Improved aerator for an air-cooled refrigeration cycle arrangement

Abstract

Aerator for an air-cooled refrigeration cycle arrangement, comprising compensable connection configured to connect an air-cooled module on a structure defining the aerator in a releasable manner and providing a displacement clearance between the air-cooled module and the structure.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This Patent Application claims priority from Italian Patent Application No. 102022000025983 filed on Dec. 19, 2022, the entire disclosure of which is incorporated herein by reference.TECHNICAL FIELD

[0002] The present invention concerns an aerator for an air-cooled refrigeration cycle arrangement, in particular for air conditioning, food storage, process cooling machines and other machines intended for managing media temperature and / or humidity.BACKGROUND OF THE INVENTION

[0003] Air-cooled refrigeration cycle arrangements are widely known and used for managing media temperature and / or humidity into a closed space. However, such arrangements are known to have a high energetic consumption.

[0004] Such high energetic consumption is a crucial parameter, especially for large plants such as industrial or commercial spaces which need to conditioning great flows of air or large process cooling installations.

[0005] An example of air-cooled refrigeration cycle arrangement is disclosed in WO2021 / 099955 A1.

[0006] In the aforementioned air-cooled refrigeration cycle arrangement at least an aerator is used to exchange an air flow with heat exchangers, e.g. the condenser and the subcooler. As known the aerator comprises a structure that houses the heat exchangers and allows the passage of air through these latter.

[0007] However, the known aerators structure carries the heat exchangers by brackets that however generate thermal bridges with the heat exchangers by supporting these latter. Accordingly, the efficiency of the overall air-cooled refrigeration cycle arrangement is reduced.

[0008] Furthermore, the structure supporting the heat exchanger must be designed to support a wide range of stress due to thermal dilatation caused by the wide temperature range in which the aerator operates. Therefore, such structure is bulky and costly.

[0009] Moreover, if more than one heat exchanger is supported by the structure, the lateral extension of this latter is not negligible, thereby causing installation problems.

[0010] Therefore, the need is felt to solve the aforementioned drawbacks linked to aerators for known air-cooled refrigeration cycle arrangements so that their energetic consumption is reduced.

[0011] An aim of the present invention is to satisfy the above-mentioned needs in a cost effective and optimized way.SUMMARY OF THE INVENTION

[0012] The aforementioned aim is reached by an aerator and an air-cooled refrigeration cycle arrangement as claimed in the appended set of claims.BRIEF DESCRIPTION OF DRAWINGS

[0013] For a better understanding of the present invention, a preferred embodiment is described in the following, by way of a non-limiting example, with reference to the attached drawings wherein:

[0014] FIG. 1 is a perspective view of an aerator according to the present invention;

[0015] FIG. 2 is a lateral schematic view of the aerator of FIG. 1;

[0016] FIG. 3 is a sectional partial view of the aerator of FIG. 2 along line III-III;

[0017] FIG. 4 is a partial perspective view of a bottom portion of the aerator of FIG. 1; and

[0018] FIG. 5 is a partial perspective view of a top portion of the aerator of FIG. 1.DETAILED DESCRIPTION OF THE INVENTION

[0019] FIGS. 1 and 2 show an aerator 1 according to the invention configured to support at least an air-cooled module 2 as described in the following and making part of an air-cooled refrigeration cycle arrangement, not shown and described in its entirety for sake of brevity.

[0020] In synthesis, and as known, the air-cooled refrigeration cycle arrangement comprises compressor means, evaporator means, valve means and the below described condenser and subcooler as disclosed in WO2021 / 099955 A1, the content of which is incorporated therein by reference.

[0021] According to the non-limiting shown embodiment, the aerator 1 is of V-shaped typology, i.e. comprises a first, left, support side 3a and a second, right support side opposite one another with respect to a first, vertical, axis A and preferably converging to this latter.

[0022] The first and second sides 3a, 3b are each configured to house an air-cooled module 2. An air-cooled module 2 comprises at least a heat exchanger, in the disclosed example three heat exchangers 2′, 2″, 2′″ whose function will be described in the following.

