EP3748270B1 - Hybrid tube bundle evaporator - Google Patents
Hybrid tube bundle evaporator Download PDFInfo
- Publication number
- EP3748270B1 EP3748270B1 EP20175886.9A EP20175886A EP3748270B1 EP 3748270 B1 EP3748270 B1 EP 3748270B1 EP 20175886 A EP20175886 A EP 20175886A EP 3748270 B1 EP3748270 B1 EP 3748270B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tubes
- evaporator
- tube bundle
- shell
- refrigerant fluid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000012530 fluid Substances 0.000 claims description 76
- 239000003507 refrigerant Substances 0.000 claims description 46
- 238000005192 partition Methods 0.000 claims description 20
- 238000000034 method Methods 0.000 claims description 15
- 230000008569 process Effects 0.000 claims description 15
- 239000007788 liquid Substances 0.000 claims description 7
- 238000005057 refrigeration Methods 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 4
- 230000000630 rising effect Effects 0.000 claims description 4
- 230000006835 compression Effects 0.000 claims description 3
- 239000007792 gaseous phase Substances 0.000 description 14
- 238000009826 distribution Methods 0.000 description 12
- 230000037361 pathway Effects 0.000 description 9
- 230000005484 gravity Effects 0.000 description 5
- 239000007791 liquid phase Substances 0.000 description 5
- 239000011552 falling film Substances 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- 230000003287 optical effect Effects 0.000 description 2
- 230000000750 progressive effect Effects 0.000 description 2
- 238000006424 Flood reaction Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010924 continuous production Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000003698 laser cutting Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000012071 phase Substances 0.000 description 1
- 239000002244 precipitate Substances 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
- F28D7/1607—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D3/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits
- F28D3/04—Distributing arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
Definitions
- the present invention refers to an improved hybrid tube bundle evaporator having a low-load and high performance for vapour compression refrigeration circuits.
- tube bundle and shell evaporators for known-type vapour compression refrigerating circuits, constituted substantially by a tube bundle inside a recipient usually having a cylindrical shape with a horizontal axis, usually known as a "shell", and closed at the ends.
- the device is crossed by two fluid currents: a current corresponding to the process fluid, i.e. the fluid that is to be cooled, which flows on the "tube-side", that is, inside the tubes, while the other current corresponds to the service fluid, i.e. the refrigerant fluid used as the vector of the heat exchange and which flows on the "shell-side", i.e. in the space delimited between the inner surface of the shell and the outer surfaces of the tubes; the large outer surfaces of the tubes, generally having a modest diameter and in a large number, enable heat exchange of large quantities of heat.
- the pathway of the tube bundle inside the shell can be straight, with a parallel axis to the longitudinal axis of the evaporator, from an inlet head to the opposite outlet head, or can be straight but with an outward and return pathway over the whole length of the shell, with an inlet and outlet at the same evaporator head; the type depends on the general characteristics of the system and the design choices and expected performances.
- the process that takes place inside an evaporator in a refrigeration circuit is a continuous process, through which the flow of the service refrigerant fluid at a lower temperature subtracts heat from the process fluid flow at a higher temperature, and in turn heats up and changes from the liquid phase to the gaseous phase.
- the flooded type i.e. with the tube bundle completely immersed in the service fluid in the moist phase
- the low-load flooded type in which the service fluid load is reduced coherently with the setting and control of other parameters of the system
- the falling film type in which the tubes are sprinkled by the service refrigerant fluid which falls in cascade
- the spray type where the service refrigerant fluid is sprayed onto the tubes.
- hybrid Another type, known as hybrid, pairs the characteristics of the low-load flooded type with those of the falling film type.
- US 2010/276130 A1 discloses a horizontal tube bundle evaporator according to the preamble of claim 1.
- the technical task of the present invention is, therefore, to provide a tube bundle evaporator which obviates the above-described technical drawbacks of the prior art.
- an object of the invention is to realise a tube bundle evaporator of a hybrid type, which unites the characteristics of the low-load flooded type and of the falling film type, thus obviating the drawbacks of both.
- a further aim of the invention is to realise a tube bundle evaporator of a hybrid type which optimises the fluid-dynamics of the service fluid and the heat exchange with the process flow.
- a further aim of the invention is to realise a tube bundle evaporator of a hybrid type from which the service fluid in outlet can be returned to the refrigeration circuit prevalently in the gaseous phase.
- a further aim of the invention is to realise a tube bundle evaporator of a hybrid type which improves the distribution system of the service fluid on the tube bundle.
- a further aim of the invention is to realise a tube bundle evaporator of a hybrid type which optimises the positions of the fittings towards the external devices.
