HEAT EXCHANGER

FIELD OF THE INVENTION

Embodiments described here concern a heat exchanger. In particular, a heat exchanger described in the present invention is suitable to promote the heat exchange between two fluids, of which at least one is a heat-carrier fluid which recirculates in the heat exchanger thanks to suitable feed means.

BACKGROUND OF THE INVENTION

Heat exchangers are known which comprise a plurality of circulation elements able to be passed through by fluids, such as for example cooling fluids.

These circulation elements usually comprise pipes or channels and have an oblong development. The pipes or channels are disposed parallel to each other and distributed over the width of the circulation element.

In particular, some circulation elements comprise a plurality of oblong pipes disposed parallel. Other circulation elements, on the other hand, appear as an oblong body with a flattened cross section inside which a plurality of parallel channels are made.

Furthermore, the circulation elements are located parallel to each other, and heat exchange fins can be attached between adjacent circulation elements.

In particular, the fins are attached on the external surfaces of the circulation elements to increase the useful heat exchange surface of the circulation elements.

The circulation elements are in turn connected, at their respective opposite ends, to manifolds, configured to be passed through by the heat-carrier fluid, which has to enter the circulation elements, or which has just come out of them.

The manifolds are therefore connected to at least one feed duct and a recovery duct respectively to introduce the heat-carrier fluid toward the heat exchanger, and recover it from the latter.

The manifolds, in turn, can be connected to a circuit, for example a cooling circuit, in which the same heat-carrier fluid is subjected to predefined thermodynamic cycles.

The circuit generally comprises a mean to feed the heat-carrier fluid which can be configured, for example, as a compressor or as a pump.

The mean to feed the heat-carrier fluid can modulate the parameters of the feed of the fluid (for example pressure or flow rate) based on the performances required of the heat exchanger.

This modulation can generate pressure waves in the heat-carrier fluid which can be transmitted in it with a certain frequency. The amplitude and frequency of the pressure waves may depend on the feed parameters (pressure and flow rate) and on the type of feed mean.

Heat exchangers of the known type as described above have some disadvantages.

A first disadvantage of known solutions is that vibrations of the heat exchanger can be generated, excited by possible resonances between the flow of the heat-carrier fluid and the structure of the exchanger itself. In fact, some amplitude and frequency values of the pressure waves as above may be such as to trigger a resonance with the vibration frequencies that are characteristic of the geometry of the heat exchanger or parts of it.

These vibrations may be transient and appear only during the modulation of the feed parameters, or they may be stationary and occur even when the feed parameters of the heat-carrier fluid are constant over time.

Another disadvantage is that this resonance between the feed mean and the structure of the exchanger can lead to a deterioration in the performance of the exchanger, interfering with the thermo-fluid dynamics of the entire apparatus.

This deterioration in performance can also lead to an energy inefficiency of the exchanger itself, which can cause an increase in polluting emissions linked to the functioning of the exchanger.

Another disadvantage is that this resonance between the feed mean and the structure of the exchanger can lead to the generation of noises which, in some cases, can be particularly annoying.

Another disadvantage is that the vibrations can lead to the breakage of components of the exchanger, causing a worsening of its performance.

Another disadvantage is that the vibrations can also be transmitted to other parts of the hydraulic circuit associated with the exchanger, causing malfunctions, inefficiency and in some cases breakages.

To try to overcome some of these disadvantages, some solutions known in the state of the art have been developed, which provide structural reinforcement elements to be disposed in the manifolds. Solutions of this type are known, for example, from prior art documents JP 2008/298349 A, US 2019/162488 A1 and JP S53 63771 U.

Some of these solutions, such as US 2019/162488 A1 and JP 55363771 U for example, provide to distribute the structural reinforcement elements homogeneously along the entire length of the manifold in order to define a suitable structural reinforcement for the latter.

