Devices for intense / rapid cooling and for removing substances in suspension in gaseous fluids

Abstract

1. An apparatus for strongly / rapidly cooling and removing substances in suspension in a gaseous fluid, comprising: i) a conveying means (2) for conveying the gaseous fluid; ii) a system (3) for alternatively condensing / freezing or defrosting substances present in the gaseous fluid, the system (3) comprising: a first group of cooling or defrosting stages (31); a second group of cooling or defrosting stages (32); a means (347) for collecting the substances; the conveying means (2) comprising first and second lines (311, 321) arranged in parallel; iii) a heat exchanger (4) for pre-cooling the gaseous fluid upstream of the first group (31) or the second group (32); iv) a heat exchanger (4) for pre-cooling the gaseous fluid upstream of the first group (31) or the second group (32); a conveying means (2) upstream of the first group (31) or the second group (32) for conveying the gaseous fluid present downstream of the first group (31) or the second group (32) to the heat exchanger (4), the conveying means (2) comprising means (5) for removing heat from the gaseous fluid passing through the heat exchanger (4); v) a directing means (6) for directing the fluid alternately to the first line or the second line (311, 321); vi) a first fan (71) and a second fan (72) located along the conveying means (2), the volumetric flow rate of the gaseous fluid generated by the first fan (71) being greater than the volumetric flow rate of the air generated by the second fan (72).

Description

[Technical Field]

[0001] The present invention relates to an apparatus for the strong / rapid cooling and removal of substances present in suspension in a gaseous fluid, typically air.

[0002] The substance may be, for example, a contaminant (eg, a solvent such as a volatile organic compound, an aliphatic compound, a hydrocarbon, an oil, an acid, etc.) or even simply water.

[0003] In particular, this applies both to cryogenic processing for strong cooling (e.g., of electronic components or semiconductors) or rapid cooling (e.g., of fluids downstream of exothermic processes), and to condense solvents or contaminants by separating them from the fluid in the gas phase. [Background technology]

[0004] Various industrial applications utilizing chemicals are known. Purely by way of example, these include plastic material processing, printing, pickling, painting, and the pharmaceutical industry. Chemicals include solvents that are exhausted together with the airflow coming from the work zone. This airflow must be treated before being released into the environment. In this regard, there are known systems that involve cooling the airflow to promote the condensation of such substances. These substances can be in various forms, such as vapors, gases, microdroplets, etc.

[0005] One drawback of such solutions is their discontinuous operation. In fact, during operation, contaminants can cool down and freeze the passages, gradually hindering correct operation. Therefore, periodic defrosting cycles are provided for the refrigeration system or part of the device.

[0006] Another drawback is that known solutions (incinerators, activated carbon...) are usually too expensive and sometimes even ineffective.

[0007] The drawback of this solution is related to the fact that it is difficult to obtain temperatures below -100°C using an evaporator-compressor-condenser-stacked cooling plant.

[0008] The object of the present invention is to eliminate the above-mentioned drawbacks by making available an apparatus and a method capable of separating at least one solvent or contaminant from a fluid in the gas phase at low cost and with a consistent yield.

[0009] Another objective is to facilitate the recovery of contaminants so that they can be easily stored and disposed of.

[0010] Another object is to provide a device for removing substances in suspension in a gaseous fluid that makes it possible to facilitate maintenance operations without disrupting the continuity of operation.

[0011] Another objective is to allow for strong and rapid cooling. Summary of the Invention

[0012] The present invention relates to a device for the strong / rapid cooling and removal of substances in suspension in a gaseous fluid, said device comprising:

[0013] i) a conveying means for conveying a gaseous fluid;

