the end plate is in very little contact with the media flowing
through the heat exchanger. The compensation plates will expand somewhat slower than
the heat exchanger plates, since most of the compensation plates are not in great
contact with the flow through the heat exchanger.
[0035] When the heat exchanger plates expand, the compensation plate stack can not expand
in the same way, since a compensation plate is fixed to the end plate. The compensation
plates can, due to the concentric pattern, expand in a different way than the heat
exchanger plates and will expand in a somewhat elliptical shape. Since the compensation
plate stack is attached to the heat exchanger plate stack on one side and to the end
plate on the other side, each compensation plate will expand somewhat differently.
Each plate will thus help to minimize the stress imposed on the joint 25 between the
inlet pipe 24 and the port opening circumference 31 of the compensation plate closest
to the end plate. Since the compensation plates have a relatively low radial stiffness,
the stress imposed on the plates due to the thermal expansion is divided over the
complete plate stack, and the stress imposed on each plate is divided over each plate.
[0036] The complete core of the heat exchanger, comprising the heat exchanger plate stack
17 and one or two compensation plate stacks 21, 212, is held in position by the end
plates. Since all plates are welded together, the core is stiff and can only expand
in the radial direction, towards the shell. Other forms of deformation are not possible
when the core is mounted in the heat exchanger housing. If the core was not mounted
in a heat exchanger, the distance between the inlet axis 34 and the outlet axis 35
would increase with higher temperature. Because that the core is fixedly attached
to the end plates, the distance between the inset axis 34 and the outlet axis 35 can
not change when the temperature changes. Instead, stress will be imposed on the joint
between the core and the end plates.
[0037] The stress imposed on the joints between the core and the end plates will be the
same for the two shown embodiments. Since the heat exchanger core is pressed between
the end plates, the stress will be the same regardless of on which side of the inlet
or outlet flow duct the inlet or outlet port is located.
[0038] In a second embodiment of the compensation plate, shown in fig. 7 and 8, the compensation
plate 20 is provided With an opening 28 in the centre of the compensation plate. The
opening may be cut out during the pressing of the compensation plate or in a later
process step. With the opening in the centre of the compensation plate, every other
compensation plate must be welded to an adjacent compensation plate also at the inner
periphery 27 in order to obtain a closed channel for the plate side flow channel.
The advantage of having an opening in the centre of the compensation plate is that
the radial stiffness of the compensation plate is decreased further.
[0039] In order to support the heat exchanger plates, the central opening 28 must be provided
with some kind of support means for the support of the centre of the heat exchanger
plates. For this purpose, a pressure plate 29 is provided in the centre of each compensation
plate. It is advantageous to use the cut-out for the central opening as a pressure
plate 29. In order to facilitate the handling of the compensation plates and the assembly
of the heat exchanger, the pressure plate is preferably attached to the compensation
plate. One way of attaching the pressure plate to the compensation plate is by welding.
The outer and inner peripheries of the compensation plate are seal welded in order
to obtain a pressure tight weld. The pressure plate is preferably tack welded to the
compensation plate in a few positions, in order to obtain a flexible attachment of
the pressure plate. The pressure plate should not be rigidly attached to the compensation
plate.
[0040] It is also possible to leave a few plate bridges 26 between the pressure plate and
the compensation plate during the pressing of the compensation plate. The plate bridges
26 will thus connect the compensation plate to the pressure plate. In this way, the
pressure plate and the compensation plate will not be completely separated. This will
facilitate the handling of the compensation plate, but may interfere with the attachment
of the inner peripheries to each other. It is also possible to attach all pressure
plates into one pressure plate unit that is assembled to the heat exchanger separately.
Other types of support means are also conceivable.
[0041] The number of compensation plates used in a compensation plate stack may vary depending
e.g. on the diameter of the heat exchanger, the temperatures that the heat exchanger
is designed for and the thickness and pressing depth of the compensation plates. A
suitable number of compensation plates for a heat exchanger having a diameter of 1
meter is between 3 and 9. In the shown example, 7 compensation plates are used. By
using too few compensation plates, the stress imposed on the joint between the inlet
pipe and the compensation plate will be too high. By using too many compensation plates,
an unnecessary large volume is wasted in the heat exchanger, since the compensation
plate stack is not part of the heat transfer surface of the heat exchanger.