Another solution, described by JP 2008/298349 A, provides to dispose a plate in the manifold, provided with a hole or an equivalent recess on one of the perimeter sides of the plate, which allows the passage of the fluid. The plate is located in a median position of symmetry of the manifold, which is important since it allows the plate to perform the function of a stiffening mean. In fact, in order to lighten as much as possible the weight of the exchanger described in this document, the walls of its structural components have reduced thicknesses and this means that the exchanger can be subject to resonance phenomena, generated by the mechanical lightening of the structure, with consequent vibrations that can cause damage to some components of the structure itself.

There is therefore a need to perfect a heat exchanger which can overcome at least one of the disadvantages of the state of the art.

In particular, one purpose of the present invention is to provide a heat exchanger that can at least limit, or even eliminate, the excitation of vibrations due to the resonance between the feed of the heat-carrier fluid and the structure of the exchanger itself.

Another purpose is to provide a heat exchanger that can reduce the noise pollution produced by said vibrations.

Another purpose of the present invention is to provide a heat exchanger that reduces the breakages due to the resonance phenomena between the feed of the heat-carrier fluid and the structure of the exchanger.

Yet another purpose of the present invention is to reduce or eliminate the transmission of said vibrations to other components of the circuit associated with the exchanger.

Another purpose is to perfect a heat exchanger which limits or completely prevents the worsening of its thermo-fluid dynamic performance due to vibrations.

Another purpose is to provide an exchanger which is more efficient from an energy point of view, less polluting, and more durable over time.

The Applicant has devised, tested and embodied the present invention to overcome the shortcomings of the state of the art and to obtain these and other purposes and advantages.

SUMMARY OF THE INVENTION

The present invention is set forth and characterized in the independent claim. The dependent claims describe other characteristics of the present invention or variants to the main inventive idea.

In accordance with the above purposes, a heat exchanger is described that overcomes the limits of the state of the art and eliminates the defects present therein.

In accordance with some embodiments, a heat exchanger is provided comprising at least one heat exchange unit and recirculation means fluidically connected to the unit.

The heat exchange unit comprises circulation elements which can be, for example but not limited to, of the type with “micro-channels”.

In some embodiments, the recirculation means comprise at least one tubular manifold with a cross section for the passage of a heat-carrier fluid.

The manifold is closed at its opposite ends by respective end caps and is fluidically connected to the circulation elements of the heat exchange unit, being configured to feed a heat-carrier fluid into the circulation elements and to collect the heat-carrier fluid at exit therefrom.

According to one aspect, the heat exchanger comprises clamping means operatively associated with at least one of the manifolds.

In some embodiments, the damping means are configured to dampen pressure waves that characterize the flow of heat-carrier fluid, and modify their relative frequency and/or amplitude in order to prevent the occurrence of resonance phenomena.

According to one aspect of the present invention, the damping means are disposed in the proximity of one of the end caps.

This position of the damping means is advantageous since it allows to achieve the effect of clamping the pressure waves, with the consequent modification of the relative frequency and/or amplitude of such waves, without significantly impacting the fluid-dynamic efficiency of the heat exchanger.

In some embodiments, the damping means comprise at least one distributor baffle disposed transversely inside the at least one manifold.

The distributor baffle can have a plan shape defined by an external perimeter and at least partly mating with the passage cross section of the manifold.

According to some embodiments, the distributor baffle comprises one or more through holes.

The through holes can have a cross section that varies as a function of the thickness of the distributor baffle.

According to other embodiments, the perimeter of the plan shape of the distributor baffle can partly differ from the passage cross section of the manifold in which it is disposed. In this way, the distributor baffle can define, in cooperation with the manifold, one or more passage gaps for the flow of the heat-carrier fluid.

According to other embodiments, the damping means can comprise a phase shifter unit fluidically connected to the recirculation means.

The phase shifter unit can comprise at least one phase shift chamber and at least one pipe configured to fluidically connect the phase shift chamber with a manifold.

The present invention also concerns an exchanger comprising a plurality of distributor baffles, even different from each other, and a plurality of phase shifter units both operatively associated with one or more manifolds.

In some embodiments, at least one manifold can be fluidically connected to a feed pipe for feeding a heat-carrier fluid. Furthermore, at least one manifold can be fluidically connected to a recovery pipe.