[0014] ii) A system for alternatively condensing / freezing or defrosting substances present in a gaseous fluid, comprising: a first group of cooling or defrosting stages arranged in succession along a section of the conveying means, a second group of cooling or defrosting stages arranged in succession along the conveying means, - means for collecting substances, a system comprising conveying means with first and second lines arranged operatively in parallel, a first group of cooling or defrosting stages being arranged along the first line and a second group of cooling or defrosting stages being arranged along the second line, iii) a heat exchanger for pre-cooling the gaseous fluid upstream of the first group or the second group; conveying means for conveying the gaseous fluid present downstream of the first or second group to a heat exchanger and for removing heat from the gaseous fluid present upstream of the first or second group passing through the heat exchanger; iv) a directing means for directing the fluid alternately to the first line or the second line; and vi) a first fan and a second fan disposed along the conveying means, a first fan is arranged upstream of the first group and the second group of cooling or defrosting stages, and a second fan is arranged downstream of the first group and the second group; The system includes a first fan and a second fan, wherein a volumetric flow rate of the gaseous fluid generated by the first fan is greater than a volumetric flow rate of the air generated by the second fan.

[0015] Preferably, the first and second lines converge in a junction zone located downstream of the first and second groups of cooling or defrosting stages, said first fan being arranged upstream of the induction means and said second fan being arranged downstream of the junction zone.

[0016] Advantageously, the heat exchanger comprises: a first zone of conveying means located upstream of the first and second groups of cooling or defrosting stages; - being arranged in thermal communication with a second zone of the conveying means located downstream of the first and second groups of cooling or defrosting stages;

[0017] In a particular embodiment, the first group of cooling or defrosting stages comprises a first unit, a second unit and a third unit, and the second group of cooling or defrosting stages comprises a first unit, a second unit and a third unit, each pair of units (first unit, second unit, third unit) comprising a cooling circuit, which circuit comprises: - an evaporator of the working fluid, located in each unit; - a throttle valve for the working fluid, located in each unit; a condenser for the working fluid, located outside the units and connected to each pair of units; - a compressor for the working fluid arranged outside the units and connected to each pair of units;

[0018] Preferably, the pair of third units further comprises subcooling means, advantageously comprising a further compressor and a heat exchanger.

[0019] Preferably, the device comprises cooling means for cooling the working fluid, said cooling means being interposed between the condenser and the throttle valve.

[0020] Advantageously, the cooling circuit comprises two receivers of the liquid phase of the working fluid, said two receivers being in series with one another and being located downstream of the condenser and upstream of the throttle valve along the direction of circulation of the working fluid in the cooling circuit.

[0021] In one embodiment, the cooling circuit comprises cooling means for cooling the working fluid, said cooling means being interposed between the condenser and the throttle valve.

[0022] In certain embodiments, the first line and the second line are: Advantageously - a chamber located along the gaseous fluid conveying means after the first and second groups, a refrigerant channel in thermal communication with the chamber for cooling a gaseous fluid; - a solid body located inside the chamber, an inlet port for the entry of a gaseous fluid into the chamber; - providing an outlet port for the exit of the gaseous fluid from the chamber.

[0023] Preferably, gaseous nitrogen is present in at least one portion of the coolant channel that is in thermal contact with the chamber.

[0024] The coolant channel preferably comprises a coil passing inside the chamber.

[0025] In certain embodiments, the solid occupies the space surrounding the coil.

[0026] Preferably, the solid comprises Raschig rings.

[0027] In some embodiments, the apparatus comprises a Stirling refrigerator, said Stirling refrigerator being located downstream of a connection zone of the first and second lines.

[0028] The Stirling refrigerator preferably comprises: - cycle fluid, - a heat sink that dissipates the heat of the cycle fluid to the outside of the Stirling refrigerator; a low temperature zone in thermal communication with the gaseous fluid; - a line connecting the heat sink with the low-temperature zone through which the cycle fluid moves; -Provided with means for compressing / expanding the cycle fluid.

[0029] Additionally, the present invention relates to a method for strongly / rapidly cooling and removing substances in suspension in a gaseous fluid,

[0030] conveying a fluid inside an apparatus comprising a first group of cooling or defrosting stages and a second group of cooling or defrosting stages, the first group of cooling or defrosting stages being arranged along a first line and the second group of cooling or defrosting stages being arranged along a second line, said first line and said second line being arranged to be able to operate in parallel, - directing a fluid alternately into a first line or a second line, wherein a first fan located upstream of the first and second groups of cooling or defrosting stages generates a volumetric flow rate of gaseous fluid that is greater than the air flow rate generated by a second fan located downstream of the first and second groups of cooling or defrosting stages.

