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EP3034965B1 - Condenseur bloc et plaque, procédé d'extraction d'huile à partir d'un fluide frigorigène et utilisation d'un tel condenseur - Google Patents

Condenseur bloc et plaque, procédé d'extraction d'huile à partir d'un fluide frigorigène et utilisation d'un tel condenseur Download PDF

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Publication number
EP3034965B1
EP3034965B1 EP14199301.4A EP14199301A EP3034965B1 EP 3034965 B1 EP3034965 B1 EP 3034965B1 EP 14199301 A EP14199301 A EP 14199301A EP 3034965 B1 EP3034965 B1 EP 3034965B1
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EP
European Patent Office
Prior art keywords
shell
flow distribution
oil
distribution chamber
refrigerant
Prior art date
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Application number
EP14199301.4A
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German (de)
English (en)
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EP3034965A1 (fr
Inventor
Christian Per Bunde-Pedersen
Simon Stubkier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Johnson Controls Denmark ApS
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Johnson Controls Denmark ApS
Priority date (The priority date 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 date listed.)
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Publication date
Application filed by Johnson Controls Denmark ApS filed Critical Johnson Controls Denmark ApS
Priority to DK14199301.4T priority Critical patent/DK3034965T3/da
Priority to EP14199301.4A priority patent/EP3034965B1/fr
Priority to PCT/DK2015/050368 priority patent/WO2016095919A1/fr
Publication of EP3034965A1 publication Critical patent/EP3034965A1/fr
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Publication of EP3034965B1 publication Critical patent/EP3034965B1/fr
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Classifications

    • 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
    • F25B39/04—Condensers
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/043—Condensers made by assembling plate-like or laminated elements
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant

Definitions

  • the present invention relates to a shell-and-plate condenser comprising a stack of corrugated heat transfer plates arranged inside a tubular outer shell.
  • the invention further relates to a method for removing oil from a refrigerant by means of an oil separator unit arranged inside a tubular outer shell of a shell-and-plate condenser.
  • the invention also relates to use of a shell-and-plate condenser.
  • Shell-and-plate (or plate-and-shell) condensers consist of a series of corrugated plates peripherally welded or bonded to each other in pairs (so-called cassettes) which in turn are welded to each other along the entrance holes and exit holes to form a complete plate stack (or plate pack).
  • the plate pack is inserted within a tubular shell, typically formed from steel.
  • Shell-and-plate condensers are often used in refrigeration cycles typically also comprising an evaporator and a compressor. In large refrigeration cycles the compressor is oil lubricated, and over time some of this oil will be diluted and mixed with the refrigerant circulating in the refrigeration cycle. If this oil is not removed it will form a layer or a coating on the plates in the condenser and/or the evaporator which will severely reduce the efficiency.
  • the invention relates to a shell-and-plate condenser comprising a stack of corrugated heat transfer plates arranged inside a tubular outer shell, wherein the outer shell comprises at least one entrance hole for leading oil-containing refrigerant into the condenser and the condenser further comprises an integrated oil separator unit arranged above the plate stack.
  • the oil separator unit includes at least one flow distribution chamber being connected to at least one of the entrance holes, wherein the flow distribution chamber substantially extends in a longitudinal direction of the tubular outer shell and wherein the flow distribution chamber comprises at least one sidewall comprising a plurality of exit holes through which the oil-containing refrigerant leaves the flow distribution chamber in a direction substantially transversal to the longitudinal direction of the outer shell and flows out into a flow guide channel of the oil separator unit.
  • the oil separator unit further includes at least one outflow demister element arranged in a demister part of the flow guide channel.
  • Forming the oil separator as a separate unit is advantageous in that the risk of oil-containing refrigerant getting in contact with the plate pack is hereby reduced. And placing the unit inside the condenser is advantageous in that the oil separator unit hereby does not have to be formed as a pressure vessel since the pressure inside and outside the unit is substantially the same.
  • Arranging the oil separating unit above the plate stack is advantageous in that in the condenser the refrigerant - that has changed from gaseous to liquid phase - will naturally seek downwards due to gravitational pull. It is therefore advantageous to lead the refrigerant downwards through the plate stack.
  • the oil separator unit is arranged above the plate stack, because it provides a less space consuming design and because it reduces the risk of refrigerant condensation before the refrigerant reaches the plate stack.
  • orientation - such as above, below, under, downwards, horizontal etc. - refers to the condenser's orientation during normal use i.e. where the refrigerant is lead down through the plate stack so that the condensed liquid refrigerant can be drained from the bottom of the condenser.
  • the condenser might function even if it is not orientated as intended but the skilled person would recognise that the condenser is most efficient if it is orientated as intended and the skilled person would therefore not question which orientation of the condenser would be the correct one to use during normal use of the condenser.
  • the term "demister element” is to be understood as any kind of device designed to enhance the removal of liquid droplets entrained in a vapour stream.
  • the demister element may be any kind of mesh type coalescer, knitted mesh, nonwoven filament structure, vane pack or other structure intended to aggregate the mist into droplets that are heavy enough to separate from the vapour stream.
  • the demister part of the flow guide channel is arranged in an angle of between 5° and 85°, preferably between 15° and 75° and most preferred between 30° and 60° upwards in relation to a horizontal plane.
  • the demister part of the flow guide channel is too steep the risk of separated oil being suspended by the upward gas flow is increased and such suspended oil will decrease the efficiency of the demister element or at least increase the drop of pressure across the demister element.
  • the demister part of the flow guide channel is too flat the risk of separated oil being dragged out of the demister element by the gas flow is increased thus reducing the efficiency of the demister element.
  • the present angle ranges are particularly advantageous regarding efficiency of the demister element.
  • the exit holes constitutes between 1% and 90%, preferably between 2% and 50%, and most preferred between 3% and 25% of the total area of the flow distribution chamber.
  • exit holes constitute too much of the total area of the flow distribution chamber most of the entering oil-containing refrigerant will leave the flow distribution chamber at the far end opposite from the entrance hole and the incoming flow will hereby not be efficiently distributed in the oil separator unit. And if the exit holes constitute too little of the total area of the flow distribution chamber, the pressure drop across the flow distribution chamber becomes too high and the energy required for circulating the refrigerant is increased. Thus, the present exit hole area ratios presents an advantageous relationship between gas flow distribution efficiency and power consumption.
  • the flow distribution chamber comprises an inflow demister element arranged inside the flow distribution chamber.
  • Arranging an inflow demister element inside the flow distribution chamber is advantageous in that even though the flow speed is so high through the flow distribution chamber that substantially no oil will be separated in the inflow demister element, the inflow demister element will still increase the size of the oil particles or aerosols of the oil-containing refrigerant, thus making the subsequent oil separation more efficient.
  • the shell-and-plate condenser comprises an inflow demister element arranged at the at least one entrance hole.
  • Arranging the inflow demister element at the entrance hole is advantageous in that hereby the oil droplet distribution of the entire oil-containing refrigerant is altered before the gas flow leaves the flow distribution chamber.
  • the flow distribution chamber's length in the longitudinal direction is substantially the same as the plate stack's length in the longitudinal direction.
  • Forming the flow distribution chamber substantially as long as the plate stack is advantageous in that in that the inflow hereby can be distributed over a large area - thus enabling better oil separation.
  • the outflow demister element's length in the longitudinal direction is substantially the same as the plate stack's length in the longitudinal direction.
  • Forming the outflow demister element substantially as long as the plate stack is advantageous in that it hereby is possible to form the outflow demister element with a large area - thus enabling better oil separation.
  • the flow distribution chamber is formed as a circular tube.
  • Forming the flow distribution chamber as a circular tube is advantageous in that the circular shape is space-efficient and it enables a more efficient and even flow distribution.
