Patent Description:
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 as disclosed in the preamble of claim <NUM> are known, for example, from prior art documents <CIT>, <CIT>and <CIT>.

Some of these solutions, such as <CIT> and <CIT> 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 <CIT>, 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.

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

It is understood that elements and characteristics of one embodiment can conveniently be combined or incorporated into other embodiments without further clarifications.

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 <NUM>.

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

The circulation elements <NUM> 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>), preferably equidistant from each other along the positioning axis X.

According to some embodiments, not shown, the circulation elements <NUM> 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 <NUM>. The diameter of the tubes can be a few centimeters.

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

The channels <NUM> extend between a first end <NUM> and a second end <NUM> of the circulation element <NUM>.

Each channel <NUM> has a very small cross section for the passage of the fluid, for example comprised between <NUM>*<NUM>-<NUM> and <NUM> 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 <NUM>.

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

The channels <NUM> 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 <NUM> 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 <NUM> times greater than the thickness.

The circulation elements <NUM> 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 <NUM> adequate resistance to corrosion.

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

Each circulation element <NUM> can be disposed so that its first surface <NUM> faces the second surface <NUM> of the adjacent circulation element <NUM>.

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

The fins <NUM> are disposed along the oblong development of two adjacent circulation elements <NUM>, as shown in <FIG>, and can be defined by at least one substantially flat and rectangular sheet.

The plurality of fins <NUM> 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 <NUM> is defined by each of the bent segments of a sheet.

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

According to some embodiments, the recirculation means <NUM> can be fluidically connected to each circulation element <NUM> 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 <NUM>.

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

The recirculation means <NUM> can be associated with the first end <NUM> and with the second end <NUM> of each circulation element <NUM> and can comprise at least one or more tubular manifolds <NUM> fluidically connected to the circulation elements <NUM> (<FIG>).

According to some embodiments, the manifolds 20a, 20b can be configured as tubular-shaped bodies delimited by walls <NUM> 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 <NUM>.

In some embodiments, the passage cross section of the manifold <NUM> 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 <NUM> are not excluded.

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

In some embodiments, the recirculation means <NUM> comprise at least one feed pipe <NUM> and at least one recovery pipe <NUM>.

The feed pipe <NUM> can be fluidically associated with a manifold <NUM>.

The feed pipe <NUM> allows to put the recirculation means <NUM> in fluidic communication with a feed circuit <NUM> which, in some embodiments, can comprise a feed mean <NUM> disposed upstream of the feed pipe <NUM>.

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

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

The recovery pipe <NUM> can in turn be put in fluidic communication with the feed circuit <NUM>, upstream of the feed mean <NUM>.

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

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

Note that <FIG> show embodiments of the heat exchanger <NUM> without the dividing baffle <NUM>. In fact, in the above embodiments the recovery pipe <NUM> can be associated with another manifold 20b, not shown.

According to one aspect of the invention, the heat exchanger <NUM> can comprise damping means <NUM> which can be operatively associated with the manifolds <NUM> in order to damp pressure waves that characterize the flow of heat-carrier fluid.

In this case, the damping means <NUM> are configured to constitute a discontinuity with respect to the geometry of the manifold <NUM> 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 <NUM>. In fact, the damping means <NUM> 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 <NUM> as described here can be easily integrated into heat exchangers even in a step that follows their production.

In some embodiments, the damping means <NUM> comprise at least one distributor baffle <NUM> (<FIG>, <FIG> and <FIG>) which, in some embodiments, can be disposed transversely with respect to the longitudinal development of the manifold <NUM>, that is, transversely with respect to the positioning axis X.

Furthermore, the distributor baffle <NUM> 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 <NUM> (<FIG>). Preferably, the external perimeter 25a of the distributor baffle <NUM> is exactly mating with the shape of the cross section of the manifold <NUM> in which the baffle is installed.

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

The distribution holes <NUM> can be of any shape whatsoever and their cross section can be variable as a function of the thickness S of the distributor baffle <NUM> (<FIG> and <FIG>), that is, variable along the positioning axis X.

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

A distributor baffle can also comprise a plurality of different distribution holes <NUM> (<FIG>).

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

In this way, the distributor baffle <NUM>, in cooperation with the manifold <NUM>, can define one or more passage gaps <NUM> for the flow of heat-carrier fluid (<FIG>), through which the latter can flow in addition or as an alternative to the distribution holes <NUM>.

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

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

A person of skill in the art can easily understand that the shape and amount of distribution holes <NUM> and/or the passage gaps <NUM> can be designed and sized as a function of the overall geometry of the entire heat exchanger <NUM> 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 <NUM> can be disposed in a manifold <NUM> in the proximity of one of the end caps 28a, 28b.

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

As shown in <FIG> and <FIG>, the passage cross section of the manifold <NUM> is substantially free of damping means for most of its longitudinal extension, a distributor baffle <NUM> being provided only in the proximity of the end cap 28a. The absence of distributor baffles <NUM> in other positions improves the circulation of the heat-carrier fluid and the heat exchange efficiency of the heat exchanger <NUM>. 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 <NUM> can comprise a phase shifter unit <NUM> fluidically connected to a manifold <NUM>.