The clamping means as described here can be advantageously integrated in heat exchangers even in a step that follows their production.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other aspects, characteristics and advantages of the present invention will become apparent from the following description of some embodiments, given as a non-restrictive example with reference to the attached drawings wherein:

FIGS. 1 and 2 are schematic representations of longitudinal sections of two different embodiments of an exchanger according to the present invention;

FIG. 3 is a partial and schematic three-dimensional representation of another embodiment of a heat exchanger according to the present invention, in which some parts have been removed;

FIGS. 4, 5 and 6 are partial and schematic representations of cross sections of as many possible embodiments of a distributor baffle comprised in the heat exchanger according to the present invention;

FIGS. 7 to 10 are partial and schematic representations of longitudinal sections that show as many possible embodiments of clamping means comprised in the heat exchanger according to the present invention.

To facilitate comprehension, the same reference numbers have been used, where possible, to identify identical common elements in the drawings. It is understood that elements and characteristics of one embodiment can conveniently be combined or incorporated into other embodiments without further clarifications.

DETAILED DESCRIPTION OF SOME EMBODIMENTS

We will now refer in detail to the possible embodiments of the invention, of which one or more examples are shown in the attached drawings, by way of a non-limiting illustration. The phraseology and terminology used here are also for the purposes of providing non-limiting examples.

With reference to the attached drawings, the present invention concerns a heat exchanger, indicated as a whole with reference number 10.

The heat exchanger 10 comprises at least one heat exchange unit 11, hereafter unit 11, and recirculation means 12 fluidically connected to the unit 11. The unit 11 can comprise a plurality of circulation elements 13 having an oblong development along a longitudinal axis Z and distanced from each other.

The circulation elements 13 can be placed on planes P parallel to each other and disposed in succession along a positioning axis X perpendicular to the planes P (FIG. 3), preferably equidistant from each other along the positioning axis X.

According to some embodiments, not shown, the circulation elements 13 can comprise a plurality of different tubes distanced from each other in parallel along a transverse axis that defines the width of the circulation elements 13. The diameter of the tubes can be a few centimeters.

In other possible embodiments, the circulation elements 13 can be configured as substantially flat elements each incorporating a plurality of channels 14 in a single body (FIG. 3).

The channels 14 extend between a first end 15 and a second end 16 of the circulation element 13.

Each channel 14 has a very small cross section for the passage of the fluid, for example comprised between 5*10⁻⁵and 20 square millimeters. For this reason, the channels in question are also called “micro-channels” and consequently, by extension, we speak of a “micro-channel” unit 11.

In some embodiments, the channels 14 can be distanced from each other in parallel along a transverse axis Y (FIG. 3) which defines the direction of the width of the circulation elements 13.

The channels 14 can have a shape of the cross section for the passage of the fluid that is rectangular, circular, semicircular, although other geometric shapes are not excluded.

The circulation elements 13 can have a shape of the cross section that is substantially flat, that is, in which the width is greater than the thickness, for example at least 5 times greater than the thickness.

The circulation elements 13 can be made of a thermally conductive material, such as a metal material, for example selected from a group comprising aluminum or its alloys, stainless steel, or copper. The choice of these materials also allows to give the elements 13 adequate resistance to corrosion.

In some embodiments, the circulation elements 13 can be provided with a first surface 17 and a second surface 18 at least one of which, usually both, is in direct contact with a plurality of fins 19.

Each circulation element 13 can be disposed so that its first surface 17 faces the second surface 18 of the adjacent circulation element 13.

The circulation elements 13 can be distanced from each other by the plurality of fins 19 which can be integrally attached to the circulation elements 13, for example by welding, more specifically by brazing.

The fins 19 are disposed along the oblong development of two adjacent circulation elements 13, as shown in FIGS. 1-3, and can be defined by at least one substantially flat and rectangular sheet.

The plurality of fins 19 can be obtained from a sheet, suitably corrugated or bent in a zig zag manner according to a homogeneous development in order to define the heat exchange surfaces.

In other words, each fin 19 is defined by each of the bent segments of a sheet.

The fins 19 can be disposed adjacent to each other and transverse with respect to the axis Z of longitudinal development of the circulation elements 13.