[0023] The aerator 1 further comprises a top plate 3c provided with ventilation means 4, e.g. at least an electric actuated fan. On the bottom the aerator 1 may be closes by a bottom wall or, as in the present case, the left and right support side 3a, 3b close one in contact to the other at their lower extremity.

[0024] On a longitudinal direction, i.e. along a second, longitudinal, axis B perpendicular to vertical axis A, the aerator comprises axial plates 3d configured to close a space 7. The space 7 therefore results delimited with respect to environment by support sides 3a, 3b, top plate 3c and axial plates 3b.

[0025] In particular, the aerator 1 comprises a structure 5 that defines each support side 3a, 3b and that allows the fixation to each support side 3a, 3b of the respective air-cooled module 2 and of the top plate 3c.

[0026] Preferably, structure 5 comprises a plurality of first support element, such as beam-like elements 6, preferably realized as profilate elements, connected together to define the structure 5. In particular, the beam-like elements 6 provide support for top plate 3c and of the support sides 3a, 3b supporting the air-cooled modules 2.

[0027] In the vertical extremities of the aerator 1, i.e. on the top and on the bottom of aerator according to vertical axis A direction, structure 5 comprises respective second support elements, such as support plates 8 configured to allow support of the air-cooled module 2 on the structure 5 and to connected the beam-like elements 6.

[0028] In detail, each air-cooled module 2 is supported by the support plate 8 in a selectively removable manner. Moreover, each air-cooled module 2 is supported by support plate 8 with space compensation due to thermal expansion and retraction of air-cooled module 2.

[0029] Conveniently, each air-cooled module 2 is supported by the support plate 8 via a compensable connection 9 provided at each of its corners. In particular, in the disclosed embodiment, the compensable connection 9 is provided between the top and the bottom of heat exchanger 2′, 2″, 2′″ of the air-cooled module 2 and the support plate 8 on front and rear ends of the support side 3a, 3b.

[0030] Each compensable connection 9 comprise a pin element 10 configured to be housed in a slidable manner in a seat 11 realized in the support plate 8.

[0031] In particular, each support plate 8 defines a number of seats 11′, 11″, 11′″ equal to the number of heat exchangers 2′, 2″, 2′″ of the cooling module 2. In the disclosed embodiment the seats 11′, 11″, 11′″ are in number of three as the number of heat exchangers 2′, 2″, 2′″ and are spaced along a direction perpendicular to axes A and B. Such spacing may by designed according to the dimension of heat exchangers 2′, 2″, 2′″ and according to their spacing needs.

[0032] Each seat 11 has preferably a U-shaped cross-section with the opening on the upper portion of the support plate 8, i.e. in the vertical axis A direction, and is defined through the support plate in the longitudinal axis B direction. Consequently, the pin element 10 is shaped to cooperate at contact, with a preset clearance movement within the seat 11, i.e. in longitudinal direction and in the transversal direction perpendicular to both axis A and B.

[0033] Clearly, since the opening is U-shaped and opened in vertical direction, the movement of such axis is always allowed.

[0034] The pin element 10 essentially comprises a base 12 that is configured to be fixed to the heat exchanger 2′, 2″, 2′″ in particular by welding. The base 12 has a shape that is configured to be accommodated around a portion of the heat exchanger 2′, 2″, 2′″; in the disclosed embodiment is therefore shaped curved in order to match to a substantial circular cross-section portion of the heat exchanger 2′, 2″, 2′″.

[0035] The pin element 10 further comprises a protrusion 13 extending from the base in a direction parallel to longitudinal axis B and configured to engage the respective slot 11. Accordingly, in the disclosed embodiment the protrusion is essentially cylindrical.

[0036] Preferably the pin element 10 is realized as a single element, i.e. monolithic, and in metallic material.

[0037] As best shown in FIGS. 3 and 4, the compensable connection 9 further comprises a cushion element 14 operationally interposed between the pin element 10 and the seat 11, in particular configured to be passed through by the pin element 10 and seated within seat 11.

[0038] Conveniently, the cushion element 14 is configured to be seated within seat 11 and is configured to house the pin element 10 without any spatial clearance.