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

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

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

In other embodiments, a phase shift chamber <NUM> can be fluidically connected to at least one of the manifolds 20a, 20b by means of a first pipe <NUM> and a second pipe <NUM> (<FIG>), which respectively lead the fluid into the phase shift chamber <NUM> 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 <NUM>, specifically the definition of the cross section and its longitudinal development, depend on the geometry of the entire heat exchanger <NUM> 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 <NUM> or the second pipe <NUM> can be connected to one of the manifolds <NUM>, 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 <NUM> can comprise one or more distributor baffles <NUM> comprised in the manifolds 20a, 20b and at least one phase shift chamber <NUM> fluidically connected to one of the manifolds 20a, 20b by means of a single pipe <NUM> (<FIG>).

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

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

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

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

In other possible variants, the damping means <NUM> can comprise one or more protrusions <NUM>, <NUM>, <NUM> (<FIG>).

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

In other embodiments, the protrusions <NUM>, <NUM> can be associated with a dividing baffle <NUM> of a heat exchanger <NUM> (<FIG>) or with the walls <NUM> of the manifold <NUM>.

The protrusions <NUM>, <NUM>, <NUM> 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 <NUM>, <NUM>, <NUM> to attenuate the vibrations transmitted in the heat-carrier fluid. Furthermore, it is not excluded that the protrusions <NUM>, <NUM>, <NUM> can be associated with a distributor baffle <NUM> and/or with a phase shifter unit <NUM>.

In other embodiments, the damping means <NUM> can comprise elongated protrusions <NUM>, <NUM> which have an oblong development (<FIG>). The elongated protrusions <NUM>, <NUM> can develop inside a manifold <NUM> of the heat exchanger <NUM>.

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

In other embodiments, the elongated protrusions <NUM>, <NUM> can be associated with a dividing baffle <NUM> of a heat exchanger <NUM> (<FIG>) or with the walls <NUM> of the manifold <NUM>.

The elongated protrusions <NUM>, <NUM> 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 <NUM>, <NUM> to attenuate the vibrations transmitted in the heat-carrier fluid. Furthermore, it is not excluded that the elongated protrusions <NUM>, <NUM> can be associated with a distributor baffle <NUM> and/or with a phase shifter unit <NUM>, such as those described above.

In some embodiments, the external surface of the protrusions <NUM>, <NUM>, <NUM> and/or of the elongated protrusions <NUM>, <NUM> can be corrugated.

In possible variants, the damping means <NUM> can comprise one or more tubular elements <NUM> (<FIG>).

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

In other embodiments, a tubular element <NUM> can be associated with a dividing baffle <NUM> of a heat exchanger <NUM> or with the walls <NUM> of the manifold <NUM>.

In other embodiments, not shown, a tubular element <NUM> can be associated with a distributor baffle <NUM> and/or with a phase shifter unit <NUM>.

The tubular element <NUM> 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 <NUM> can be perforated laterally.

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

According to other variants, the damping means <NUM> can comprise mobile damper elements <NUM>, as in the example shown in <FIG>.

According to some embodiments, a mobile damper element <NUM> can be associated with at least one of the end caps 28a, 28b.

In other embodiments, not shown, the mobile damper element <NUM> can be associated with a dividing baffle <NUM> of a heat exchanger <NUM>, or with the walls <NUM> of the manifold <NUM>.

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

In some embodiments, a mobile damper element <NUM> can comprise a body operatively associated with the manifold <NUM> 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 <NUM> can comprise transverse protrusions <NUM>, <NUM>, <NUM> which protrude into a manifold <NUM> in a direction substantially transverse with respect to the longitudinal development thereof (<FIG>).

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 <NUM> can be made in such a way as to at least partly follow the perimeter development of the section of the manifold <NUM>.

In other embodiments, the damping means <NUM> can comprise an insert <NUM> associated with a manifold <NUM>.

In some embodiments, the insert <NUM> can constitute a structural discontinuity in the manifold <NUM>.

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

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

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

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

The bodies <NUM> 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 <NUM> can be configured as protruding portions 62a, 62b of the feed pipe <NUM> and/or of the recovery pipe <NUM> and/or of the circulation elements <NUM>, configured to protrude inside a manifold <NUM> 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 <NUM> comprise at least one membrane <NUM> operatively associated with a manifold <NUM> (<FIG>). The membrane <NUM> can be flexible and can be configured to absorb vibrations that are transmitted in the heat-carrier fluid.

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

The membrane <NUM> can be perforated and/or micro-perforated.

It is noted that all the embodiments of damping means <NUM> described are configured to constitute a geometric discontinuity in the manifold <NUM> so as to reduce the propagation of pulsations in the heat-carrier fluid circulating in the manifold <NUM>. 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 <NUM> as described heretofore, without departing from the field and scope of the present invention as defined by the claims.

Claim 1:
Heat exchanger (<NUM>) comprising circulation elements (<NUM>) fluidically connected to one or more manifolds (<NUM>) which are closed at the ends by respective end caps (28a, 28b), have a passage cross section for said heat-carrier fluid and are configured to feed a heat-carrier fluid in said circulation elements (<NUM>) and to collect said heat-carrier fluid at exit from said circulation elements (<NUM>), damping means (<NUM>) comprising at least one distributor baffle (<NUM>), wherein said damping means (<NUM>) are operatively associated with at least one of said manifolds (<NUM>) able to damp pressure waves which characterize the flow of heat-carrier fluid and modify their relative frequency and/or amplitude in order to prevent the occurrence of resonance phenomena, said heat exchanger (<NUM>) being characterized in that said at least one distributor baffle (<NUM>) is disposed only in the proximity of one of said end caps (28a, 28b) so that said passage cross section of said manifolds (<NUM>) is substantially free of damping means (<NUM>) for most of its longitudinal extension.