Storage Exchanger Provided With Storage Material, And Air Conditioning Loop Or Cooling Circuit Including Such A Heat Exchanger

Abstract

The invention relates to a storage heat exchanger (12, 12′) including at least one first flow tube (25) and one second flow tube (25) for a heat transfer fluid that respectively include a first end (26) leading into a first manifold (27) and a second end (28) leading into a second manifold (29), the first and second flow tubes (25) being placed adjacent to one another. The storage heat exchanger also includes at least one insert (30) positioned between the first flow tube (25) and the second flow tube (25), the insert (30) consisting of a plurality of blades (31) comprising a first edge (32) contacting the first flow tube (25) and a second edge (33) contacting the second flow tube (25), at least one interstitial space (35) being defined between the insert (30) and the flow tubes (25). The interstitial space (35) is filled with a material for storing calories or frigories.

Description

This invention belongs to the field of heat exchangers meant to be installed on an air conditioning loop and/or cooling circuit working with the heating, ventilation, and/or air conditioning equipment of an automotive vehicle constituting, by working together, a heating, ventilation, and/or air conditioning system. This invention relates to a storage heat exchanger as well as an air conditioning loop and/or cooling circuit including such a heat exchanger.

An automotive vehicle is currently equipped with heating, ventilation, and/or air conditioning equipment to regulate the aerothermal parameters by at least providing distribution of air flow inside the passenger compartment of an automotive vehicle. The heating, ventilation, and/or air conditioning equipment is principally constituted of a case, generally of a plastic material, housed under the dashboard of the vehicle. The case ensures channelization and movement of at least one flow of air prior to its distribution into the passenger compartment.

The heating, ventilation, and/or air conditioning equipment works with a main air conditioning loop to cool the flow of air prior to its distribution out of the case housing the heating, ventilation, and/or air conditioning equipment to the passenger compartment. The main air conditioning loop includes a plurality of elements, in particular a compressor, able to compress refrigeration fluid circulating inside the air conditioning loop, and an evaporator, over which a flow of air may cross in order to perform the heat exchange and cool the air.

The main air conditioning loop may possibly work with a secondary air conditioning loop arranged in such a way to allow a heat exchange with the main air conditioning loop. A secondary heat transfer fluid circulates inside the secondary air conditioning loop. For example, the secondary heat transfer fluid is constituted by a mixture of water and glycol.

The installation of a heat exchanger on the secondary air conditioning loop which is capable to store units of cold is known. This type of heat exchanger is constituted by a cold reserve, formed when the main air conditioning loop is in operation, and restored when the main air conditioning loop is stopped. This scenario is produced in particular when the vehicle is equipped with an automatic system to stop the compressor of the main air conditioning loop, especially after stopping the vehicle.

The heating, ventilation, and/or air conditioning equipment also works together with the main cooling circuit of the engine vehicle, which may interchangeably be thermal, electrical or hybrid. The main cooling circuit includes a pump to circulate a coolant inside the main cooling circuit. The main cooling circuit also includes a heating radiator which is crossed by the flow of air to allow warming of the latter prior to its distribution to the inside of the passenger compartment.

The main cooling circuit may possibly work with a secondary cooling circuit arranged in such a way to allow a heat exchange with the main cooling circuit. A second secondary heat transfer fluid circulates inside the secondary cooling circuit. For example, the secondary heat transfer fluid is made up of a mixture of water and glycol.

Installation of a heat exchanger enabled for storing calories on the main cooling circuit and/or on the secondary cooling circuit is also known. Said heat exchanger is built with a heat reservoir, formed when the main cooling circuit is working, and is restored when the main cooling circuit is stopped. This scenario is produced in particular when the vehicle is equipped with an automatic system to stop the main cooling circuit pump, especially after stopping the vehicle.

In all the cases mentioned above, the heat exchanger comprising a plurality of flow tubes containing heat transfer fluid, the ends of said tubes opening into the manifolds, and the reservoirs containing the material which stores heat in contact with the tubes are arranged in such a way that the storage material and the heat transfer fluid may exchange heat. As an example we may refer to French patent applications FR 2,878,613 and FR 2,878,614 which describe this type of heat exchangers.

However, currently known heat exchangers comprising reservoirs for heat storage material deserve to be improved in order to optimize comfort by keeping the user of the vehicle warm, even when the motor of the vehicle is stopped.