[0039] In detail, the cushion element 14 is realized of polymeric material and more preferably in a compressible material in order to compensate relative movements between pin element 10 and seat 11. In particular, the material of cushion element 14 is a thermo-insulant material.

[0040] Preferably, the cushion element 14 is realized as an axial-symmetric element with respect to the axis of the pin element 10, i.e. parallelly to longitudinal axis B.

[0041] In particular, the cushion element 14 comprises a main portion 14a having a diametral H-cross section thereby defining a seat 15 configured to be housed within walls of support portion 8 defining seat 11 and an opening 16 passing through the main portion 14a and dimensioned to house the pin element 10.

[0042] Once fixed to the structure 5, the ventilation means 4 can suck air from the space 7 thereby sucking air through air-cooled modules 2.

[0043] Coming into details of the heat-exchangers, they are realized as plate-like exchangers through which air flow may pass as stated above and they are carried by structure 5 on the respective side 3a, 3b one faced with respect to the other and separated by a space along the air flow direction. In particular, each air-cooled module 2 comprises a condenser 2′and a subcooler 2″ and in detail, the condenser 2′ has a side facing space 7 and the opposite side facing, spaced, the subcooler 2″, while the subcooler 2″ has a side facing the environment and the opposite side facing, spaced, the condenser 2′.

[0044] Accordingly, the aforementioned air flow is sucked by ventilation means 4 through the air-cooled module 2, i.e. through both the condenser 2′ and the subcooler 2″ and than ejected through ventilation means 4 into the environment.

[0045] In particular, the refrigerant fluid enters into condenser 2′ from the edge nearer with respect to top plate 3c, i.e. at an upper portion of the condenser 2′ along the vertical axis A and then, exit from condenser 2′ from the edge nearer with respect to the bottom portion of the aerator 1, i.e. at a lower portion of the condenser 2′ along the vertical axis A.

[0046] Then, the exit of condenser 2′ is fluidly connected by a conduit to subcooler 2″ into which the fluid enters from a bottom portion of the subcooler 2″ along the vertical axis A and exit from subcooler 2″ from an edge nearer with respect to the top plate 3c, i.e. at an upper portion of the subcooler 2″ along the vertical axis A.

[0047] Therefore, in such configuration the condenser 2′ and the subcooler 2″ are fluidically placed one with respect to the other in a counterflow configuration.

[0048] Furthermore, the subcooler 2″ may be provided with a lower density of fins with respect to the condenser 6.

[0049] Moreover, optionally, the subcooler 2″ comprises tubes having a cross section lower with respect to the tubes comprised by the condenser 2′.

[0050] Each air-cooled module 2 may further comprise a third heat exchanger 2′″ that is placed faced to the subcooler 2″ from one side and to environment to the other and configured to allow free-cooling operation of the aerator, i.e. by cooling down the refrigerant without passing through condenser 2′ and subcooler 2″.

[0051] The operation of the above disclosed aerator 1 as disclosed above is the following.

[0052] In case of operation active mechanical refrigeration, the air-cooled refrigeration cycle carries the refrigerant fluid according to the following thermodynamic operations:

[0053] A compression thanks to compressor means wherein the gaseous refrigerant fluid passes to higher pressure superheated state thanks to work provided by compression means;

[0054] A constant pressure (except for pressure losses) heat exchange thanks to condenser 2′, wherein the refrigerant fluid passes to superheated vapor to saturated liquid providing heat to the ambient air;

[0055] A further heat exchange thanks to subcooler 2″ wherein the condensed fluid continues to decrease its temperature providing heat to the ambient air; and

[0056] An isenthalpic wherein the condensed fluid decreases its pressure till reaching a pre-set temperature; and

[0057] A constant temperature heat exchange (except for the pressure losses) wherein the fluid evaporates and superheat passing to vapor phase, thereby extracting heat from the media.

[0058] In case of free-cooling operation, the air-cooled refrigeration cycle arrangement carries a refrigerant fluid to be cooled only thanks to the passage of air in the third heat exchanger thereby bypassing the condenser and the subcooler, i.e. by-passing the aforementioned active mechanical refrigeration cycle.