According to some embodiments, the recirculation means 12 can be fluidically connected to each circulation element 13 in order to circulate a heat-carrier fluid.

With the term circulation we mean both the feed and also the collection of the heat-carrier fluid in the circulation elements 13.

In this way, it can be provided that the recirculation means 12 allow the circulation of the heat-carrier fluid in the circulation elements 13.

The recirculation means 12 can be associated with the first end 15 and with the second end 16 of each circulation element 13 and can comprise at least one or more tubular manifolds 20 fluidically connected to the circulation elements 13 (FIG. 3).

According to some embodiments, the manifolds 20a, 20b can be configured as tubular-shaped bodies delimited by walls 29 which develop parallel to the positioning axis X, and which have a cross section for the passage of a heat-carrier fluid.

Each manifold 20a, 20b can be closed, or “capped”, at the ends by means of end caps 28a, 28b, by means of welding, preferably brazing.

The caps 28a, 28b, or “end caps”, can be configured as plates having a plan shape substantially similar to the passage cross section of the manifold 20.

In some embodiments, the passage cross section of the manifold 20 is circular. In other embodiments, the passage section is in the shape of a “D”. However, other shapes for the passage cross section of the manifold 20 are not excluded.

According to some embodiments, a heat exchanger 10 according to the present invention can comprise a first manifold 20a and a second manifold 20b, both associated respectively with the first end 15 and with the second end 16 of the circulation elements 13, or vice versa.

In some embodiments, the recirculation means 12 comprise at least one feed pipe 40 and at least one recovery pipe 41.

The feed pipe 40 can be fluidically associated with a manifold 20.

The feed pipe 40 allows to put the recirculation means 12 in fluidic communication with a feed circuit 22 which, in some embodiments, can comprise a feed mean 23 disposed upstream of the feed pipe 40.

The feed mean 23 can be any known device whatsoever suitable to generate a flow of heat-carrier fluid. For example, the feed mean 23 can be a compressor or a pump.

The recovery pipe 41 can be fluidically connected to a manifold 20 and can be configured to collect the heat-carrier fluid at exit from the circulation elements 13.

The recovery pipe 41 can in turn be put in fluidic communication with the feed circuit 22, upstream of the feed mean 23.

In some embodiments, the feed pipe 40 can be associated with the first manifold 20a and the recovery pipe 41 can be associated with the second manifold 20b, or vice versa.

Referring to FIGS. 1 and 2, both the feed pipe 40 and also the recovery pipe 41 can be fluidically connected to a manifold 20. In particular, in these embodiments the manifold 20a can also comprise a dividing baffle 24, interposed between the inlet of the feed pipe 40 and the inlet of the recovery pipe 41. More in particular, the dividing baffle 24 defines two fluidically separated portions in the manifold 20a. A plane containing the dividing baffle 24 and parallel to the axes Y and Z can be called the flow inversion plane A (FIG. 3).

Note that FIGS. 9 and 10 show embodiments of the heat exchanger 10 without the dividing baffle 24. In fact, in the above embodiments the recovery pipe 41 can be associated with another manifold 20b, not shown.

According to one aspect of the invention, the heat exchanger 10 can comprise clamping means 21 which can be operatively associated with the manifolds 20 in order to clamp pressure waves that characterize the flow of heat-carrier fluid.

In this case, the damping means 21 are configured to constitute a discontinuity with respect to the geometry of the manifold 20 with which they are associated, preventing the excitation of vibrations due to the resonance between the flow of heat-carrier fluid and the structure of the entire heat exchanger 10. In fact, the damping means 21 can modify the frequency and/or the amplitude of the pressure waves that pass through the heat-carrier fluid.

Another advantage of the present invention consists in the fact that the damping means 21 as described here can be easily integrated into heat exchangers even in a step that follows their production.

In some embodiments, the damping means 21 comprise at least one distributor baffle 25 (FIGS. 1, 2 and 3) which, in some embodiments, can be disposed transversely with respect to the longitudinal development of the manifold 20, that is, transversely with respect to the positioning axis X.