- a horizontal axis hybrid tube bundle evaporator is denoted in its entirety by reference number 1, essentially constituted by a cylindrical shell 2, by two closing heads 3A and 3B, a tube bundle 4 thus identified in its entirety and contained inside the shell 2 where the tubes individually perform an outward and return pathway parallel to the longitudinal horizontal axis and over the whole length of the shell 2, an inlet 5 in a closing head 3A of the process fluid to be cooled and an outlet 6 in a closing head 3A of the cooled process fluid;
- the evaporator 1 further has two inlets 7A and 7B of the service refrigerant fluid in the liquid state in a lower lateral zone of the shell 2, symmetrically arranged in the direction of the longitudinal axis with respect to an outlet 8 of the service refrigerant fluid in the gaseous state positioned in an upper lateral zone of the shell 2, and an optical viewer 9 for controlling the level of the service refrigerant fluid on the lower lateral wall of the shell 2.
- a first number of tubes 41 of the tube bundle 4 is positioned in a lower zone 21 of the evaporator 1 flooded by the service fluid, a second number of tubes 42 is positioned in an upper zone 22 of the evaporator 1 above the first number of tubes 41.
- a distributor 70 of the service refrigerant fluid is positioned in an upper zone 22 of the evaporator 1 above the second number of tubes 42 of the tube bundle 4, and is constituted by two opposite collectors 71A and 71B respectively connected to the inlets 7A and 7B of the refrigerant fluid in the evaporator 1, and mounted with a perpendicular axis to the longitudinal axis of the evaporator 1 and of the tube bundle 4.
- a plurality of straight distribution tubes 72i is perpendicularly connected to both collectors 71A and 71B, by means of respective fittings 73i at the ends thereof, with a longitudinal axis parallel to the axis of the evaporator 1 and the tube bundle 4.
- the tube bundle 4 is supported inside the shell 2 by a plurality of transversal support plates 80i perpendicular to the longitudinal axis of the tubes and the evaporator 1, appropriately perforated for guided and continuous passage of the single tubes and appropriately configured for mounting inside the evaporator 1.
- a further plurality of vertical longitudinal secondary partitions 81i advantageously joint-fixed to the transversal support plates 80i longitudinally divides, into a plurality of sectors, the second number of tubes 42 of the tube bundle 4 in the zone 22 of the evaporator 1.
- the transversal support plates 80i further divide the longitudinal sectors into sub-units.
- transversal support plates 80i and the longitudinal partitions 81i have appropriate pluralities of savings and through openings, respectively 82i and 83i which have the function of equalising the pressure of the refrigerant fluid between these sectors and sub-units inside the evaporator 1.
- a plurality of longitudinal deflecting fins 85ni is further fixed on the longitudinal partitions 81i, again with the aim of equalising the flow distribution of the refrigerant fluid by force of gravity on the tubes of the second number of tubes 42.
- a special primary vertical partition 88 longitudinally extended, conjoined at the top thereof to the internal lateral surface of the shell 2 and inferiorly extending downwards up to a suitable distance from the free surface of the flooded lower zone 21 for collecting the refrigerant fluid in the liquid state.
- the primary vertical partition 88 divides the upper zone 22 of the evaporator in which it defines a first upper chamber 23 in which the second number of tubes 42 and the distributor 70 of the service refrigerant fluid are housed, and a second upper lateral chamber 24 of the evaporator 1, towards the side of the shell 2 where the inlets 7A and 7B are located, to which the distributor 70 and the outlet 8 of the refrigerant fluid in the gaseous state are connected.
- a third number of tubes 43 connected via a collector 51 in the head 3A is housed inside the second upper lateral chamber 24 of the evaporator 1.
- the head 3 A has the inlet collector 51 connected to the inlet 5 of the process fluid in the evaporator 1, and an outlet collector 61 connected to the outlet 6 of the cooled process fluid; the inlet collector 51 supplies the first number of tubes 41, the third number of tubes 43 and the lower group of tubes of said second number of tubes 42; and an outlet collector 61 is supplied by an upper group of tubes of said second number of tubes 42.
- the process fluid to be cooled is introduced into the evaporator 1 through the inlet 5 in the head 3A, and thus in the inlet collector 51 from which it is distributed into the first number of tubes 41, the third number of tubes 43 and the lower group of tubes of the second number of tubes 42.
- the process fluid to be cooled coming from the system circulation and appropriately moved by movement means outside the evaporator, travels through the tubes in a horizontal-axis outward and return pathway inside the evaporator 1 over the whole length of the shell 2.
- the upper group of tubes of the second number of tubes 42 thus returns to the outlet collector 61 in the head 3A, from which the appropriately-cooled process fluid is collected and connected to the outlet 6 from the evaporator 1 and reinjected into the cooling system circulation of which the evaporator is a part.
- the service refrigerant fluid in the liquid state coming from other lines of the cooling system and appropriately moved by movement means outside the evaporator, is injected into the evaporator 1 symmetrically, given equal conditions of temperature and pressure, through the two inlets 7A and 7B positioned in the lower lateral zone of the shell 2 the inside of which corresponds to the second upper lateral chamber 24 of the evaporator 1.