[0031] Advantageously, the first group comprises a cooling stage, while the second group comprises a defrosting stage.

[0032] In a preferred embodiment, the first or second group of cooling stages comprises at least a first, second and third stage; - The first stage allows for a temperature difference of approximately 10 to 30°C and the removal of moisture, - The second stage allows a temperature jump of approximately 40-50°C compared to the temperature of the first stage, The third stage allows a temperature jump of approximately 40°C compared to the temperature of the second stage.

[0033] Further features and advantages of the present invention will become more clearly apparent from the approximate, and therefore non-limiting, description of preferred but non-exclusive embodiments of the device as shown in the accompanying drawings. [Brief explanation of the drawings]

[0034] [Figure 1] FIG. 1 shows a perspective view of the device according to the invention. [Figure 2] FIG. 2 shows a side view of the device of FIG. [Figure 3] FIG. 3 shows a plan view of the device of FIG. [Figure 4] FIG. 4 shows a schematic representation of a cooling circuit according to one embodiment of the present invention. [Figure 5] FIG. 5 shows a schematic representation of a cooling circuit according to one embodiment of the present invention. [Figure 6] FIG. 6 shows a schematic representation of a cooling circuit according to another embodiment of the invention. [Figure 7] FIG. 7 shows a schematic representation of a Stirling refrigerator according to the invention. [Figure 8] FIG. 8 shows a schematic representation of a chamber according to the invention. DETAILED DESCRIPTION OF THE INVENTION

[0035] In the accompanying drawings, reference number 1 designates an apparatus for intense / rapid cooling and for removing substances in suspension in a gaseous fluid.

[0036] The device 1 allows the treatment of gaseous fluids, preferably air to be cooled / condensed, or for the separation and recovery of pollutants such as solvents (volatile organic compounds, aliphatics, hydrocarbons, oils, acids).

[0037] The apparatus 1 comprises a conveying means 2 for conveying a gaseous fluid. The conveying means 2 typically comprises a set of conduits for conveying the gaseous fluid. The apparatus 1 comprises a system 3 for condensing / freezing substances present in the gaseous fluid. The system 3 is arranged along the conveying means 2. The system 3 advantageously comprises a first group 31 of cooling or defrosting stages and a second group 32 of cooling or defrosting stages arranged in succession along a section of the conveying means 2.

[0038] 1, when operating in cooling mode, the first group of cooling stages 31 or the second group of cooling stages 32 comprises at least a first, second and third stage, the stages of the first group 31 extending one after the other in series.

[0039] Conveniently: The first stage can allow a temperature difference of about 10 to 30°C and the removal of moisture (for example, the gaseous fluid can reach a temperature of -5 to -10°C), The second stage can allow a temperature jump of approximately 40-50°C compared to the temperature of the first stage (e.g., the gaseous fluid can reach a temperature of approximately -50°C),

[0040] The third stage may allow a temperature jump of approximately 40°C compared to the temperature of the second stage (for example, the gaseous fluid may reach a temperature of approximately -100°C).

[0041] Additionally or alternatively, the cooling or defrosting stage may include various refrigerators, such as Stirling cycle, coiled chamber, Raschig ring, etc., which are better described below and are mentioned here only. Such refrigerators are typically used to reach very low temperatures of gaseous fluids. In certain configurations, the device 1 may also reach temperatures below -270°C.

[0042] The system 3 also comprises material recovery means 347. Indeed, the condensed material is then collected for discharge. In at least one (but usually all) of the refrigeration stages, a separator is provided to separate the liquid droplets from the gaseous fluid. It may be of a turbulent nature or of another type. To facilitate the collection of the condensed material, a vacuum pump may be used, which draws the condensed material into a collection tank. Once ice is produced, defrosting cycles are required to allow periodic percolation of the frozen product.