REFERENCE SIGNS
[0042]
- 1:
- heat exchanger
- 2:
- Inlet port
- 3:
- Outlet port
- 4:
- Inlet port
- 5:
- Outlet hole
- 6:
- First end plate
- 7:
- Second end plate
- 8:
- Shell
- 9:
- Heat exchanger plate outer periphery
- 10:
- Heat exchanger plate
- 11:
- Heat exchanger plate
- 12:
- Ridge
- 13:
- Groove
- 14:
- First flow channel
- 15:
- Second flow channel
- 16:
- Heat exchanger plate port opening
- 17:
- Heat exchanger plate stack
- 18:
- Compensation plate ridge
- 19:
- Compensation plate groove
- 20:
- Compensation plate
- 21:
- Compensation plate stack
- 212:
- Another compensation plate stack
- 22:
- Compensation plate outer periphery
- 23:
- Compensation plate port opening
- 24:
- Inlet pipe
- 25:
- Joint
- 26:
- Plate bridge
- 27:
- Compensation plate inner periphery
- 28:
- Central opening
- 29:
- Pressure plate
- 30:
- Housing
- 31:
- Port opening circumference
- 32:
- Inlet flow duct
- 33:
- Outlet flow duct
- 34:
- Inlet axis
- 34:
- Outlet axis
- 35:
- Centre axis
1. Heat exchanger (1), comprising a housing (30) having a first end plate (6), a second
end plate (7) and a shell (8), where the first end plate (6) is provided with an inlet
port (2) and the first or the second end plate (6, 7) is provided with an outlet port
(3), and further comprising a plurality of corrugated heat exchanger plates (10, 11)
having ridges (12) and grooves (13), where the heat exchanger plates are fixedly attached
to each other, such that a first flow channel (14) is created between the heat exchanger
plates (10, 11),
characterized in that the heat exchanger further comprises a plurality of corrugated compensation plates
(20) fixedly attached to each other to form a compensation plate stack (21) positioned
between the heat exchanger plates (10, 11) and at least one of the end plates (6,
7), wherein
a) the first end plate (6) is provided with the inlet port (2) and the outlet port
(3), and the compensation plate stack (21) is fixedly attached to the heat exchanger
plates (10, 11) on one side and to the inlet and outlet ports (2, 3) of the first
end plate (6) on the other side, or
b) the first end plate (6) is provided with the inlet port (2) and the second end
plate (7) is provided with the outlet port (3), and the compensation plate stack (21)
is fixedly attached to the heat exchanger plates (10, 11) on one side and to the inlet
port (2) of the first end plate (6) on the other side, and that another compensation
plate stack (212) is fixedly attached to the heat exchanger plates (10, 11) on one
side and to the outlet port (3) of the second end plate (7) on the other side.
2. Heat exchanger according to claim 1, characterized in that the shell (8) is circular.
3. Heat exchanger according to claim 1 or 2, characterized in that the pattern of a compensation plate (20) comprises concentric ridges (18) and grooves
(19).
4. Heat exchanger according to claim 3, characterized in that flank angle (α) of the compensation plates (20) is smaller than the flank angle (β)
of the heat exchanger plates (10, 11).
5. Heat exchanger according to any of claims 1 to 4, characterized in that the flank angle (α) of the compensation plates (20) is less than 30 degrees.
6. Heat exchanger according to any of claims 1 to 5, characterized in that the compensation plate (20) comprises a circular opening (28) in the centre of the
compensation plate.
7. Heat exchanger according to claim 6, characterized in that two adjacent compensation plates (20) are fixedly attached to each other at the outer
periphery (22) and the inner periphery (27) of the compensation plate.
8. Heat exchanger according to claim 6 or 7, characterized in that the compensation plate (20) comprises a pressure plate (29) in the central opening
(28) of the compensation plate.