- the two opposite collectors 71A and 71B are respectively connected to the inlets 7A and 7B of the fluid distributor 70 of the service refrigerant fluid, via which collectors and via the successive plurality of fittings 73i derived therefrom, the refrigerant fluid reaches the plurality of distribution tubes 72i from opposite ends.
- the supply of the refrigerant fluid from the collectors 71A and 71B to the opposite ends of the plurality of distribution tubes 72i advantageously guarantees the homogeneity of the temperature and pressure conditions of the refrigerant fluid in each tube and inside each of the tubes of the plurality of distribution tubes 72i.
- the refrigerant fluid locates, in the plurality of distribution tubes 72i, the plurality of lower longitudinal dispensing openings 74i, through which the refrigerated fluid in the liquid state sprinkles the second number of tubes 42 by force of gravity.
- the heat exchange by convection, between the refrigerant flow and the outer walls of the second number of tubes 42 inside which the process fluid flows at a higher temperature causes, among other things, the raising of the temperature of the refrigerant fluid, and a partial passage thereof from the liquid phase to the mixed-gaseous phase ("mist") and to the gaseous phase.
- the refrigerant fluid in its fall by force of gravity from the plurality of lower longitudinal dispensing openings 74i in the plurality of distribution tubes 72i on the second number of tubes 42, is compartmentalised into a plurality of sub-units of a plurality of sectors defined by the plurality of transversal support plates 80i and of vertical longitudinal partitions 81i.
- the plurality of longitudinal deflecting fins 85i fixed on the longitudinal partitions 81i advantageously facilitates the detachment of the refrigerant fluid that might have accumulated on the longitudinal partitions 81i during the liquid phase and a better and progressive redistribution on the rows of the second number of tubes 42 positioned inferiorly of the longitudinal deflecting fins 85i.
- the pluralities of savings and through openings, respectively 82i and 83i in the transversal support plates 80i and in the longitudinal partitions 81i which are compartmentalised into a plurality of sub-units of a plurality of sectors inside the evaporator 1, advantageously facilitate the uniformity of the distribution of the refrigerant fluid during the progressively gaseous and mixed-gaseous phase in the progressive fall thereof on the rows of the second number of tubes 42.
- the portion of refrigerant fluid still in the liquid phase after having sprayed the second number of tubes 42 by force of gravity, precipitates and is collected (floods) in the lower zone 21 of the evaporator 1, where the first number of tubes 41 of the tube bundle 4 is positioned and where the heat exchange is actuated in a static form by conduction between the refrigerant fluid in the liquid phase and the outer walls of the first number of tubes 41 of the tube bundle 4 which remains completely immersed (flooded) in the fluid.
- the level of the service refrigerant fluid in the flooded lower zone 21 is controlled, which level must be maintained, by an appropriate control and balancing of the functions of the system outside the evaporator 1, at a higher level than the upper horizontal row of the first number of tubes 41 of the tube bundle 4.
- the portion of refrigerant fluid in the gaseous and mixed-gaseous phase, created for the heat exchange realised with interaction of the refrigerant fluid and the second number of tubes 42 in the first upper chamber 23 of the evaporator 1, physically and naturally tending to vertically rise towards the top of the first upper chamber 23, is advantageously aspirated by means of an appropriate depression created by aspirating means outside the evaporator 1 at the outlet 8 from the shell 2, positioned at the upper lateral chamber 24 of the evaporator 1.
- the primary partition 88 in cooperation with the free surface of the collecting flooded lower zone 21, inferiorly delimits a connecting passage between the first upper chamber 23 where a descending portion of circuit extends, and the second upper lateral chamber 24 where a rising portion of circuit extends in succession to a descending portion of circuit of the tortuous pathway of the refrigerant fluid in the gaseous and mixed-gaseous phase.
- the tortuous pathway of the refrigerant fluid in gaseous and mixed-gaseous phase advantageously strikes, in the inversion from the descending portion of circuit to the rising portion of circuit, the upper horizontal row 44 of tubes of the first number of tubes 41 and thus actuates a heat exchange which tends to reduce the number of tubes 41 and thus actuates a heat exchange which tends to reduce the moisture of the mixed-gaseous phase which is still residual.
- the third number of tubes 43 is also housed in the second upper lateral chamber 24 and is arranged at a greater height than the horizontal row of tubes 44, which is further struck by the refrigerant fluid in the gaseous and mixed-gaseous phase in a rising portion of circuit of the tortuous pathway, actuating a further heat exchange which tends to eliminate the moisture still residual in the mixed-gaseous phase (mist).
- the refrigerated service fluid is advantageously thus distanced by the evaporator 1 from the outlet 8 and injected into the circuit of the refrigeration system in prevalently gaseous phase.
- a horizontal tube bundle evaporator according to the invention is particularly advantageous for optimisation of the fluid-dynamics of the service fluid and the heat exchange with the process flow.