In fact, the concept of an evaporator including reservoirs for heat storage material quickly reaches its physical limit. Notably, the presence of the reservoirs for heat storage material resulted in a decrease in the exchange surface with the flow of air passing through the evaporator.

In addition, this type of evaporator requires a reduction in the quantity of heat storage material in the tubes in order to not increase disproportionately the dimensions of the evaporator.

Lastly, these evaporators have deterioration in their overall exchange coefficient.

It is thus desirable to optimize the size of the heat exchanger so that it will be the same and have better efficiency with respect to the heat exchanger with which it works, while minimizing the footprint provided by the heat exchanger.

Finally, it was found that a significant amount of calories or units of cold, particularly between 200 kJ and 270 kJ, may be quickly stored, notably within a period of less than two minutes.

The purpose of this invention is to propose a heat exchanger able to solve the previously mentioned disadvantages.

In particular, the storage exchanger, according to this invention, is suitable for installation on a secondary air conditioning loop or on the main cooling circuit, said storage exchanger having a small footprint, while obtaining an optimized thermal efficiency, notably allowing the storage of between 200 kJ and 270 kJ in less than two minutes, for temperature and output of a heat transfer fluid circulating inside the heat exchanger which are relatively unspecified, and more particularly for a coolant temperature of around 3° C. and a heat transfer fluid output of around 1000 1/hr.

The exchanger of this invention is a storage exchanger, comprising at least a first and a second tube for the circulation of heat transfer fluid. Each tube respectively includes a first end opening into a first manifold and a second end opening into a second manifold. The first and second flow tubes are placed adjacent to each other. At least one insert in between the first flow tube and the second flow tube. Each insert is made up of a plurality of blades comprising a first edge in contact with the first flow tube and a second edge in contact with the second flow tube. At least one interstitial space is established between the insert and the flow tubes. According to this invention, the interstitial space is filled with a material for storing calories or units of cold.

Preferably, the blades of the insert have spaces between them at the blading pitch (Pa). The blading pitch (Pa) falls between 0.4 mm and 0.75 mm. Preferably the blading pitch (Pa) will fall between 0.4 mm and 0.7 mm, especially between 0.4 mm and 0.6 mm, and specifically around 0.5 mm.

The length of each blade will advantageously be at a length (La) falling between 5 mm and 8 mm and the thickness (Ea) of the blades between 0.4 mm and 0.12 mm.

The length of each tube will advantageously be at a length (Lt) falling between 270 mm and 360 mm and the height (Ht) between 1.2 mm and 1.3 mm.

The space between two adjacent tubes should advantageously be of a tube pitch (Pt) of between 7 mm and 9 mm. The width of each tube (Et) will advantageously be between 0.2 mm and 0.25 mm.

The height (Hc) of each manifold should advantageously fall between 10 mm and 14 mm.

The depth (Pe) of the heat exchanger will advantageously fall between 20 mm and 35 mm, the width (Le) of the exchanger should be between 300 mm and 400 mm, total width (Lte) of the exchanger should be between 250 mm and 300 mm and the usable width (Lue) of the exchanger should fall between 235 mm 275 mm.

The other characteristics and advantages of the invention will become apparent by examining the description below in the attached drawings, give as non-restrictive examples, which may be used to supplement understanding of this invention and the presentation of its embodiment, but also, where appropriate, to contribute to its definition, of which:

FIGS. 1 and 2 show two variations of the respective embodiments of an air conditioning loop including a heat exchanger, according to this invention,

FIG. 3 illustrates a cooling circuit including a heat exchanger according to this invention,

FIG. 4 shows a surface view of an exchanger according to this invention and is presented in diagram form in FIGS. 1 to 3,

FIG. 5 is a partial view of an insert component of the heat exchanger according to this invention illustrated in the previous Figure,

FIG. 6 is a detailed view illustrating a component blade of the insert shown in the previous Figure,

FIG. 7 is a partial view of the heat exchanger illustrated in FIGS. 1 to 4 representing a cover plate component of the heat exchanger according to this invention,

FIG. 8 shows the evolution of the temperature of the storage material component of the heat exchanger according to this invention as a function of time, and

FIG. 9 shows the evolution of the energy stored by the heat exchanger according to this invention as a function of time.