[0059] In both the operations described above, the compensable connection 9 maintains the air-cooled module 2 coupled to the structure 5. However, due to the compressible nature of cushion element 14, the vibrations between the air-cooled module 2 and the structure 5 are compensated as well as the movements due to thermal expansion and retraction of each heat exchanger.

[0060] Moreover, if needed to remove or add a heat exchanger 2′, 2″, 2′″ to the structure 5, it is sufficient to compress the cushion element 14 thereby freeing one between the top or the bottom pin elements 10 from seats 11 thereby allowing the removal or insertion of a heat exchanger 2′, 2″, 2′″.

[0061] In view of the foregoing, the advantages of the proposed air-cooled refrigeration cycle arrangement 1 according to the invention are apparent.

[0062] Thanks to the proposed compensable connection 9 the air-cooled module 2 may allow easy and quick coupling of more than two heat exchangers in a very compact space.

[0063] Indeed, in the three heat exchangers configurations only 120 mm are needed to provide a wide thermal operative range of aerator 1.

[0064] Furthermore, the compensable connection 9 allows to compensate movements due to vibration and to thermal expansion / retraction, thereby allowing to provide a structure that is lighter.

[0065] Moreover, since the cushion element is made of compressible and polymeric, i.e. thermo-insulant, material no (or lower) thermal bridges are present between the air-cooled module 2 and the structure, thereby increasing the overall efficiency.

[0066] It is clear that modifications can be made to the described air arrangement apparatus 1 which do not extend beyond the scope of protection defined by the claims.

[0067] For instance, the air-cooled module 2 may comprise a variable number of heat exchanger that may be placed with respect to the structure 5 in a different manner, thereby leading to a different structure with respect to the disclosed V-shaped one.

[0068] Furthermore, even if a peculiar condenser-subcooler structure of the air-cooled refrigeration cycle arrangement is disclosed, clearly the proposed aerator may be used in different system.

[0069] Furthermore, the compensable connection and the cushion element could be realized in different shapes and manner.

Examples

Embodiment Construction

[0019]FIGS. 1 and 2 show an aerator 1 according to the invention configured to support at least an air-cooled module 2 as described in the following and making part of an air-cooled refrigeration cycle arrangement, not shown and described in its entirety for sake of brevity.

[0020]In synthesis, and as known, the air-cooled refrigeration cycle arrangement comprises compressor means, evaporator means, valve means and the below described condenser and subcooler as disclosed in WO2021 / 099955 A1, the content of which is incorporated therein by reference.

[0021]According to the non-limiting shown embodiment, the aerator 1 is of V-shaped typology, i.e. comprises a first, left, support side 3a and a second, right support side opposite one another with respect to a first, vertical, axis A and preferably converging to this latter.

[0022]The first and second sides 3a, 3b are each configured to house an air-cooled module 2. An air-cooled module 2 comprises at least a heat exchanger, in the disclos...

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This Patent Application claims priority from Italian Patent Application No. 102022000025983 filed on Dec. 19, 2022, the entire disclosure of which is incorporated herein by reference.TECHNICAL FIELD

[0002] The present invention concerns an aerator for an air-cooled refrigeration cycle arrangement, in particular for air conditioning, food storage, process cooling machines and other machines intended for managing media temperature and / or humidity.BACKGROUND OF THE INVENTION

[0003] Air-cooled refrigeration cycle arrangements are widely known and used for managing media temperature and / or humidity into a closed space. However, such arrangements are known to have a high energetic consumption.

[0004] Such high energetic consumption is a crucial parameter, especially for large plants such as industrial or commercial spaces which need to conditioning great flows of air or large process cooling installations.

[0005] An example of air-cooled refrigeration cycle arrangement is disclosed in WO2021 / 099955 A1.

[0006] In the aforementioned air-cooled refrigeration cycle arrangement at least an aerator is used to exchange an air flow with heat exchangers, e.g. the condenser and the subcooler. As known the aerator comprises a structure that houses the heat exchangers and allows the passage of air through these latter.

[0007] However, the known aerators structure carries the heat exchangers by brackets that however generate thermal bridges with the heat exchangers by supporting these latter. Accordingly, the efficiency of the overall air-cooled refrigeration cycle arrangement is reduced.