- the materials used, as well as the dimensions, can be any according to the needs and the state of the art.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
- The present invention refers to an improved hybrid tube bundle evaporator having a low-load and high performance for vapour compression refrigeration circuits.
- For some time the market has offered tube bundle and shell evaporators for known-type vapour compression refrigerating circuits, constituted substantially by a tube bundle inside a recipient usually having a cylindrical shape with a horizontal axis, usually known as a "shell", and closed at the ends.
- The device is crossed by two fluid currents: a current corresponding to the process fluid, i.e. the fluid that is to be cooled, which flows on the "tube-side", that is, inside the tubes, while the other current corresponds to the service fluid, i.e. the refrigerant fluid used as the vector of the heat exchange and which flows on the "shell-side", i.e. in the space delimited between the inner surface of the shell and the outer surfaces of the tubes; the large outer surfaces of the tubes, generally having a modest diameter and in a large number, enable heat exchange of large quantities of heat.
- The pathway of the tube bundle inside the shell can be straight, with a parallel axis to the longitudinal axis of the evaporator, from an inlet head to the opposite outlet head, or can be straight but with an outward and return pathway over the whole length of the shell, with an inlet and outlet at the same evaporator head; the type depends on the general characteristics of the system and the design choices and expected performances.
- In extreme and simplistic synthesis, the process that takes place inside an evaporator in a refrigeration circuit is a continuous process, through which the flow of the service refrigerant fluid at a lower temperature subtracts heat from the process fluid flow at a higher temperature, and in turn heats up and changes from the liquid phase to the gaseous phase.
- In the literature and on the market at least four types of tube bundle evaporators are well-known: the flooded type, i.e. with the tube bundle completely immersed in the service fluid in the moist phase; the low-load flooded type, in which the service fluid load is reduced coherently with the setting and control of other parameters of the system; the falling film type, in which the tubes are sprinkled by the service refrigerant fluid which falls in cascade; of the spray type, where the service refrigerant fluid is sprayed onto the tubes.
- Another type, known as hybrid, pairs the characteristics of the low-load flooded type with those of the falling film type.
- As is known, each of these types has advantages and drawbacks: it is also known that exchangers at present in use require a considerable load of refrigerant fluid to improve the heat exchange, and adopt mechanical solutions that constrain the arrangement of the inlet and outlet fittings of the refrigerant fluid, which must necessarily be arranged respectively on the bottom and on the top of the shell.
- These traditional arrangements of the fittings lead to significant evaporator volumes and constraints with the other components of the system, often relevant.
- It is also known that all tube bundle evaporators have a service flow distribution in the shell that is not uniform, which can lead to a worsening of the evaporator performance.
- To reduce the effect of the non-uniform flow distribution, generally partial partitions are installed, in a perpendicular direction to that of the flow, which switch the direction and make the velocity profile more uniform. <
WO 2011/011421 A2 ,US 2006/080998 A1 , andUS 2011/120181 A1 all disclose tube bundle evaporators.> -
US 2010/276130 A1 discloses a horizontal tube bundle evaporator according to the preamble ofclaim 1. - These configurations are notoriously poorly efficient, as the control and intervention conditions during routine operation of the system are especially delicate.
- There therefore exists a need to simplify the structure of tube bundle evaporators for known-type vapour-compression refrigerating circuits.
- The technical task of the present invention is, therefore, to provide a tube bundle evaporator which obviates the above-described technical drawbacks of the prior art.
- Within the context of this technical task, an object of the invention is to realise a tube bundle evaporator of a hybrid type, which unites the characteristics of the low-load flooded type and of the falling film type, thus obviating the drawbacks of both.
- A further aim of the invention is to realise a tube bundle evaporator of a hybrid type which optimises the fluid-dynamics of the service fluid and the heat exchange with the process flow.
- A further aim of the invention is to realise a tube bundle evaporator of a hybrid type from which the service fluid in outlet can be returned to the refrigeration circuit prevalently in the gaseous phase.
- A further aim of the invention is to realise a tube bundle evaporator of a hybrid type which improves the distribution system of the service fluid on the tube bundle.
- A further aim of the invention is to realise a tube bundle evaporator of a hybrid type which optimises the positions of the fittings towards the external devices.