In a known manner, an automotive vehicle is equipped with heating, ventilation, and/or air conditioning equipment to regulate the aerothermal parameters by at least providing distribution of air flow (1) inside the passenger compartment of the vehicle. The heating, ventilation, and/or air conditioning equipment is mainly comprised of a case constituted of an enclosure made of plastic material in which are placed various components of a heating circuit for the air flow (1) and channeling the air flow (1) prior to its distribution in the passenger compartment.

A motorized fan group placed at the entrance of the heating, ventilation, and air conditioning equipment case introduces the air flow (1) coming from outside the vehicle and/or the passenger compartment, into the heating circuit, to be heat treated.

This invention is of application within the context of cold unit storage, i.e., the thermal energy contained in a fluid called “cold”. FIGS. 1 and 2 show such an arrangement in accordance with two variants of respective embodiments of an air conditioning loop.

In a general fashion, the heating, ventilation, and/or air conditioning equipment works with a main air conditioning loop (2) in order to constitute a heating, ventilation, and/or air conditioning installation. Refrigerant fluid travels through the main air conditioning loop (2). The air conditioning loop allows circulation of the refrigerant fluid so that it may undergo a defined thermodynamic cycle. The refrigerant fluid may be a supercritical fluid, in particular carbon dioxide or a sub-critical fluid, such as R134a or similar fluid, or any other alternative fluid.

The main air conditioning loop (2) is arranged so that the refrigerant fluid successively travels through a compressor (3), a release mechanism (4), and an evaporator (5). Consequently the refrigerant fluid returns to the compressor (3).

The evaporator (5) ensures heat exchange between the refrigerant fluid and the air flow (1) which crosses through it. The air flow (1) is dehumidified and cooled by crossing through an evaporator (5) prior to its dispersion inside the passenger compartment of the vehicle. The passenger compartment is an area of the vehicle inside which at least one vehicle user is seated.

The heating, ventilation, and/or air conditioning case also includes a radiator, (not shown in FIGS. 1 and 2), capable of warming the air flow (1) and which forms part of an engine cooling system, in particular a heat-producing engine which makes propulsion of the vehicle possible. This type of radiator may correspond to the exchanger (13′) as seen in FIG. 4.

FIG. 1 is more in particular representative of the main air conditioning loop (2) in which the refrigerant fluid is a sub-critical fluid, such as R134a or similar fluid. In this case, the main air conditioning loop (2) also includes a condenser (6) placed on the main air conditioning loop (2) between the compressor (3) and the release mechanism (4) according to the direction of the refrigerant fluid circulation (8) inside the main air conditioning loop (2).

FIG. 2 is more in particular representative of the main air conditioning loop (2) in which the refrigerant fluid is a sub-critical fluid, such as R744 or similar fluid. In this case, the main air conditioning loop (2) also includes a gas cooler (7) placed on the main air conditioning loop (2) between the compressor (3) and the internal heat exchanger (9) placed upstream from the release mechanism (4) according to the direction of the refrigerant fluid circulation (8) inside the main air conditioning loop (2).

In accordance with the two examples of embodiments described with respect to FIGS. 1 and 2, the main air conditioning loop works with a secondary loop (10).

A secondary heat transfer fluid circulates inside the secondary loop (10). The secondary loop (10) includes a storage exchanger (12) intended for the accumulation of cold units in order to subsequently be reconstituted if needed, and a secondary circulation pump (11) (preferably an electrical pump), allowing circulation of the secondary heat transfer fluid within the secondary loop (10).

The main air conditioning loop (2) and the secondary loop (10) work together through a heat exchange device. In a particularly advantageous manner, the heat exchange device is constituted by the evaporator (5).

The heat exchange device, preferably, the evaporator (5), allows the transfer of heat between the refrigerant fluid circulating inside the main air conditioning loop (2) and the secondary heat transfer fluid circulating inside the secondary loop (10).

In accordance with an alternative embodiment, the secondary loop (10) includes a return exchanger (13) placed downstream from the storage exchanger (12) in the direction of the secondary heat transfer fluid circulation (8′).

For example, the secondary heat transfer fluid is constituted by a mixture of 50% to 70% water and respectively 50% to 30% glycol.

The return exchanger (13) makes it possible to reconstitute the cold units stored in the storage exchanger (12) when the main air conditioning loop (2) is stopped. In a particularly advantageous manner, the return exchanger (13) is crossed by the air flow (1). The air flow (1) is cooled by passing through the return exchanger (13) prior to the distribution of the latter to the inside of the passenger compartment of the vehicle.