Furthermore, the distributor baffle 25 can be configured as a flat body with a thickness S and a plan shape at least partly mating with the passage cross section of at least one of the manifolds 20 (FIGS. 4, 5 and 6). Preferably, the external perimeter 25a of the distributor baffle 25 is exactly mating with the shape of the cross section of the manifold 20 in which the baffle is installed.

According to some embodiments, the distributor baffle 25 can comprise one or more through distribution holes 26 that pass through it.

The distribution holes 26 can be of any shape whatsoever and their cross section can be variable as a function of the thickness S of the distributor baffle 25 (FIGS. 1 and 2), that is, variable along the positioning axis X.

As shown in FIGS. 1 and 2, in some embodiments the distribution holes 26 can have a conical development as a function of the thickness S. In other embodiments, the distribution holes 26 can have a development along the axis X which provides a narrowing of the section of the hole 26 followed by a widening of the section.

A distributor baffle can also comprise a plurality of different distribution holes 26 (FIG. 6).

According to other embodiments, the plan shape of the distributor baffle 25 can partly differ from the passage cross section of the baffle 20 with which it is associated.

In this way, the distributor baffle 25, in cooperation with the manifold 20, can define one or more passage gaps 27 for the flow of heat-carrier fluid (FIGS. 4, 5 and 6), through which the latter can flow in addition or as an alternative to the distribution holes 26.

The distribution holes 26 and/or the passage gaps 27 are configured to allow the heat-carrier fluid flowing in the manifold 20 to pass from one side to the other of the distributor baffle 25.

In other embodiments, the heat exchanger 10 can comprise a plurality of distributor baffles 25, possibly disposed in different positions inside the one or more manifolds 20. The distributor baffles 25 can also be different from each other, that is, they can comprise distribution holes 26 and/or define passage gaps 27 that differ from one distributor baffle 25 to another.

A person of skill in the art can easily understand that the shape and amount of distribution holes 26 and/or the passage gaps 27 can be designed and sized as a function of the overall geometry of the entire heat exchanger 10 and of the thermo-fluid dynamic characteristics of the flow of heat-carrier fluid which, during use, will flow inside it.

In preferred embodiments, a distributor baffle 25 can be disposed in a manifold 20 in the proximity of one of the end caps 28a, 28b.

In particular, in some embodiments, at least one circulation element 13 is disposed between at least one of the end caps 28a, 28b and a distributor baffle 25. More preferably, only one circulation element 13 is disposed between at least one of the end caps 28a, 28b and the distributor baffle 25.

As shown in FIGS. 1 and 2, the passage cross section of the manifold 20 is substantially free of clamping means for most of its longitudinal extension, a distributor baffle 25 being provided only in the proximity of the end cap 28a. The absence of distributor baffles 25 in other positions improves the circulation of the heat-carrier fluid and the heat exchange efficiency of the heat exchanger 10. This is advantageous, especially if one considers that the solutions known in the state of the art need to dispose such distributor baffles either in a median zone of the manifold equidistant from its opposite ends or along the entire manifold, in order to guarantee the necessary structural reinforcement action of the manifold itself.

According to another aspect of the invention, the damping means 21 can comprise a phase shifter unit 30 fluidically connected to a manifold 20.

In some embodiments, the phase shifter unit 30 can comprise a phase shift chamber 31 which can be configured as a tubular body generally defined by a cross section and a longitudinal development.

The phase shift chamber 31 can be configured to receive at least part of the flow of heat-carrier fluid which flows in the manifold 20 with which it is associated.

According to some embodiments, a phase shift chamber 31 can be fluidically connected to at least one of the manifolds 20a, 20b by means of a single pipe 32 (FIG. 1) through which the fluid enters and exits the phase shift chamber 31.

In other embodiments, a phase shift chamber 31 can be fluidically connected to at least one of the manifolds 20a, 20b by means of a first pipe 33 and a second pipe 34 (FIG. 2), which respectively lead the fluid into the phase shift chamber 31 and evacuate the fluid therefrom.