- The objects of the present invention are solved by the features of the
independent claim 1. Preferred embodiments are given in the dependent claims. Further characteristics and advantages of the invention will more fully emerge from the description of a preferred but not exclusive embodiment of the tube bundle evaporator according to the invention, illustrated by way of nonlimiting example in the appended drawings, wherein: -
figure 1 shows an external view of the evaporator; -
figure 2 shows a perspective exploded view of the evaporator; -
figure 3 shows a cross-section of the evaporator perpendicular to the longitudinal axis; -
figure 4 shows a perspective upper view of the refrigerant fluid distributor; -
figure 5 shows a partial lower view of a detail of the refrigerant fluid distributor; -
figure 6 shows a partial perspective view of the assembly of internal components of the evaporator; -
figure 7 shows a partial perspective view of internal components of the evaporator; -
figure 8 shows a sectioned partial perspective view of the head with the inlet and outlet of the process fluid. - With reference to the figures mentioned, a horizontal axis hybrid tube bundle evaporator is denoted in its entirety by
reference number 1, essentially constituted by acylindrical shell 2, by twoclosing heads shell 2 where the tubes individually perform an outward and return pathway parallel to the longitudinal horizontal axis and over the whole length of theshell 2, aninlet 5 in aclosing head 3A of the process fluid to be cooled and anoutlet 6 in aclosing head 3A of the cooled process fluid; theevaporator 1 further has twoinlets shell 2, symmetrically arranged in the direction of the longitudinal axis with respect to anoutlet 8 of the service refrigerant fluid in the gaseous state positioned in an upper lateral zone of theshell 2, and anoptical viewer 9 for controlling the level of the service refrigerant fluid on the lower lateral wall of theshell 2. - A first number of
tubes 41 of the tube bundle 4 is positioned in alower zone 21 of theevaporator 1 flooded by the service fluid, a second number oftubes 42 is positioned in anupper zone 22 of theevaporator 1 above the first number oftubes 41. - A
distributor 70 of the service refrigerant fluid is positioned in anupper zone 22 of theevaporator 1 above the second number oftubes 42 of the tube bundle 4, and is constituted by twoopposite collectors inlets evaporator 1, and mounted with a perpendicular axis to the longitudinal axis of theevaporator 1 and of the tube bundle 4. - A plurality of
straight distribution tubes 72i is perpendicularly connected to bothcollectors respective fittings 73i at the ends thereof, with a longitudinal axis parallel to the axis of theevaporator 1 and the tube bundle 4. - The
distribution tubes 72i inferiorly have a plurality oflongitudinal dispensing openings 74i made using laser cutting in the wall of the tube, through which the refrigerated fluid in the liquid state sprinkles the second number oftubes 42 by force of gravity. - The tube bundle 4 is supported inside the
shell 2 by a plurality oftransversal support plates 80i perpendicular to the longitudinal axis of the tubes and theevaporator 1, appropriately perforated for guided and continuous passage of the single tubes and appropriately configured for mounting inside theevaporator 1. - Perpendicularly to the plurality of the
transversal support plates 80i, and therefore parallel to the longitudinal axis of theevaporator 1, a further plurality of vertical longitudinalsecondary partitions 81i advantageously joint-fixed to thetransversal support plates 80i longitudinally divides, into a plurality of sectors, the second number oftubes 42 of the tube bundle 4 in thezone 22 of theevaporator 1. - The
transversal support plates 80i further divide the longitudinal sectors into sub-units. - The
transversal support plates 80i and thelongitudinal partitions 81i have appropriate pluralities of savings and through openings, respectively 82i and 83i which have the function of equalising the pressure of the refrigerant fluid between these sectors and sub-units inside theevaporator 1. - A plurality of longitudinal deflecting fins 85ni is further fixed on the
longitudinal partitions 81i, again with the aim of equalising the flow distribution of the refrigerant fluid by force of gravity on the tubes of the second number oftubes 42. - Laterally of the tube bundle of the second number of
tubes 42 is located a special primaryvertical partition 88 , longitudinally extended, conjoined at the top thereof to the internal lateral surface of theshell 2 and inferiorly extending downwards up to a suitable distance from the free surface of the floodedlower zone 21 for collecting the refrigerant fluid in the liquid state. - The primary
vertical partition 88 divides theupper zone 22 of the evaporator in which it defines a firstupper chamber 23 in which the second number oftubes 42 and thedistributor 70 of the service refrigerant fluid are housed, and a second upperlateral chamber 24 of theevaporator 1, towards the side of theshell 2 where theinlets distributor 70 and theoutlet 8 of the refrigerant fluid in the gaseous state are connected. - A third number of
tubes 43 connected via acollector 51 in thehead 3A is housed inside the second upperlateral chamber 24 of theevaporator 1. - The
head 3 A has theinlet collector 51 connected to theinlet 5 of the process fluid in theevaporator 1, and anoutlet collector 61 connected to theoutlet 6 of the cooled process fluid; theinlet collector 51 supplies the first number oftubes 41, the third number oftubes 43 and the lower group of tubes of said second number oftubes 42; and anoutlet collector 61 is supplied by an upper group of tubes of said second number oftubes 42. - Above the