9. Heat exchanger according to claim 8, characterized in that the compensation plate (20) and the pressure plate (29) are attached to each other.
10. Heat exchanger according to any of claims 1 to 9, characterized in that the heat exchanger plates and/or the compensation plates are welded to each other.
11. Heat exchanger according to any of claims 1 to 9, characterized in that the heat exchanger plates and/or the compensation plates are brazed to each other.
1. Wärmetauscher (1), umfassend ein Gehäuse (30), das eine erste Endplatte (6), eine
zweite Endplatte (7) und einen Mantel (8) aufweist, wobei die erste Endplatte (6)
mit einer Einlassöffnung (2) versehen ist und die erste oder die zweite Endplatte
(6, 7) mit einer Auslassöffnung (3) versehen ist, und ferner umfassend eine Vielzahl
gewellter Wärmetauscherplatten (10, 11), die Erhöhungen (12) und Rillen (13) aufweisen,
wobei die Wärmetauscherplatten fest aneinander befestigt sind, sodass ein erster Strömungskanal
(14) zwischen den Wärmetauscherplatten (10, 11) entsteht,
dadurch gekennzeichnet, dass der Wärmetauscher ferner eine Vielzahl gewellter Ausgleichsplatten (20) umfasst,
die fest aneinander befestigt sind, um einen Ausgleichsplattenstapel (21) zu bilden,
der zwischen den Wärmetauscherplatten (10, 11) und mindestens einer der Endplatten
(6, 7) angeordnet ist, wobei
a) die erste Endplatte (6) mit der Einlassöffnung (2) und der Auslassöffnung (3) versehen
ist und der Ausgleichsplattenstapel (21) fest an den Wärmetauscherplatten (10, 11)
auf einer Seite und an der Einlass- und Auslassöffnung (2, 3) der ersten Endplatte
(6) auf der anderen Seite befestigt ist, oder
b) die erste Endplatte (6) mit der Einlassöffnung (2) versehen ist und die zweite
Endplatte (7) mit der Auslassöffnung (3) versehen ist und der Ausgleichsplattenstapel
(21) fest an den Wärmetauscherplatten (10, 11) auf einer Seite und an der Einlassöffnung
(2) der ersten Endplatte (6) auf der anderen Seite befestigt ist, und dass ein weiterer
Ausgleichsplattenstapel (212) fest an den Wärmetauscherplatten (10, 11) auf einer
Seite und an der Auslassöffnung (3) der zweiten Endplatte (7) auf der anderen Seite
befestigt ist.
2. Wärmetauscher nach Anspruch 1, dadurch gekennzeichnet, dass der Mantel (8) kreisförmig ist.
3. Wärmetauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Muster einer Ausgleichsplatte (20) konzentrische Erhöhungen (18) und Rillen (19)
umfasst.
4. Wärmetauscher nach Anspruch 3, dadurch gekennzeichnet, dass der Flankenwinkel (α) der Ausgleichsplatten (20) kleiner ist als der Flankenwinkel
(β) der Wärmetauscherplatten (10, 11).
5. Wärmetauscher nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der Flankenwinkel (α) der Ausgleichsplatten (20) kleiner als 30 Grad ist.
6. Wärmetauscher nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Ausgleichsplatte (20) eine kreisförmige Öffnung (28) in der Mitte der Ausgleichsplatte
umfasst.
7. Wärmetauscher nach Anspruch 6, dadurch gekennzeichnet, dass zwei benachbarte Ausgleichsplatten (20) am äußeren Umfang (22) und am inneren Umfang
(27) der Ausgleichsplatte fest aneinander befestigt sind.
8. Wärmetauscher nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass die Ausgleichsplatte (20) eine Druckplatte (29) in der mittigen Öffnung (28) der
Ausgleichsplatte umfasst.
9. Wärmetauscher nach Anspruch 8, dadurch gekennzeichnet, dass die Ausgleichsplatte (20) und die Druckplatte (29) aneinander befestigt sind.
10. Wärmetauscher nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Wärmetauscherplatten und/oder die Ausgleichsplatten miteinander verschweißt sind.