A person of skill in the art can easily understand that the sizing and design of the phase shift chamber 31, specifically the definition of the cross section and its longitudinal development, depend on the geometry of the entire heat exchanger 10 and on the thermo-fluid dynamic characteristics of the flow of heat-carrier fluid which, during use, will flow inside it.

According to some embodiments, one of either the first pipe 33 or the second pipe 34 can be connected to one of the manifolds 20, 20b above the flow inversion plane A, and the other pipe can be connected to the same manifold below of the flow inversion plane A.

In some embodiments, a heat exchanger 10 can comprise one or more distributor baffles 25 comprised in the manifolds 20a, 20b and at least one phase shift chamber 31 fluidically connected to one of the manifolds 20a, 20b by means of a single pipe 32 (FIG. 1).

In other embodiments, a heat exchanger 10 can comprise one or more distributor baffles 25 comprised in the manifolds 20a, 20b and at least one phase shift chamber 31 fluidically connected to one of the manifolds 20a, 20b by means of a first pipe 33 and a second pipe 34 (FIG. 2).

In other embodiments, not shown, a heat exchanger 10 can comprise a phase shift chamber 31 fluidically connected to one of the manifolds 20a, 20b by means of one or more pipes and be without distributor baffles 25. In these embodiments, the phase shift function is performed exclusively by the phase shift chamber 31.

According to other embodiments, a heat exchanger 10 can comprise one or more distributor baffles 25 comprised in the manifolds 20 and a plurality of phase shift chambers 31 fluidically connected to at least one manifold 20.

A person of skill in the art will easily understand that the disposition and number of the distributor baffles 25 and of the phase shift chambers 31 depend on the geometric characteristics of the entire heat exchanger 10 and on the thermo-fluid dynamic characteristics of the flow of heat-carrier fluid flowing through it.

In other possible variants, the damping means 21 can comprise one or more protrusions 50, 53, 54 (FIGS. 7 and 8).

In some embodiments, the protrusions 50 can be associated with at least one of the end caps 28a, 28b of a manifold 20 and can project toward the inside of the manifold 20 itself (FIG. 7), or be associated with the walls 29 of the manifold 20.

In other embodiments, the protrusions 53, 54 can be associated with a dividing baffle 24 of a heat exchanger 10 (FIG. 8) or with the walls 29 of the manifold 20.

The protrusions 50, 53, 54 can be, for example but not limited to, of a conical shape, of a hemispherical shape, of a truncated conical or pyramidal shape. However, we do not exclude other shapes that can allow the protrusions 50, 53, 54 to attenuate the vibrations transmitted in the heat-carrier fluid. Furthermore, it is not excluded that the protrusions 50, 53, 54 can be associated with a distributor baffle 25 and/or with a phase shifter unit 30.

In other embodiments, the damping means 21 can comprise elongated protrusions 51, 56 which have an oblong development (FIGS. 7 and 9). The elongated protrusions 51, 56 can develop inside a manifold 20 of the heat exchanger 10.

In some embodiments, the elongated protrusions 51, 56 can be associated with at least one of the end caps 28a, 28b of a manifold 20 and can protrude toward the inside of the manifold 20 itself (FIG. 9).

In other embodiments, the elongated protrusions 51, 56 can be associated with a dividing baffle 24 of a heat exchanger 10 (FIG. 7) or with the walls 29 of the manifold 20.

The elongated protrusions 51, 56 can be substantially cylindrical in shape, but also have a truncated cone, conical or pyramidal shape. However, we do not exclude other shapes that can allow the elongated protrusions 51, 56 to attenuate the vibrations transmitted in the heat-carrier fluid. Furthermore, it is not excluded that the elongated protrusions 51, 56 can be associated with a distributor baffle 25 and/or with a phase shifter unit 30, such as those described above.

In some embodiments, the external surface of the protrusions 50, 53, 54 and/or of the elongated protrusions 51, 56 can be corrugated.

In possible variants, the damping means 21 can comprise one or more tubular elements 52 (FIG. 8).

According to some embodiments, a tubular element 52 can be associated with at least one of the end caps 28a, 28b.

In other embodiments, a tubular element 52 can be associated with a dividing baffle 24 of a heat exchanger 10 or with the walls 29 of the manifold 20.