lower zone 21 of theevaporator 1 flooded by service fluid, but in proximity thereof vertically at the second upperlateral chamber 24, there is an upper horizontal row oftubes 44 of said first number oftubes 41, positioned at a higher level than the upper horizontal row of the tubes facing and vertically at said firstupper chamber 23. - The operation of the
evaporator 1 according to the invention appears clear from the description and illustration and, in particular, is substantially as follows. - The process fluid to be cooled is introduced into the
evaporator 1 through theinlet 5 in thehead 3A, and thus in theinlet collector 51 from which it is distributed into the first number oftubes 41, the third number oftubes 43 and the lower group of tubes of the second number oftubes 42. - The process fluid to be cooled, coming from the system circulation and appropriately moved by movement means outside the evaporator, travels through the tubes in a horizontal-axis outward and return pathway inside the
evaporator 1 over the whole length of theshell 2. - The upper group of tubes of the second number of
tubes 42 thus returns to theoutlet collector 61 in thehead 3A, from which the appropriately-cooled process fluid is collected and connected to theoutlet 6 from theevaporator 1 and reinjected into the cooling system circulation of which the evaporator is a part. - The service refrigerant fluid in the liquid state, coming from other lines of the cooling system and appropriately moved by movement means outside the evaporator, is injected into the
evaporator 1 symmetrically, given equal conditions of temperature and pressure, through the twoinlets shell 2 the inside of which corresponds to the second upperlateral chamber 24 of theevaporator 1. - The two
opposite collectors inlets fluid distributor 70 of the service refrigerant fluid, via which collectors and via the successive plurality offittings 73i derived therefrom, the refrigerant fluid reaches the plurality ofdistribution tubes 72i from opposite ends. The supply of the refrigerant fluid from thecollectors distribution tubes 72i advantageously guarantees the homogeneity of the temperature and pressure conditions of the refrigerant fluid in each tube and inside each of the tubes of the plurality ofdistribution tubes 72i. - The refrigerant fluid locates, in the plurality of
distribution tubes 72i, the plurality of lowerlongitudinal dispensing openings 74i, through which the refrigerated fluid in the liquid state sprinkles the second number oftubes 42 by force of gravity. - The heat exchange by convection, between the refrigerant flow and the outer walls of the second number of
tubes 42 inside which the process fluid flows at a higher temperature, causes, among other things, the raising of the temperature of the refrigerant fluid, and a partial passage thereof from the liquid phase to the mixed-gaseous phase ("mist") and to the gaseous phase. - The refrigerant fluid, in its fall by force of gravity from the plurality of lower
longitudinal dispensing openings 74i in the plurality ofdistribution tubes 72i on the second number oftubes 42, is compartmentalised into a plurality of sub-units of a plurality of sectors defined by the plurality oftransversal support plates 80i and of verticallongitudinal partitions 81i. - The plurality of longitudinal deflecting fins 85i fixed on the
longitudinal partitions 81i advantageously facilitates the detachment of the refrigerant fluid that might have accumulated on thelongitudinal partitions 81i during the liquid phase and a better and progressive redistribution on the rows of the second number oftubes 42 positioned inferiorly of thelongitudinal deflecting fins 85i. - The pluralities of savings and through openings, respectively 82i and 83i in the
transversal support plates 80i and in thelongitudinal partitions 81i which are compartmentalised into a plurality of sub-units of a plurality of sectors inside theevaporator 1, advantageously facilitate the uniformity of the distribution of the refrigerant fluid during the progressively gaseous and mixed-gaseous phase in the progressive fall thereof on the rows of the second number oftubes 42. - The portion of refrigerant fluid still in the liquid phase, after having sprayed the second number of
tubes 42 by force of gravity, precipitates and is collected (floods) in thelower zone 21 of theevaporator 1, where the first number oftubes 41 of the tube bundle 4 is positioned and where the heat exchange is actuated in a static form by conduction between the refrigerant fluid in the liquid phase and the outer walls of the first number oftubes 41 of the tube bundle 4 which remains completely immersed (flooded) in the fluid. - Using the
optical viewer 9 positioned on the lateral lower wall of theshell 2, the level of the service refrigerant fluid in the floodedlower zone 21 is controlled, which level must be maintained, by an appropriate control and balancing of the functions of the system outside theevaporator 1, at a higher level than the upper horizontal row of the first number oftubes 41 of the tube bundle 4. - The portion of refrigerant fluid in the gaseous and mixed-gaseous phase, created for the heat exchange realised with interaction of the refrigerant fluid and the second number of
tubes 42 in the firstupper chamber 23 of theevaporator 1, physically and naturally tending to vertically rise towards the top of the firstupper chamber 23, is advantageously aspirated by means of an appropriate depression created by aspirating means outside theevaporator 1 at theoutlet 8 from theshell 2, positioned at the upperlateral chamber 24 of theevaporator 1. - The presence of the longitudinally-extended primary
vertical partition 88 that defines the firstupper chamber 23 and the second upperlateral chamber 24 of theevaporator 1, advantageously attributes to the portion of refrigerant fluid in the gaseous phase and mixed-gaseous phase a tortuous pathway from the firstupper chamber 23 to the second upperlateral chamber 24 comprising at least a portion of a descending circuit. - The