[0043] The device 1 comprises a heat exchanger 4 for pre-cooling a gaseous fluid. The heat exchanger 4 is intended to pre-cool the gaseous fluid upstream of the first group 31, the second group 32 of cooling or defrosting stages. It is a gas-gas (or rather air-air) exchanger. For example, it can be a tube bundle heat exchanger 4 (in particular it can be a finned tube heat exchanger).

[0044] In this regard, the conveying means 2 also comprises means 5 for conveying the gaseous fluid present downstream of the first group 31 or the second group 32 of cooling or defrosting stages to the heat exchanger 4. In this way, heat is removed from the gaseous fluid present upstream of the first group 31 or the second group 32 of cooling or defrosting stages and passing through the exchanger 4. In the exchanger 4, the gaseous fluid present downstream of the first group 31 or the second group 32 is slightly heated before being released into the atmosphere (via the stack), thereby making it possible to recover energy.

[0045] In the heat exchanger 4, the gaseous fluid present upstream of the first group 31 or the second group 32 and the gaseous fluid present downstream of the first group 31 or the second group 32 do not advantageously mix (despite being in thermal contact).

[0046] However, advantageously, the heat exchanger 4 a first zone 21 of the conveying means 2 located upstream of the first and / or second group 31, 32 of cooling or defrosting stages; being arranged in thermal communication with a second zone 22 of the conveying means 2 located downstream of the first and / or second group 31, 32 of cooling or defrosting stages;

[0047] The conveying means 2 in fact comprises a first line 311 and a second line 321 arranged operatively in parallel. A first group 31 of cooling or defrosting stages is arranged along the first line 311. A second group 32 of cooling or defrosting stages is arranged along the second line 321. In particular, the first line 311 and the second line 321 are structurally identical.

[0048] The device 1 comprises directing means 6 for directing the fluid alternately to the first line 311 or the second line 321. The directing means 6 comprises means for directing the gaseous fluid towards the first line 311 or the second line 321, for example towards one or more valves, preferably two valves 340, 341.

[0049] The two lines 311, 321 exist in parallel and innovatively, with one line performing a defrosting operation and the other line performing an operation of cooling the gaseous fluid, thereby ensuring the continuity of operation of the entire device 1.

[0050] As illustrated in FIG. 1 , the device 1 comprises a first fan 71 and a second fan 72 located along the fluid conveying means 2. The first fan 71 is preferably located upstream of the first group 31 and the second group 32 of stages. The second fan 72 is located downstream of the first group 31 and the second group 32 of cooling or defrosting stages. In at least one operating mode, the volumetric flow rate of the gaseous fluid generated by the first fan 71 is greater than the air flow rate generated by the second fan 72. In this regard, the device 1 can comprise control means (not shown) for controlling the first fan 71 and the second fan 72. In particular, the control means can adjust the operation of the first fan 71 and the second fan 72 independently of each other. Such a difference in air flow rates causes an overpressure in the gaseous fluid.

[0051] The control means are used to control and regulate the fans 71, 72 connected to appropriate sensors to control the parameters of the fluid flow, e.g. temperature, speed, pressure, humidity, etc., and thereby to appropriately adjust the fans (rotation speed, blade inclination, etc.) to move the fluid flow, and also take into account the changes in the volume of the gaseous fluid inside the device during the various operating steps (ignition, transient, normal operation).

[0052] For example, the control means can adjust the rotation speed or drive torque or blade inclination of the first fan 71 and / or the second fan 72. Typically, the first fan 71 and / or the second fan 72 are centrifugal fans.

[0053] 1, the first line 311 and the second line 321 pass through the chamber 8 and a pair of end valves 342 and 343 and converge into a junction zone 300 located downstream of the first group 31 and the second group 32 of stages. The first fan 71 is located upstream of the induction means 6. The second fan 72 is located downstream of the junction zone 300.