In an alternative or complementary fashion, the evaporator (5) also contributes to the reconstitution of the cold units stored in the storage exchanger (12) when the main air conditioning loop (2) is stopped.

In order to allow implementation of the reconstitution of the calories stored in the storage exchanger (12), the secondary heat transfer fluid is put into circulation by the secondary circulation pump (11). In an advantageous fashion, the secondary circulation pump (11) functions as the main air conditioning loop (2) whether it is stopped or working.

It is possible, however, to allow the secondary circulation pump (11) to stop when the storage capacity of the storage exchanger (12) is reached in order to optimize consumption, especially electrical, of the heating, ventilation and/or air conditioning installation.

In the examples of embodiments described in FIGS. 1 and 2, a system for exchanging heat is provided allowing the exchange of heat between the main air conditioning loop (2) and the secondary loop (10) performed by the evaporator (5). According to these two examples, the evaporator (5) is of the tri-fluid type, in particular of the air/refrigerant fluid/secondary heat transfer fluid type.

However, the heat exchange device which allows an exchange of heat between the main air conditioning loop (2) and the secondary loop (10) according to this invention may be performed by a heat exchanger of the bi-fluid type, particularly of the refrigerant fluid/secondary heat transfer fluid type. During the use of this type of bi-fluid heat exchanger, only the return exchanger (13) is crossed by the cooled air flow (1) which it crossed prior to the distribution of the latter to the inside of the passenger compartment of the vehicle.

This invention also finds application within the context of calorie storage, i.e., the thermal energy contained in a fluid called “hot”. FIG. 3 illustrates such an embodiment and shows a cooling circuit including respectively a heat exchanger according to this invention.

To warm the air flow (1), the heating, ventilation, and/or air conditioning equipment houses a heating radiator (13′) which works with a main cooling circuit (15) of the vehicle motor (M), and is interchangeably thermal, electrical or hybrid, and which ensures propulsion of the vehicle.

A heat transfer fluid coolant circulates inside the main cooling circuit (15) to dispel the heat produced by the engine (M) as well as to provide cooling. To this end, the heat transfer fluid for cooling is put into circulation in the main cooling circuit (15) through a main circulation pump (19), driven by the engine (M).

For example, the heat transfer coolant is constituted by a coolant, composed of a mixture of 50% to 70% water and 50% to 30% glycol.

To ensure heating of the air flow (1), the main cooling circuit (15) includes a main valve switch (17) used to direct the heat transfer coolant to a cooling branch (15′) with a cooling radiator (14) crossed by the air flow (1′). The cooling radiator (14) is placed in front area of the vehicle through which the air flow (1′) will pass from the outside the vehicle, thus allowing the heat transfer coolant to be cooled and thus ensuring the temperature of the engine (M) is maintained at the optimum temperature.

The main switch valve (17) is also connected to a heating branch (16) comprising a heat exchanger (12′) used to store calories in order to return them later on if necessary, and a secondary circulation pump (11′), preferably an electrical pump, which will allow circulation of the coolant within the heating branch (16).

Lastly, the main switch valve (17) is also connected to a bypass branch (15″) to ensure parallel circulation of the coolant in the cooling (15′) and heating branches (16). In an advantageous way, the main switch valve (17) is configured so as to allow circulation of the coolant in the cooling branch (15′) and/or in the bypass branch (15″) and/or in the heating branch (16).

In accordance with an alternative embodiment, the storage loop (16) includes a return exchanger (13′) placed downstream from the storage exchanger (12′) in the direction of the secondary coolant circulation (20).

The return exchanger (13′) makes it possible to reconstitute the cold units stored in the storage exchanger (12) when the main air conditioning loop (15) is stopped. In a particular advantageous way, the return exchanger (13′) is crossed by the air flow (1). The air flow (1) is reheated by crossing through the return exchanger (13′) prior to its dispersion inside the passenger compartment of the vehicle.

According to a certain embodiment, the return exchanger (13′) is composed by the heating or aerothermal radiator (13′) used to heat the air flow (1) capable of being diffused in the passenger compartment of the vehicle. In this configuration, the heating radiator (13′) contributes to reconstituting the calories stored in the storage exchanger (12′) when the cooling circuit (15) is stopped.