[0008] Furthermore, the structure supporting the heat exchanger must be designed to support a wide range of stress due to thermal dilatation caused by the wide temperature range in which the aerator operates. Therefore, such structure is bulky and costly.

[0009] Moreover, if more than one heat exchanger is supported by the structure, the lateral extension of this latter is not negligible, thereby causing installation problems.

[0010] Therefore, the need is felt to solve the aforementioned drawbacks linked to aerators for known air-cooled refrigeration cycle arrangements so that their energetic consumption is reduced.

[0011] An aim of the present invention is to satisfy the above-mentioned needs in a cost effective and optimized way.SUMMARY OF THE INVENTION

[0012] The aforementioned aim is reached by an aerator and an air-cooled refrigeration cycle arrangement as claimed in the appended set of claims.BRIEF DESCRIPTION OF DRAWINGS

[0013] For a better understanding of the present invention, a preferred embodiment is described in the following, by way of a non-limiting example, with reference to the attached drawings wherein:

[0014] FIG. 1 is a perspective view of an aerator according to the present invention;

[0015] FIG. 2 is a lateral schematic view of the aerator of FIG. 1;

[0016] FIG. 3 is a sectional partial view of the aerator of FIG. 2 along line III-III;

[0017] FIG. 4 is a partial perspective view of a bottom portion of the aerator of FIG. 1; and

[0018] FIG. 5 is a partial perspective view of a top portion of the aerator of FIG. 1.DETAILED DESCRIPTION OF THE INVENTION

[0019] FIGS. 1 and 2 show an aerator 1 according to the invention configured to support at least an air-cooled module 2 as described in the following and making part of an air-cooled refrigeration cycle arrangement, not shown and described in its entirety for sake of brevity.

[0020] In synthesis, and as known, the air-cooled refrigeration cycle arrangement comprises compressor means, evaporator means, valve means and the below described condenser and subcooler as disclosed in WO2021 / 099955 A1, the content of which is incorporated therein by reference.

[0021] According to the non-limiting shown embodiment, the aerator 1 is of V-shaped typology, i.e. comprises a first, left, support side 3a and a second, right support side opposite one another with respect to a first, vertical, axis A and preferably converging to this latter.

[0022] The first and second sides 3a, 3b are each configured to house an air-cooled module 2. An air-cooled module 2 comprises at least a heat exchanger, in the disclosed example three heat exchangers 2′, 2″, 2′″ whose function will be described in the following.

[0023] The aerator 1 further comprises a top plate 3c provided with ventilation means 4, e.g. at least an electric actuated fan. On the bottom the aerator 1 may be closes by a bottom wall or, as in the present case, the left and right support side 3a, 3b close one in contact to the other at their lower extremity.

[0024] On a longitudinal direction, i.e. along a second, longitudinal, axis B perpendicular to vertical axis A, the aerator comprises axial plates 3d configured to close a space 7. The space 7 therefore results delimited with respect to environment by support sides 3a, 3b, top plate 3c and axial plates 3b.

[0025] In particular, the aerator 1 comprises a structure 5 that defines each support side 3a, 3b and that allows the fixation to each support side 3a, 3b of the respective air-cooled module 2 and of the top plate 3c.

[0026] Preferably, structure 5 comprises a plurality of first support element, such as beam-like elements 6, preferably realized as profilate elements, connected together to define the structure 5. In particular, the beam-like elements 6 provide support for top plate 3c and of the support sides 3a, 3b supporting the air-cooled modules 2.

[0027] In the vertical extremities of the aerator 1, i.e. on the top and on the bottom of aerator according to vertical axis A direction, structure 5 comprises respective second support elements, such as support plates 8 configured to allow support of the air-cooled module 2 on the structure 5 and to connected the beam-like elements 6.

[0028] In detail, each air-cooled module 2 is supported by the support plate 8 in a selectively removable manner. Moreover, each air-cooled module 2 is supported by support plate 8 with space compensation due to thermal expansion and retraction of air-cooled module 2.