[0054] Advantageously, the first group (31) of cooling or defrosting stages comprises a first unit (301 a), a second unit (302 a) and a third unit (303 a), and the second group (32) of cooling or defrosting stages comprises a first unit (301 b), a second unit (302 b) and a third unit (303 b), each pair of units (first unit, second unit, third unit) comprising a cooling circuit (33), said circuit comprising: an evaporator (331, 338) for the working fluid arranged in each unit (301a, 301b, 302a, 302b, 303a, 303b); - throttle valves (334, 339) for the working fluid, arranged in each unit (301a, 301b, 302a, 302b, 303a, 303b); - a condenser (333) for the working fluid, located outside the units and connected to each pair of units; - a compressor (332) for the working fluid arranged outside the units and connected to each pair of units;

[0055] Advantageously, the pair of third units (303a, 303b) further comprises subcooling means, which advantageously comprise a further compressor (344) and a heat exchanger (345).

[0056] The working fluid preferably circulates in a cooling circuit 33. The working fluid may be Freon or another refrigerant.

[0057] Advantageously, one of the two groups of cooling or defrosting stages 31, 32 operates as a cooler for the gaseous fluid, while the other group of cooling or defrosting stages 31, 32 is frozen after the cooling operation and undergoes defrosting, these operations being carried out in parallel.

[0058] FIG. 4 illustrates a particular embodiment showing the cooling circuits 33 of a pair of first units 301a, 301b and a pair of second units 302a, 302b.

[0059] 4, once the gaseous fluid has been cooled in the group 32 of cooling or defrosting stages, the working fluid circulating in the cooling circuit 33 of the pair of first units 301a, 301b and the pair of second units 302a, 302b enters the compressor 332 as a low pressure liquid and exits as a hot gas (e.g., at a pressure of 32 bar), which causes it to flow into the condenser 333. The pressure of the working fluid gas is slightly reduced (e.g., to 28 bar) and it is slightly cooled.

[0060] Preferably, the cooling circuit 33 comprises two receivers 336 for the liquid phase of the working fluid, said two receivers 336 being in series with one another and located downstream of the condenser 333 and upstream of the throttle valve 339 along the direction of circulation of the working fluid in the cooling circuit 33. The receivers 336 prevent slagging of the liquid in the compressor 332.

[0061] Condensation of the gas can lead to the formation of droplets, which are collected in two receivers 336. After entering the condenser 333, the gas is directed to a throttle valve 339 where it is throttled to a lower pressure (e.g., 0.6 bar). Thus, the fluid upstream of the throttle valve 339 is cooled to enhance performance in subsequent throttling.

[0062] The working fluid enters the evaporator 338 where it is combined with the gaseous fluid to be decontaminated. The gaseous fluid is cooled and the working fluid is heated. The evaporator 338 removes heat from the gaseous fluid passing along the conveying means 2, thereby causing the working fluid gas to transition to a liquid phase.

[0063] The working fluid enters compressor 332 and undergoes the same cycle.

[0064] In parallel, the other group 31 of cooling or defrosting stages is frozen and defrosted. After being compressed in the compressor 332, the working fluid flows into the branch 337 and into the throttle valve 334, where the working gas fluid is throttled and its pressure is reduced. It flows into the evaporator 331 for defrosting. In doing so, the frozen material is liquefied and recovered in the material recovery means 347. The working fluid gas is liquefied in the evaporator 331 and flows back to the compressor 332.

[0065] 5 shows a cooling unit 33 included in a pair of third units 303a, 303b, in which one group 31 of cooling or defrosting stages is frozen and defrosted. After being compressed into a compressor 332, the working fluid circulates in a similar manner as described above by entering a branch 337 and heading to a throttle valve 334, where it is throttled and its pressure is reduced. The working fluid then flows into an evaporator 331 for defrosting, thus defrosting the material. The working fluid then flows back to the compressor 332. It enters a heat exchanger 345, preferably a plate exchanger, where it comes into contact with a second working fluid that circulates into the subcooling system.

[0066] The subcooling system for circulating the second working fluid comprises a compressor 344 and a condenser 333. Preferably, the second working fluid is of a different type to the working fluid compressed in compressor 332.