In order to allow implementation of the reconstitution of the calories stored in the storage exchanger (12′), the heat transfer cooling fluid is put into circulation by the secondary circulation pump (11′). In an advantageous fashion, the secondary circulation pump (11′) functions whether the cooling loop (15) is stopped or working.

It is possible, however, to allow the secondary circulation pump (11′) to stop when the storage capacity of the storage exchanger (12′) is reached in order to optimize consumption, especially electrical, of the heating, ventilation and/or air conditioning installation.

The storage loop (16) also includes two secondary switching valves, (18′ and 18″). The secondary switching valves (18′ and 18″) making circulation of coolant possible in the heating loop (16) no matter what the state of operation of the main cooling circuit (15), i.e., the main circulation pump (19) may either be stopped or working.

FIGS. 1 to 3 present various examples of arrangements which are given as an example of a storage exchanger. However, this invention finds application in all installations requiring storage of calories and/or cold units.

FIG. 4 shows a surface view of a storage exchanger according to this invention and used in the loops and circuits shown in diagram form in the preceding Figures.

FIG. 4 presents a heat exchanger such as the storage exchanger (12) installed on the secondary loop (10) of FIG. 1 or 2, or the storage exchanger (12′) installed on the heating loop (16) of FIG. 3. The storage exchangers (12 and 12′) are the common point for transporting a heat transfer fluid, the secondary heat transfer fluid or the coolant respectively.

The storage exchanger (12), and respectively (12′), includes a plurality of flow tubes (25) for the heat transfer fluid. Each flow tube (25) includes a first end (26) which opens into a first heat transfer fluid collector (27), notably an inlet header. Each flow tube (15) also includes a first end (28) which opens into a first heat transfer fluid collector (29), notably an inlet header. The flow tubes (25) are placed in parallel to and separated from each other. An insert (30) is placed between two adjacent flow tubes (25). The insert (30) is in contact with each of the flow tubes (25) enclosing it in order to increase the heat exchange between the heat transfer fluid circulating in the flow tubes (25) and another medium of heat transport, passing between the flow tubes (25) and crossing the insert (30).

The unit that is constituted by the layers of the flow tubes (25) and inserts (30) defines a bundle from the storage exchanger (12), and respectively (12″).

According to a preferred embodiment of the storage exchanger (12), the first manifold (27) and the second manifold (29) extend depending on their respective axes (A1 and A2), and preferably in parallel to each other. Advantageously, the flow tubes (25) are arranged at right angles to the general extension axes (A1 and A2) and respectively from the first manifold (27) and second manifold (29).

The insert (30) is introduced between two flow tubes (25), so that each flow tube (25) is bordered by two inserts (30). The purpose of each insert (30) is to increase the heat exchange surface area offered by the flow tubes 25. Each insert (30) is in line with a group of folds formed by blades (31).

FIG. 5 is a partial view of the insert (30) of the heat exchanger (12), and respectively (12′), illustrated in FIG. 4. Each blade (31) includes a first edge 32 in contact with the first flow tube (25) and a second edge (33) in contact with the second tube (25) placed next to the first flow tube (25).

The insert (30) is, broadly speaking, laid out as a succession of blades (31). The first edge (32) of a first blade (31) and the first edge (32) of a second blade (31), adjacent to the first blade (31), are spaced with a blading pitch (Pa) between them. In other words, the blading pitch (Pa) is the distance between two consecutive blades (31), and more in particular, their first edges (32) respectively, or their second edges (33), respectively.

According to this invention, the blading pitch (Pa) is comprised of between 0.4 mm and 0.75 mm, preferably around 0.5 mm. This range of size represents the best compromise between an optimized thermal performance and a minimized footprint of the heat exchanger (12), and respectively (12′). The best thermal performance given by the heat exchanger (12), and respectively (12′), is obtained when the blading pitch (Pa) is around 0.5 mm. When the blading pitch (Pa) falls between 0.4 mm and 0.75 mm, it is possible to ensure storage of between 200 kJ and 270 KJ during a period of less than two minutes. Alternately, the blading pitch (Pa) may fall between 0.4 mm and 0.7 mm, and more in particular, between 0.4 mm and 0.6 mm.