primary partition 88, in cooperation with the free surface of the collecting floodedlower zone 21, inferiorly delimits a connecting passage between the firstupper chamber 23 where a descending portion of circuit extends, and the second upperlateral chamber 24 where a rising portion of circuit extends in succession to a descending portion of circuit of the tortuous pathway of the refrigerant fluid in the gaseous and mixed-gaseous phase. - In proximity of the connecting passage of the tortuous pathway, and superiorly of the flooded
lower zone 21 of collection of a service fluid, but in proximity thereof and vertically at the second upperlateral chamber 24, there is the upper horizontal row oftubes 44 of the first number oftubes 41, positioned at a higher level than the upper horizontal row of the tubes facing and vertically at said firstupper chamber 23. - The tortuous pathway of the refrigerant fluid in gaseous and mixed-gaseous phase advantageously strikes, in the inversion from the descending portion of circuit to the rising portion of circuit, the upper
horizontal row 44 of tubes of the first number oftubes 41 and thus actuates a heat exchange which tends to reduce the number oftubes 41 and thus actuates a heat exchange which tends to reduce the moisture of the mixed-gaseous phase which is still residual. - The third number of
tubes 43 is also housed in the second upperlateral chamber 24 and is arranged at a greater height than the horizontal row oftubes 44, which is further struck by the refrigerant fluid in the gaseous and mixed-gaseous phase in a rising portion of circuit of the tortuous pathway, actuating a further heat exchange which tends to eliminate the moisture still residual in the mixed-gaseous phase (mist). - The refrigerated service fluid is advantageously thus distanced by the
evaporator 1 from theoutlet 8 and injected into the circuit of the refrigeration system in prevalently gaseous phase. - Modifications and variants to the hybrid tube bundle evaporator described in the foregoing are, naturally, possible. The invention however is defined by the appended claims.
- It has been observed that a horizontal tube bundle evaporator according to the invention is particularly advantageous for optimisation of the fluid-dynamics of the service fluid and the heat exchange with the process flow.
- In practice, the materials used, as well as the dimensions, can be any according to the needs and the state of the art.
Claims (12)
- A horizontal tube bundle evaporator (1) longitudinally extending along a horizontal axis, comprising a shell (2), a tube bundle (4) housed inside said shell (2), a shell-side refrigerant fluid, a tube-side refrigerated fluid, a lower zone (21) of said evaporator (1) flooded by the refrigerant fluid in the liquid state and containing a first number of tubes (41) of said tube bundle (4), a process fluid distributor (70) positioned in an upper zone (22) of said evaporator (1), a second number of tubes (42) of said tube bundle (4) positioned outside said flooded lower zone (21), and at least one outlet (8) of refrigerant fluid in the gaseous state from the shell (2), further comprising inside the shell (2), a tortuous circuit for the refrigerant fluid which vaporises on contact with said second number (42) of tubes comprising at least one descending portion of said circuit, wherein the descending portion of circuit is delimited by at least one separating primary vertical partition (88), longitudinally extended along said horizontal axis, said primary vertical partition (88) separating a first upper chamber (23) of said evaporator where the second number of tubes (42) is positioned from a second upper lateral chamber (24) of said evaporator (1) where said outlet (8) from the shell is positioned, characterized in that it comprises a plurality of secondary vertical longitudinal partitions (81i) which divide said first upper chamber (23) into a plurality of sectors where said tubes of said second number (42) of tubes are distributed, and wherein said secondary vertical partitions (81i) are provided with a plurality of longitudinal deflecting fins (85i) of the refrigerant fluid.
- The horizontal tube bundle evaporator (1) according to the preceding claim, wherein said second number of tubes (42) is greater than said first number of tubes (41).
- The horizontal tube bundle evaporator (1) according to any one of preceding claims , wherein said separating primary vertical partition (88) superiorly separates said first upper chamber (23) and said second upper lateral chamber (24) and extends downwards up to a distance from the free surface of said flooded lower zone (21) for collecting the refrigerant fluid in the liquid state.
- The horizontal tube bundle evaporator (1) according to the preceding claim, wherein said separating primary vertical partition (88), in cooperation with the free surface of said lower zone (21), inferiorly delimits a connecting passage between said first upper chamber (23) where said descending portion of circuit extends and said second upper lateral chamber (24) where a rising portion of circuit extends in succession to said descending portion of circuit.
- The horizontal tube bundle evaporator (1) according to the preceding claim, wherein said second upper lateral chamber (24) contains a third number of tubes (43) of said tube bundle (4) arranged outside said lower zone (21).
- The horizontal tube bundle evaporator (1) according to the preceding claim, wherein said outlet (8) is positioned in said second upper lateral chamber (24) above said third number of tubes (43).
- The horizontal tube bundle evaporator (1) according to any one of preceding claims, wherein said secondary vertical partitions (81i) are provided with a plurality of through-openings (83i) for equalisation of the pressure of the refrigerant fluid among said sectors.