[0029] Conveniently, each air-cooled module 2 is supported by the support plate 8 via a compensable connection 9 provided at each of its corners. In particular, in the disclosed embodiment, the compensable connection 9 is provided between the top and the bottom of heat exchanger 2′, 2″, 2′″ of the air-cooled module 2 and the support plate 8 on front and rear ends of the support side 3a, 3b.

[0030] Each compensable connection 9 comprise a pin element 10 configured to be housed in a slidable manner in a seat 11 realized in the support plate 8.

[0031] In particular, each support plate 8 defines a number of seats 11′, 11″, 11′″ equal to the number of heat exchangers 2′, 2″, 2′″ of the cooling module 2. In the disclosed embodiment the seats 11′, 11″, 11′″ are in number of three as the number of heat exchangers 2′, 2″, 2′″ and are spaced along a direction perpendicular to axes A and B. Such spacing may by designed according to the dimension of heat exchangers 2′, 2″, 2′″ and according to their spacing needs.

[0032] Each seat 11 has preferably a U-shaped cross-section with the opening on the upper portion of the support plate 8, i.e. in the vertical axis A direction, and is defined through the support plate in the longitudinal axis B direction. Consequently, the pin element 10 is shaped to cooperate at contact, with a preset clearance movement within the seat 11, i.e. in longitudinal direction and in the transversal direction perpendicular to both axis A and B.

[0033] Clearly, since the opening is U-shaped and opened in vertical direction, the movement of such axis is always allowed.

[0034] The pin element 10 essentially comprises a base 12 that is configured to be fixed to the heat exchanger 2′, 2″, 2′″ in particular by welding. The base 12 has a shape that is configured to be accommodated around a portion of the heat exchanger 2′, 2″, 2′″; in the disclosed embodiment is therefore shaped curved in order to match to a substantial circular cross-section portion of the heat exchanger 2′, 2″, 2′″.

[0035] The pin element 10 further comprises a protrusion 13 extending from the base in a direction parallel to longitudinal axis B and configured to engage the respective slot 11. Accordingly, in the disclosed embodiment the protrusion is essentially cylindrical.

[0036] Preferably the pin element 10 is realized as a single element, i.e. monolithic, and in metallic material.

[0037] As best shown in FIGS. 3 and 4, the compensable connection 9 further comprises a cushion element 14 operationally interposed between the pin element 10 and the seat 11, in particular configured to be passed through by the pin element 10 and seated within seat 11.

[0038] Conveniently, the cushion element 14 is configured to be seated within seat 11 and is configured to house the pin element 10 without any spatial clearance.

[0039] In detail, the cushion element 14 is realized of polymeric material and more preferably in a compressible material in order to compensate relative movements between pin element 10 and seat 11. In particular, the material of cushion element 14 is a thermo-insulant material.

[0040] Preferably, the cushion element 14 is realized as an axial-symmetric element with respect to the axis of the pin element 10, i.e. parallelly to longitudinal axis B.

[0041] In particular, the cushion element 14 comprises a main portion 14a having a diametral H-cross section thereby defining a seat 15 configured to be housed within walls of support portion 8 defining seat 11 and an opening 16 passing through the main portion 14a and dimensioned to house the pin element 10.

[0042] Once fixed to the structure 5, the ventilation means 4 can suck air from the space 7 thereby sucking air through air-cooled modules 2.

[0043] Coming into details of the heat-exchangers, they are realized as plate-like exchangers through which air flow may pass as stated above and they are carried by structure 5 on the respective side 3a, 3b one faced with respect to the other and separated by a space along the air flow direction. In particular, each air-cooled module 2 comprises a condenser 2′and a subcooler 2″ and in detail, the condenser 2′ has a side facing space 7 and the opposite side facing, spaced, the subcooler 2″, while the subcooler 2″ has a side facing the environment and the opposite side facing, spaced, the condenser 2′.

[0044] Accordingly, the aforementioned air flow is sucked by ventilation means 4 through the air-cooled module 2, i.e. through both the condenser 2′ and the subcooler 2″ and than ejected through ventilation means 4 into the environment.