In other embodiments, not shown, a tubular element 52 can be associated with a distributor baffle 25 and/or with a phase shifter unit 30.

The tubular element 52 can have a circular or oval section. However, other types of section are not excluded such as, for example, but not limited to, a square, rectangular or polygonal section and others.

In some embodiments, the tubular element 52 can be perforated laterally.

The presence of a plurality of tubular elements 52, possibly operatively interconnected, for example disposed concentric with each other, is not excluded.

According to other variants, the damping means 21 can comprise mobile clamper elements 55, as in the example shown in FIG. 9.

According to some embodiments, a mobile clamper element 55 can be associated with at least one of the end caps 28a, 28b.

In other embodiments, not shown, the mobile damper element 55 can be associated with a dividing baffle 24 of a heat exchanger 10, or with the walls 29 of the manifold 20.

In other embodiments, not shown, the mobile damper element 55 can be associated with a distributor baffle 25 and/or with a phase shifter unit 30, such as those described above.

In some embodiments, a mobile damper element 55 can comprise a body operatively associated with the manifold 20 by means of elastic means. The body can capture the pressure pulsations transmitted in the heat-carrier fluid and transmit them to the elastic means configured to absorb the pulsations.

According to other possible variants, the damping means 21 can comprise transverse protrusions 57, 58, 59 which protrude into a manifold 20 in a direction substantially transverse with respect to the longitudinal development thereof (FIG. 10).

In some embodiments, the transverse protrusions can be configured as a single protrusion or as a series of successive protrusions. Furthermore, in some embodiments, the transverse protrusions 58 can be made in such a way as to at least partly follow the perimeter development of the section of the manifold 20.

In other embodiments, the damping means 21 can comprise an insert 60 associated with a manifold 20.

In some embodiments, the insert 60 can constitute a structural discontinuity in the manifold 20.

According to some embodiments, the insert 60 can be configured as a portion of the manifold 20 made of a different material than that with which the manifold 20 is made, and which develops in continuity with the walls 29.

In some embodiments, an insert 60 can be made of plastic, polymer, elastoplastic, metal, ceramic material, of rubber or synthetic or natural fibers.

According to other embodiments, the insert 60 can be configured as a portion of the manifold 20 in which there is provided a geometric variation thereof. According to a non-limiting example, the insert 60 can have an annular shape and can have a different thickness, greater or lesser, than the thickness of the walls 29 of a manifold 20.

In other embodiments, the damping means can comprise free or semi-free bodies 61, for example retained by a cable, contained in a manifold 20 of a heat exchanger.

The bodies 61 can be of a shape and/or of materials such as to allow a reduction of the vibrations that are transmitted in the heat-carrier fluid in which they are immersed.

In accordance with other possible variants, the damping means 21 can be configured as protruding portions 62a, 62b of the feed pipe 40 and/or of the recovery pipe 41 and/or of the circulation elements 13, configured to protrude inside a manifold 20 so as to constitute a discontinuity in the geometry thereof.

According to some embodiments, one or more holes can be made in the protruding portions 62a, 62b.

In other embodiments, the damping means 21 comprise at least one membrane 63 operatively associated with a manifold 20 (FIG. 8). The membrane 63 can be flexible and can be configured to absorb vibrations that are transmitted in the heat-carrier fluid.

In some embodiments, the membrane 63 can be of plastic or polymer material, of fabric, non-woven fabric, rubber and suchlike.

The membrane 63 can be perforated and/or micro-perforated.

It is noted that all the embodiments of damping means 21 described are configured to constitute a geometric discontinuity in the manifold 20 so as to reduce the propagation of pulsations in the heat-carrier fluid circulating in the manifold 20. Therefore, modifications to the embodiments described and/or their combinations are not excluded.

It is clear that modifications and/or additions of parts may be made to the heat exchanger 10 as described heretofore, without departing from the field and scope of the present invention as defined by the claims.

In the following claims, the sole purpose of the references in brackets is to facilitate reading: they must not be considered as restrictive factors with regard to the field of protection claimed in the specific claims.

HEAT EXCHANGER

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