[0067] The second working fluid passes through compressor 344 and then enters condenser 333 where it is cooled. It then flows into receiver 336, located downstream of condenser 333. The fluid enters heat exchanger 345, where it cools the working fluid coming from compressor 332. The second working fluid then flows back into compressor 344, allowing the gas to be further cooled in evaporator 338.

[0068] The cooled working fluid flows into a receiver 336 and then into an evaporator 338 to cool the gaseous fluid being processed.

[0069] In another embodiment of the invention shown in FIG. 6, the cooling circuit comprises cooling means 335 for cooling the working fluid, said cooling means 335 being interposed between the condenser 333 and the throttle valves 334, 339.

[0070] Cooling means 335 make it possible to liquefy part of the working fluid, still in the gas phase, which is then fed to compressor 332 and undergoes the same cycle as described above.

[0071] In certain embodiments, the first and second lines 311, 321 are: a chamber 8, advantageously located along the gaseous fluid conveying means (2) after the first group (31) and the second group (32), a coolant channel 83 in thermal communication with the chamber 8 for cooling a gaseous fluid; nitrogen gas is present in at least one section of the coolant channel 83 that is in thermal contact with the chamber 8, Advantageously, the coolant channel 83 comprises a coil 84 passing inside the chamber 8. a solid body 85 located inside the chamber 8, advantageously occupying the space of the coil 84; an inlet port 81 for the entry of a gaseous fluid into the chamber 8; - Providing an outlet port 82 for the exit of the gaseous fluid from the chamber 8.

[0072] Advantageously, the solid 85 comprises Raschig rings 850. The solid preferably increases the contact surface between the liquid and gas phases of the fluid.

[0073] FIG. 8 shows only a portion of the solid 85 .

[0074] Chamber 8 is the final stage of refrigeration of the first group 31 and the second group 32. It is therefore the stage closest to the connection area 300 connecting the first line 311 and the second line 321.

[0075] In one particular embodiment, the device 1 comprises a Stirling refrigerator 9. The Stirling refrigerator 9 is located downstream of the connection zone of the first line 311 and the second line 321. In particular, the Stirling refrigerator 9 is located downstream of the connection zone 300 of the first line 311 and the second line 321. Thus, the Stirling refrigerator 9 is located downstream of the section where the first line 311 and the second line 321 are connected.

[0076] The Stirling refrigerator 9 contains a cycle fluid, for example helium or another fluid, in which no change of state occurs.

[0077] 7, the Stirling refrigerator 9 also comprises a heat sink 91 that dissipates the heat of the cycle fluid towards the outside of the Stirling refrigerator 9. Advantageously, the heat sink 91 is a heat exchanger that dissipates heat towards, for example, the outside air or water.

[0078] The Stirling refrigerator 9 further comprises a low temperature zone 92 in thermal communication with the gaseous fluid.

[0079] The Stirling refrigerator 9 further comprises a line 95 connecting the heat sink 91 and the low temperature zone 92. A cycle fluid travels in the line 95.

[0080] The Stirling refrigerator 9 further comprises means 93 for compression / expansion of the cycle fluid.

[0081] Compression / expansion means 93 are means for alternately moving the cycle fluid along connecting line 95. Means 93 allow for the compression of the fluid adjacent to heat sink 91 and the expansion of the fluid in cold zone 92. Preferably, compression / expansion means 93 comprises a suitable piston.

[0082] A connecting line 95 extends between the compression / expansion means 93 and the cold zone 92. A heat sink 91 is arranged along the line 95.

[0083] The Stirling refrigerator 9 comprises a heat accumulator 94 interposed between the heat sink 91 and the low-temperature zone 92. The heat accumulator 94 exchanges heat with the cycle fluid. In particular, it absorbs heat and then returns it to the cycle fluid. The Stirling refrigerator 9 also comprises a displacer 96 interposed between the heat sink 91 and the low-temperature zone 92. In particular, the displacer 96 and the heat accumulator 94 are integrated in the same moving body. The displacer 96 can be shaped like a piston.

[0084] Advantageously, the heat sink 91 is interposed between the means 93 and the displacer 96. The displacer 96 is interposed between the heat sink 91 and the cold zone 92.