Each blade (31) has a blade length (La) of between 5 mm and 8 mm, and preferably between 6 mm and 7 mm, especially around 6.5 mm. The length of the blade (La) corresponds to the distance between the first edge (32) and the second edge (33) of the same blade (31).

Each blade (31) has a blade width (Ea) of between 0.04 mm and 0.12 mm, and preferably around 0.08 mm. For example, each insert (20) is obtained by folding layers of a heat conducting material with a thickness of between 0.04 mm and 0.12 mm, corresponding to the thickness of the blade (Ea).

In reference again to FIG. 4, the flow tube (25) has a tube length (Lt) of between 270 mm and 360 mm, and preferably of around 315 mm. The length of the tube (Lt) is measured from between the first end (16) and the second end (18) of the flow tube (25) and corresponds to the distance between two respective sides next to the first manifold (27) and the second manifold (29).

Two adjacent flow tubes (25) are spaced from one another at the tube pitch (Pt) which measures between 7 mm and 9 mm, and preferably around 7.75 mm or 8.5 mm. The tube pitch (Pt) is the distance between two respective lines of extension (A3) from two consecutive flow tubes (25).

The tube width (Et) of each flow tube (25) is between 0.2 mm and 0.25 mm, and preferably around 0.23 mm. In other words, the thickness of the wall constituting the flow tube (25) is between 0.2 mm and 0.25 mm, and preferably around 0.23 mm. Additionally, each flow tube (25) has a height (ht) of between 1.2 mm and 1.3 mm.

As defined in FIG. 4, the bundle of the storage exchanger (12), and respectively (12′), extends in a first direction corresponding to the height of the bundle, i.e., in the direction of extension of the circulation tubes (25) and in a second direction corresponding to the direction of the layers of circulation tubes (25) and of the inserts (30), i.e., the direction of the extension of the first manifold (27) and a second manifold (29).

Incidentally, the height (Hc) of the first manifold (27), and respectively the second manifold (29), of between 10 mm and 14 mm, and preferably around 12 mm. The height of the manifold (Hc) is measured in accordance with the first direction.

Lastly, the depth (Pe) of the storage exchanger (12), and respectively (12′), is between 20 and 35 mm, and preferably around 27.5 mm. The depth of exchanger Pe is measured along a third direction which forms a direct orthonormal marker with the first and second directions defined previously.

The width (Le) of the storage exchanger (12), and respectively (12′), is measured along the second direction and is between 300 mm and 400 mm, and is preferably around 340 mm.

The total width (Lte) of the storage exchanger (12), and respectively (12′), is between 250 mm and 300 mm and the usable width of the exchanger (Lue) is between 235 mm and 275 mm. The total width of the exchanger (Lte) corresponds to the width of the storage exchanger (12), and respectively (12′), along a first direction, while the usable width of the exchanger (Lue) corresponds to the width of the storage exchanger bundle (12), and respectively (12′), along the first direction. Preferably, the total width of the exchanger (Lte) is around 275 mm while the usable width of the exchanger (Lue) is around 255 mm.

FIG. 6 is a detailed view illustrating a component blade (31) of the insert shown in the previous Figure. FIG. 6 enables you to better identify the blading pitch (Pa), the length of the blade (La) and the thickness of blade (Ea).

According to this invention, in order to ensure the operation of storing calories and/or cold units, a calorie or cold unit storage material, in particular a phase change material, at least partially fills an interstitial space (35) placed between the insert (30) and the flow tubes (25) and/or even placed between two consecutive blades (31).

The storage material, in particular the phase change material may be, for example, paraffin with a melting point between 8° C. and 12° C. in the framework of a cold unit storage exchanger.

In order to easily fill in the storage material, notably, phase change material, and in particular paraffin, the interstitial space (35) and maintenance of the storage material, in the storage exchanger (12), and respectively (12′), the latter is provided with two recovery plates 40, shown in FIG. 7, to border on the flow tubes (25) and the inserts (30). The recovery plates (40) are designed to help support the first manifold (27) and second manifold (29), to enclose the flow tubes (25) and inserts (30) in an enclosed space conducive to promoting heat exchange between the phase storage material and the blades (31) and/or the flow tubes (25). The recovery plates (40) are made of aluminum, for instance. At least one of the recovery plates (40) is fitted with a plurality of apertures to be used for filling (37) allowing the introduction of the storage material between the blades (31) and the flow tubes (15).

In FIGS. 4 and 5, the recovery plates (40) are not shown.