[0045] In particular, the refrigerant fluid enters into condenser 2′ from the edge nearer with respect to top plate 3c, i.e. at an upper portion of the condenser 2′ along the vertical axis A and then, exit from condenser 2′ from the edge nearer with respect to the bottom portion of the aerator 1, i.e. at a lower portion of the condenser 2′ along the vertical axis A.

[0046] Then, the exit of condenser 2′ is fluidly connected by a conduit to subcooler 2″ into which the fluid enters from a bottom portion of the subcooler 2″ along the vertical axis A and exit from subcooler 2″ from an edge nearer with respect to the top plate 3c, i.e. at an upper portion of the subcooler 2″ along the vertical axis A.

[0047] Therefore, in such configuration the condenser 2′ and the subcooler 2″ are fluidically placed one with respect to the other in a counterflow configuration.

[0048] Furthermore, the subcooler 2″ may be provided with a lower density of fins with respect to the condenser 6.

[0049] Moreover, optionally, the subcooler 2″ comprises tubes having a cross section lower with respect to the tubes comprised by the condenser 2′.

[0050] Each air-cooled module 2 may further comprise a third heat exchanger 2′″ that is placed faced to the subcooler 2″ from one side and to environment to the other and configured to allow free-cooling operation of the aerator, i.e. by cooling down the refrigerant without passing through condenser 2′ and subcooler 2″.

[0051] The operation of the above disclosed aerator 1 as disclosed above is the following.

[0052] In case of operation active mechanical refrigeration, the air-cooled refrigeration cycle carries the refrigerant fluid according to the following thermodynamic operations:

[0053] A compression thanks to compressor means wherein the gaseous refrigerant fluid passes to higher pressure superheated state thanks to work provided by compression means;

[0054] A constant pressure (except for pressure losses) heat exchange thanks to condenser 2′, wherein the refrigerant fluid passes to superheated vapor to saturated liquid providing heat to the ambient air;

[0055] A further heat exchange thanks to subcooler 2″ wherein the condensed fluid continues to decrease its temperature providing heat to the ambient air; and

[0056] An isenthalpic wherein the condensed fluid decreases its pressure till reaching a pre-set temperature; and

[0057] A constant temperature heat exchange (except for the pressure losses) wherein the fluid evaporates and superheat passing to vapor phase, thereby extracting heat from the media.

[0058] In case of free-cooling operation, the air-cooled refrigeration cycle arrangement carries a refrigerant fluid to be cooled only thanks to the passage of air in the third heat exchanger thereby bypassing the condenser and the subcooler, i.e. by-passing the aforementioned active mechanical refrigeration cycle.

[0059] In both the operations described above, the compensable connection 9 maintains the air-cooled module 2 coupled to the structure 5. However, due to the compressible nature of cushion element 14, the vibrations between the air-cooled module 2 and the structure 5 are compensated as well as the movements due to thermal expansion and retraction of each heat exchanger.

[0060] Moreover, if needed to remove or add a heat exchanger 2′, 2″, 2′″ to the structure 5, it is sufficient to compress the cushion element 14 thereby freeing one between the top or the bottom pin elements 10 from seats 11 thereby allowing the removal or insertion of a heat exchanger 2′, 2″, 2′″.

[0061] In view of the foregoing, the advantages of the proposed air-cooled refrigeration cycle arrangement 1 according to the invention are apparent.

[0062] Thanks to the proposed compensable connection 9 the air-cooled module 2 may allow easy and quick coupling of more than two heat exchangers in a very compact space.

[0063] Indeed, in the three heat exchangers configurations only 120 mm are needed to provide a wide thermal operative range of aerator 1.

[0064] Furthermore, the compensable connection 9 allows to compensate movements due to vibration and to thermal expansion / retraction, thereby allowing to provide a structure that is lighter.

[0065] Moreover, since the cushion element is made of compressible and polymeric, i.e. thermo-insulant, material no (or lower) thermal bridges are present between the air-cooled module 2 and the structure, thereby increasing the overall efficiency.

[0066] It is clear that modifications can be made to the described air arrangement apparatus 1 which do not extend beyond the scope of protection defined by the claims.