11. Wärmetauscher nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Wärmetauscherplatten und/oder die Ausgleichsplatten miteinander verlötet sind.
1. Échangeur de chaleur (1), comprenant un boîtier (30) présentant une première plaque
terminale (6), une seconde plaque terminale (7) et une calandre (8), la première plaque
terminale (6) étant dotée d'un orifice d'entrée (2) et la première ou la seconde plaque
terminale (6, 7) étant dotée d'un orifice de sortie (3), et comprenant en outre une
pluralité de plaques d'échangeur de chaleur (10, 11) ondulées présentant des crêtes
(12) et des rainures (13), les plaques d'échangeur de chaleur étant attachées fixement
les unes aux autres, de sorte qu'un premier canal d'écoulement (14) est créé entre
les plaques d'échangeur de chaleur (10, 11),
caractérisé en ce que l'échangeur de chaleur comprend en outre une pluralité de plaques de compensation
(20) ondulées attachées fixement les unes aux autres pour former une pile (21) de
plaques de compensation positionnée entre les plaques d'échangeur de chaleur (10,
11) et au moins l'une des plaques terminales (6, 7), dans lequel
a) la première plaque terminale (6) est dotée de l'orifice d'entrée (2) et de l'orifice
de sortie (3), et la pile (21) de plaques de compensation est attachée fixement aux
plaques d'échangeur de chaleur (10, 11) d'un côté et aux orifices d'entrée et de sortie
(2, 3) de la première plaque terminale (6) de l'autre côté, ou
b) la première plaque terminale (6) est dotée de l'orifice d'entrée (2) et la seconde
plaque terminale (7) est dotée de l'orifice de sortie (3), et la pile (21) de plaques
de compensation est attachée fixement aux plaques d'échangeur de chaleur (10, 11)
d'un côté et à l'orifice d'entrée (2) de la première plaque terminale (6) de l'autre
côté, et qu'une autre pile (212) de plaques de compensation est attachée fixement
aux plaques d'échangeur de chaleur (10, 11) d'un côté et à l'orifice de sortie (3)
de la seconde plaque terminale (7) de l'autre côté.
2. Échangeur de chaleur selon la revendication 1, caractérisé en ce que la calandre (8) est circulaire.
3. Échangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que le motif d'une plaque de compensation (20) comprend des crêtes (18) et des rainures
(19) concentriques.
4. Échangeur de chaleur selon la revendication 3, caractérisé en ce que l'angle de flanc (α) des plaques de compensation (20) est plus petit que l'angle
de flanc (β) des plaques d'échangeur de chaleur (10, 11).
5. Échangeur de chaleur selon l'une quelconque des revendications 1 à 4, caractérisé en ce que l'angle de flanc (α) des plaques de compensation (20) est inférieur à 30 degrés.
6. Échangeur de chaleur selon l'une quelconque des revendications 1 à 5, caractérisé en ce que la plaque de compensation (20) comprend une ouverture circulaire (28) au centre de
la plaque de compensation.
7. Échangeur de chaleur selon la revendication 6, caractérisé en ce que deux plaques de compensation (20) adjacentes sont attachées fixement l'une à l'autre
au niveau de la périphérie extérieure (22) et de la périphérie intérieure (27) de
la plaque de compensation.
8. Échangeur de chaleur selon la revendication 6 ou 7, caractérisé en ce que la plaque de compensation (20) comprend une plaque d'appui (29) dans l'ouverture
centrale (28) de la plaque de compensation.
9. Échangeur de chaleur selon la revendication 8, caractérisé en ce que la plaque de compensation (20) et la plaque d'appui (29) sont attachées l'une à l'autre.
10. Échangeur de chaleur selon l'une quelconque des revendications 1 à 9, caractérisé en ce que les plaques d'échangeur de chaleur et/ou les plaques de compensation sont soudées
les unes aux autres.
11. Échangeur de chaleur selon l'une quelconque des revendications 1 à 9, caractérisé en ce que les plaques d'échangeur de chaleur et/ou les plaques de compensation sont brasées
les unes aux autres.