[0085] During operation, the compression / expansion means 93 compresses and therefore heats the cycle fluid, which however is partially cooled as it transfers heat to the outside via the heat sink 91. The cycle fluid therefore passes through the displacer 96 / regenerator 94 and reaches the low temperature zone 92.

[0086] As the cycle fluid passes through the heat accumulator 94, it transfers some of its heat to the heat accumulator. The compression / expansion means 93 cyclically causes expansion of the cycle fluid in the low temperature zone 92, thus providing further cooling. The compression / expansion means 93 then withdraws the cycle fluid, which as it passes through the heat accumulator 94 withdraws some of the heat previously transferred.

[0087] The cycle fluid in the cold zone 92 thus removes heat from the gaseous fluid. A displacer 96 is located along the connecting line 95. The displacer 96 moves on a seat 97, at one end of which the cold zone 92 is located. The Stirling refrigerator 9 also comprises elastic means 98 which pull the displacer 96 towards a predetermined position.

[0088] The present invention achieves important advantages.

[0089] Firstly, it facilitates the maintenance and correct operation of the equipment. In fact, it may be necessary to periodically defrost the first line 311, allowing the operation of the second line 321 in such circumstances, and vice versa. Likewise, the placement of a pre-cooling system upstream of the separation of the first and second lines allows for component optimization and avoids pointless redundancies. Thus, there is a validated distribution of the individual cooling components that allows for certain synergistic effects.

[0090] Thanks to the alternatively operable chamber 8 and the two parallel lines 311, 321, continuous operation of the device is possible without interruption, temperatures down to -176°C, and costs are reduced compared to prior art solutions. All details of the invention can be replaced by technically equivalent elements. All materials and dimensions used can be practically optional, depending on the needs.

Claims

1. 1. An apparatus for intense / rapid cooling and removal of substances in suspension in a gaseous fluid, said apparatus comprising: i) a conveying means (2) for conveying said gaseous fluid; ii) a system (3) for alternatively condensing / freezing or defrosting said substance present in said gaseous fluid, comprising: a first group (31) of cooling or defrosting stages arranged in succession along a section of said conveying means (2); a second group (32) of cooling or defrosting stages arranged in succession along said conveying means (2); - means (347) for collecting said material; a system (3) comprising said conveying means (2) with first and second lines (311, 321) arranged in parallel and operable, said first group of cooling or defrosting stages (31) being arranged along said first line (311) and said second group of cooling or defrosting stages (32) being arranged along said second line (321); iii) a heat exchanger (4) for pre-cooling the gaseous fluid upstream of the first group (31) or the second group (32); iv) the conveying means (2) comprising means (5) for conveying the gaseous fluid present downstream of the first group (31) or the second group (32) to the heat exchanger (4) and for removing heat from the gaseous fluid present upstream of the first group (31) or the second group (32) passing through the heat exchanger (4); v) a directing means (6) for directing the fluid alternately to the first line or the second line (311, 321); vi) a first fan (71) and a second fan (72) arranged along the conveying means (2), the first fan (71) is located upstream of the first group (31) and the second group (32), and the second fan (72) is located downstream of the first group (31) and the second group (32); An apparatus comprising a first fan (71) and a second fan (72), wherein a volumetric flow rate of the gaseous fluid generated by the first fan (71) is greater than a volumetric flow rate of air generated by the second fan (72).

2. 2. The device according to claim 1, characterized in that the first line (311) and the second line (321) converge in a connection zone (300) located downstream of the first and second groups (31, 32) of cooling or defrosting stages, the first fan (71) being arranged upstream of the induction means (6) and the second fan (72) being arranged downstream of the connection zone (300).

3. The heat exchanger (4) a first zone (21) of said conveying means (2) located upstream of said first and second groups (31, 32) of cooling or defrosting stages; 3. A device according to claim 1 or 2, characterized in that the first and second groups (31, 32) of cooling or defrosting stages are arranged in thermal communication with a second zone (22) of the conveying means (2) located downstream.