[0067] For instance, the air-cooled module 2 may comprise a variable number of heat exchanger that may be placed with respect to the structure 5 in a different manner, thereby leading to a different structure with respect to the disclosed V-shaped one.

[0068] Furthermore, even if a peculiar condenser-subcooler structure of the air-cooled refrigeration cycle arrangement is disclosed, clearly the proposed aerator may be used in different system.

[0069] Furthermore, the compensable connection and the cushion element could be realized in different shapes and manner.

Examples

Embodiment Construction

[0019]FIGS. 1 and 2 show an aerator 1 according to the invention configured to support at least an air-cooled module 2 as described in the following and making part of an air-cooled refrigeration cycle arrangement, not shown and described in its entirety for sake of brevity.

[0020]In synthesis, and as known, the air-cooled refrigeration cycle arrangement comprises compressor means, evaporator means, valve means and the below described condenser and subcooler as disclosed in WO2021 / 099955 A1, the content of which is incorporated therein by reference.

[0021]According to the non-limiting shown embodiment, the aerator 1 is of V-shaped typology, i.e. comprises a first, left, support side 3a and a second, right support side opposite one another with respect to a first, vertical, axis A and preferably converging to this latter.

[0022]The first and second sides 3a, 3b are each configured to house an air-cooled module 2. An air-cooled module 2 comprises at least a heat exchanger, in the disclos...

Claims

1. Aerator for an air-cooled refrigeration cycle arrangement, said aerator comprising a structure configured to define a first side, a second side opposite to a first axis and a second axis and to support at least a plate, the first and second sides and the plate being configured to limit a space which is delimited by said first and second sides and said plate, wherein said plate being configured to carry ventilation means configured to suck air from said space and flow such air towards the environment and wherein at least one between said first and second sides being configured to carry an air-cooled module configured to allow said flow to pass therethrough, said structure comprising first support elements defining said first and second sides and supporting said plate and second support elements connected to said first support elements and configured to support said air-cooled module on said at least one between said first and second sides said aerator comprising a compensable connection configured to connect said air-cooled module on said second support element in a releasable manner and providing a displacement clearance between said air-cooled module and said second support element.

2. Aerator according to claim 1, wherein said compensable connection comprises a pin element fixedly carried in one between said air-cooled module and said second support element and a seat realized in the other between said air-cooled module and said second support element, said pin element being configured to be housed within said seat.

3. Aerator according to claim 2, wherein said compensable connection comprises a cushion element operatively interposed between said pin element and said second support element.

4. Aerator according to claim 3, wherein said cushion element is realized in compressible material.

5. Aerator according to claim 3, wherein said cushion element is realized in thermo-insulating material.

6. Aerator according to claim 3, wherein said cushion element is realized in polymeric material.

7. Aerator according to claim 3, wherein said cushion element defines a hole configured to house said pin element and a seat configured to cooperate at contact with said second support element.

8. Aerator according to claim 3, wherein said cushion element as an axial-symmetric shape.

9. Aerator according to claim 2, wherein said pin element comprises a base configured to be fixedly secured to said air-cooled module and a pin extending from said base.

10. Aerator according to claim 9, wherein said pin element is monolithic.

11. Aerator according to claim 2, wherein said second support element is plate-shaped and said seats are realized passing through.

12. Aerator according to claim 1, wherein said air-cooled module comprises at least a heat exchanger each heat exchanger being carried by said structure via said compensable connection (9) at each corner of said heat exchanger.

13. Aerator according to claim 1, wherein said first and second sides are converging in a V-shaped manner along said first axis.

14. Aerator according to claim 1, wherein said air-cooled module comprises a condenser and a subcooler.

15. Aerator according to claim 1, wherein said air-cooled module comprises a condenser, a subcooler and a free-cooling heat exchanger.

16. Air-cooled refrigeration cycle arrangement comprising a compressor means configured to increase the pressure of a refrigerant fluid, expansion means configured to decrease the pressure of said refrigerant fluid and an evaporator configured to allow the passage of phase from liquid to gaseous state of said refrigerant fluid, said air-cooled refrigeration cycle apparatus comprising an aerator according to claim 1.

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