- The horizontal tube bundle evaporator (1) according to any one of preceding claims, wherein a plurality of transversal support plates (80i) of said tube bundle (4) is positioned inside said shell (2), to which plurality of transversal support plates (80i) said secondary vertical partitions (81i) are fixed.
- The horizontal tube bundle evaporator (1) according to the preceding claim, wherein said transversal support plates (80i) divide said sectors into sub-units and are provided with through-openings (82i) for the equalisation of the pressure of the refrigerant fluid among said sub-units.
- The horizontal tube bundle evaporator (1) according to any one of preceding claims, wherein above said flooded lower zone (21) for collecting a service fluid, and vertically at the position of said second upper lateral chamber (24), there is an upper horizontal row of tubes (44) of said first number of tubes (41), positioned at a higher level than the upper horizontal row of the tubes facing and vertically at said first upper chamber (23).
- The horizontal tube bundle evaporator (1) according to any one of claims 5 to 10, wherein said shell (2) has a head 3A provided with an inlet collector (51) which supplies said first number of tubes (41), said third number of tubes (43) and a lower group of tubes of said second number of tubes (42), and an outlet collector (61) supplied by an upper group of tubes of said second number of tubes (42).
- A vapour compression refrigeration circuit comprising horizontal tube bundle evaporator according to any of the preceding claims.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT201900008127 | 2019-06-05 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3748270A1 EP3748270A1 (en) | 2020-12-09 |
EP3748270B1 true EP3748270B1 (en) | 2022-08-17 |
Family
ID=68073040
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20175886.9A Active EP3748270B1 (en) | 2019-06-05 | 2020-05-21 | Hybrid tube bundle evaporator |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP3748270B1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
IT202100029945A1 (en) | 2021-11-26 | 2023-05-26 | Mitsubishi Electric Hydronics & It Cooling Systems S P A | IMPROVED HYBRID EVAPORATOR ASSEMBLY |
IT202100030026A1 (en) | 2021-11-26 | 2023-05-26 | Mitsubishi Electric Hydronics & It Cooling Systems S P A | IMPROVED HYBRID EVAPORATOR ASSEMBLY |
CN115756031B (en) * | 2022-10-12 | 2023-10-10 | 东方电气集团东方汽轮机有限公司 | Method and system for controlling coiled tube evaporator |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008516187A (en) * | 2004-10-13 | 2008-05-15 | ヨーク・インターナショナル・コーポレーション | Falling film evaporator |
WO2008080085A2 (en) * | 2006-12-21 | 2008-07-03 | Johnson Controls Technology Company | Falling film evaporator with a hood and a flow distributor |
CN101907375A (en) * | 2008-01-11 | 2010-12-08 | 江森自控科技公司 | Heat exchanger |
EP2457051A2 (en) * | 2009-07-22 | 2012-05-30 | Johnson Controls Technology Company | Compact evaporator for chillers |
-
2020
- 2020-05-21 EP EP20175886.9A patent/EP3748270B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
EP3748270A1 (en) | 2020-12-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3748270B1 (en) | Hybrid tube bundle evaporator | |
US10746441B2 (en) | Heat exchanger | |
EP2841868B1 (en) | Heat exchanger | |
EP3748272B1 (en) | A hybrid tube bundle evaporator | |
EP3165850B1 (en) | Falling film evaporator | |
US10132537B1 (en) | Heat exchanger | |
JP6002316B2 (en) | Heat exchanger | |
EP3036492B1 (en) | Heat exchanger | |
EP3019809B1 (en) | Heat exchanger | |
US20150013951A1 (en) | Heat exchanger | |
EP3899399B1 (en) | Heat exchanger | |
EP3899398B1 (en) | Heat exchanger | |
EP3748271B1 (en) | A hybrid tube bundle evaporator with an improved service refrigerant fluid distributor | |
US11898780B2 (en) | Evaporator | |
CN112283983B (en) | Falling film evaporator and air conditioning system | |
KR20190006781A (en) | Evaporative condenser | |
EP4012297B1 (en) | Liquid refrigerant sprayer and falling liquid film type evaporator | |
EP3899397B1 (en) | Heat exchanger | |
JP2014020754A (en) | Downward flow liquid film type evaporator | |
CN111854233A (en) | Falling film evaporator and refrigeration system adopting same | |
KR20170096055A (en) | A transfer device for controlling the flow of liquid when transferring two-phase flows in block-in-shell heat exchangers |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20210428 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20220329 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602020004536 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1512441 Country of ref document: AT Kind code of ref document: T Effective date: 20220915 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20220817 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG9D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221219 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221117 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 1512441 Country of ref document: AT Kind code of ref document: T Effective date: 20220817 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221217 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20221118 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602020004536 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230524 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 |
|
26N | No opposition filed |
Effective date: 20230519 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20230523 Year of fee payment: 4 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20230531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230521 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230531 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230531 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230521 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230521 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20220817 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20230531 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20240506 Year of fee payment: 5 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240529 Year of fee payment: 5 |