Finally, it should be noted that the heat transfer fluid follows along the inside of the storage exchanger (12), and respectively (12′), a route laid out in the form of an “I”, from the first manifold (27), through the tubes of movement 25, until the second collector (29).

However, this invention is also of application in storage exchangers (12), and respectively (12′), in which the heat transfer fluid follows along the inside of the storage exchanger (12), and respectively (12′), a route laid out in the form of a “U” from a bilge box comprising the first manifold (27) and the second manifold (29) placed alongside each other. According to this configuration, the flow tubes (25) ensure circulation of the heat transfer fluid in a “U” conformation.

FIGS. 8 and 9 respectively represent the evolution of the average temperature of the storage material expressed in degrees Celsius as a function of time expressed in seconds and the evolution of the energy stored by the storage exchanger (12), respectively (12′), expressed in kilojoules as a function of time expressed in seconds.

Thus, the storage exchanger (12), respectively (12′), is capable of obtaining optimal thermal efficiency, allowing for storage of between 200 kJ and 350 kJ, notably between 220 kJ and 370 kJ, in less than a given time (t0), specifically for a time period (t0) of two minutes.

Additionally, for this time period (t0), the average temperature of the heat storage material is in the optimum range of heat storage in the heat storage material, in particular the phase change material, having a melting point between 8° C. and 12° C. in the framework of a storage exchanger (12), respectively (12′) cold units.

Of course, the invention is not limited to the embodiments described above and provided for the purpose of examples only and includes other variants which may be envisaged by a professional in the field within the framework of this invention and including any combination of the various embodiments previously described.

Claims

1. A storage exchanger (12, 12′) comprising at least one flow tube (25) and a second flow tube (25) for heat transfer fluid respectively; a first end (26) opening into a first manifold (27) and a second end (28) opening into a second manifold (29); the first and second flow tubes (25) being placed adjacent to each other, and at least one insert (30) placed between the first flow tube (25) and the second flow tube (25), the insert (30) being constituted of a plurality of blades (31) comprising a first edge (32) in contact with the first flow tube (25) and a second edge (33) in contact with the second flow tube (25), at least one interstitial space (35) which is defined between the insert (30) and the flow tubes (25), wherein the interstitial space (35) is filled with a material for storing calories or cold units.

2. A storage exchanger (12, 12′) according to claim 1, wherein the blades (31) of the insert (30) are spaced at a blading pitch (Pa) from each other, comprised between 0.4 mm and 0.75 mm.

3. A storage exchanger (12, 12′) according to claim 1, wherein each blade (21) comprises a length (La) of between 5 mm and 8 mm.

4. A storage exchanger (12, 12′) according to claim 1, wherein each blade (21) comprises a width (Ea) of between 0.04 mm and 0.12 mm.

5. A storage exchanger (12, 12′) according to claim 1, wherein each tube (15) comprises a length (Lt) of between 270 mm and 360 mm.

6. A storage exchanger (12, 12′) according to claim 1, wherein each tube (15) comprises a height (Ht) of between 1.2 mm and 1.3 mm.

7. A storage exchanger (12, 12′) according to claim 1, wherein two adjacent tubes (15) are spaced at a tube pitch (Pt) from each other, of between 7 mm and 9 mm.

8. A storage exchanger (12, 12′) according to claim 1, wherein each tube (15) comprises a tube thickness (Et) of between 0.2 mm and 0.25 mm.

9. A storage exchanger (12, 12′) according to claim 1, wherein each manifold (17, 19) comprises a manifold height (Hc) of between 10 mm and 14 mm.

10. A storage exchanger (12, 12′) according to claim 1, wherein the heat exchanger (12, 12′, 12″) comprises an exchanger depth (Pe) of between 20 mm and 35 mm.

11. A storage exchanger (12, 12′) according to claim 1, wherein the heat exchanger (12, 12′, 12″) comprises an exchanger length (Le) of between 300 mm and 400 mm.

12. A storage exchanger (12, 12′) according to claim 1, wherein the heat exchanger (12, 12′, 12″) comprises a total exchanger width (Lte) of between 250 mm and 300 mm.

13. A storage exchanger (12, 12′) according to claim 1, wherein the heat exchanger (12, 12′, 12″) comprises a usable exchanger width (Lue) of between 235 mm and 275 mm.