4. The first group (31) of cooling or defrosting stages comprises a first unit (301a), a second unit (302a) and a third unit (303a), and the second group (32) of cooling or defrosting stages comprises a first unit (301b), a second unit (302b) and a third unit (303b), each pair of units (first unit, second unit, third unit) comprising a cooling circuit (33), said circuit comprising: an evaporator (331, 338) of the working fluid, arranged in each unit (301a, 301b, 302a, 302b, 303a, 303b); a throttle valve (334, 339) for said working fluid, located in each unit (301a, 301b, 302a, 302b, 303a, 303b); a condenser (333) for the working fluid, located outside the units and connected to each pair of units; A device according to any one of claims 1 to 3, characterized in that it comprises a compressor (332) for the working fluid, located outside the units and connected to each pair of units.

5. 5. Apparatus according to claim 4, characterized in that the pair of third units (303a, 303b) further comprise subcooling means, advantageously comprising a further compressor (344) and a heat exchanger (345).

6. 6. The device according to claim 4 or claim 5, characterized in that the cooling circuit (33) comprises two receivers (336) of the liquid phase of the working fluid, the two receivers (336) being in series with each other and being located downstream of the condenser (333) and upstream of the throttle valves (334, 339) along the direction of circulation of the working fluid in the cooling circuit (33).

7. 7. The device according to claim 4, wherein the cooling circuit (33) comprises cooling means (335) for cooling the working fluid, the cooling means (335) being interposed between the condenser (333) and the throttle valve (334, 339).

8. The first line (311) and the second line (321) a chamber (8) located along the conveying means (2) for the gaseous fluid after the first group (31) and the second group (32); - a coolant channel (83) in thermal communication with said chamber (8) for cooling said gaseous fluid; a solid body (85) located inside said chamber (8); an inlet port (81) for the entry of said gaseous fluid into said chamber (8); A device according to any one of claims 1 to 7, characterized in that it comprises an outlet port (82) for the exit of said gaseous fluid from said chamber (8).

9. 9. The apparatus of claim 8, wherein the solid body (85) comprises a Raschig ring.

10. 10. The device according to any one of claims 1 to 9, characterized in that it comprises a Stirling refrigerator (9), said Stirling refrigerator (9) being arranged downstream of a connection zone (300) of said first line (311) and said second line (321).

11. The Stirling refrigerator (9), - a cycle fluid; a heat sink (91) for dissipating the heat of the cycle fluid to the outside of the Stirling refrigerator (9); a cold zone (92) in thermal communication with said gaseous fluid; a line (95) connecting said heat sink (91) with said cold zone (92) through which said cycle fluid moves; A device according to claim 10, characterized in that it comprises means (93) for compressing / expanding said cycle fluid.

12. 1. A method for the strong / rapid cooling and removal of substances in suspension in a gaseous fluid, comprising: - conveying said gaseous fluid inside an apparatus comprising a first group of cooling or defrosting stages (31) and a second group of cooling or defrosting stages (32), said first group of cooling or defrosting stages (31) being arranged along a first line (311) and said second group of cooling or defrosting stages (32) being arranged along a second line (321), said first line (311) and said second line (321) being arranged to be able to operate in parallel; - directing the gaseous fluid alternately into the first line or the second line (311, 321), wherein a first fan (71) located upstream of the first (31) and second (32) groups of cooling or defrosting stages generates a volumetric flow rate of the gaseous fluid that is greater than the air flow rate generated by a second fan (72) located downstream of the first and second (31, 32) groups of cooling or defrosting stages.

13. 13. A method according to claim 12, characterized in that the first group (31) comprises a cooling stage, while the second group (32) comprises a defrosting stage.

14. the first group (31) or the second group (32) of cooling stages comprises at least a first stage, a second stage and a third stage; - said first stage allows a temperature difference of about 10-30°C and said removal of moisture, - the second stage allows a temperature jump of about 40-50°C compared to the temperature of the first stage, A method according to claim 12, characterized in that the third stage allows a temperature jump of approximately 40° C. compared to the temperature of the second stage.

Images