  • the flow guide channel is arranged to guide the oil-containing refrigerant downwards towards an impact surface before the oil-containing refrigerant is lead through the outflow demister element.
  • Guiding the oil-containing refrigerant downwards before it enters the demister element is advantageous in that it provides for a more space-efficient and compact design of the oil separator unit. And arranging an impact surface where the oil-containing refrigerant changes direction and continues through the outflow demister element is advantageous in that larger drops and particles will be flung out of the gas flow and collected on the impact surface before the gas flow enters the outflow demister element - thus, increasing the overall efficiency of the oil separator and reducing the risk of clogging the demister element.
  • a perforated flow distribution device is arranged across the flow guide channel between the flow distribution chamber and the outflow demister part of the flow guide channel.
  • Arranging a perforated flow distribution device across the entire flow guide channel is advantageous in that it enables better distribution of the flow before it hits the outflow demister element.
  • the degree of perforation of the flow distribution plate is increased upwards in the flow distribution plate.
  • the separated oil will travel downwards due to gravitational pull and if the flow speed through the bottom of the outflow demister element is too high the risk of separated oil being drawn out of the outflow demister element is increased.
  • Increasing the open area of the flow distribution plate upwards is therefore advantageous in that it will decrease the flow at the bottom of the outflow demister element.
  • the entrance hole is arranged at an entrance hole end of the flow distribution chamber and wherein the inner volume of the flow distribution chamber is larger at the entrance hole end than at the opposite end of the flow distribution chamber.
  • the oil separator unit comprises at least two outflow demister elements arranged on either sides of the flow distribution chamber.
  • Arranging an outflow demister element on either sides of the flow distribution chamber is advantageous in that it is a simple way forming a small and compact oil separator unit while increasing the size of the outflow demister element.
  • a centre of the flow distribution chamber is arranged above a centre of the outflow demister element.
  • the oil-containing refrigerant at least to some degree flows upwards while passing the outflow demister element.
  • the centre of the flow distribution chamber is arranged above the centre of the outflow demister element to enable that the flow is directed downwards before reaching the outflow demister element.
  • the tubular outer shell comprises endplates and wherein the at least one entrance hole is arranged in at least one of the endplates.
  • the tubular outer shell is formed as a circular tube provided with endplates.
  • the round shape of the outer shell ensures an even distribution of mechanical loads, without the stress concentrations that occur in the corners of polygonal constructions.
  • the endplates are welded to the outer shell.
  • Welding the endplates is an inexpensive way of ensuring that the pressure vessel is both strong and tight.
  • the tubular outer shell is a pressure vessel designed and/or approved to withstand a pressure between 0.7 and 15 MPa, preferably between 1.5 and 10 and most preferred between 2.5 and 7.5 MPa.
  • the present pressure ranges presents an advantageous relationship between safety and cost.
  • the invention further relates to a method for removing oil from a refrigerant by means of an oil separator unit arranged inside a tubular outer shell of a shell-and-plate condenser.
  • the method comprises the steps of:
  • Changing the general flow direction of the oil-containing refrigerant from being substantially parallel with a longitudinal direction of the tubular outer shell to being substantially transversal to the longitudinal direction of the tubular outer shell is advantageous in that it provides for a more even flow distribution and because it enables a larger oil separator design extending in the longitudinal direction of the shell.
  • the shell-and-plate condenser is a shell-and-plate condenser according to any of the previously mentioned shell-and-plate condensers.
  • the invention also relates to use of a shell-and-plate condenser according to any of the previously mentioned shell-and-plate condensers for removing oil from a refrigerant and for condensing the refrigerant in a refrigeration cycle also comprising an evaporator and a compressor.
  • a shell-and-plate condenser comprising an oil separator unit according to the present invention for condensing and removing oil from a refrigerant in a refrigeration cycle is advantageous in that it ensures a more efficient and less expensive refrigeration cycle.
  • Figure 1 shows an embodiment of a shell-and-plate condenser 1, as seen in perspective.
  • the shell-and-plate condenser 1 is used for condensing a refrigerant in a refrigeration cycle. I.e. after the condensed refrigerant leaves the shell-and-plate condenser 1 it is typically directed to an expansion valve, which will reduce the pressure making at least some of the refrigerant evaporate and thus making its temperature drop drastically. At this stage the cold refrigerant is then used for cooling purposes by which the entire refrigerant evaporates. The gaseous refrigerant is then directed through a compressor compressing the refrigerant, which in turn raises its temperature drastically.
  • the hot gaseous refrigerant is then lead to the condenser 1 where the gaseous refrigerant is condensed into a liquid refrigerant.
  • the gaseous refrigerant could also be lead through a de-superheater, where the refrigerants temperature is lowered to just above the condensation temperature before it enters the condenser 1.
  • the liquid refrigerant could be cooled further in a subcooler before the cycle is repeated.
  • the shell-and-plate condenser 1 comprises a single stack of heat transfer plates 5 and an oil separator unit 3 arranged inside a circular tubular outer shell 8.
  • the shell-and-plate condenser 1 could comprise two stacks of heat transfer plates 5 e.g. separated by a wall or plate arranged at the middle of the condenser 1 so that the two plate stacks 5 could be separately fed from either ends of the condenser 1.
  • the condenser 1 could also comprise more than two plate stacks 5 such as three, four, six or more.
  • the shell 8 is formed by rolling a single sheet and then welding it together along the longitudinal seam. Forming the shell 8 as a single monolithic cylindrical tube increases the strength of the shell 8 and reduces the risk of unwanted stress concentrations in the shell 8.
  • the shell 8 could also be formed by a number of shell parts welded together or bolted together either axially or radially to ensure that the shell 8 subsequently can be opened e.g. in case of maintenance and/or repair.
  • the shell-and-plate heat condenser 1 is a versatile design which combines the strength of a shell-and-tube heat exchanger with the thermal efficiency of a plate heat exchanger in that the shell-and-plate heat exchanger combines the pressure and temperature capabilities of a typically cylindrical shell with the excellent heat transfer performance of a plate heat exchanger.
  • the round or oblong shell and plates ensure an even distribution of mechanical loads, without the stress concentrations that occur in the corners of rectangular plates.
  • the shell-and-plate condenser combines the benefits of a traditional shell and tube type heat condenser but with the high efficiency provided for in a plate type condenser.
  • Fig. 2 shows a cross section through the middle of a shell-and-plate condenser 1, as seen from the front.
  • the oil separator unit 3 is arranged directly above the plate stack 5 in an upper part 18 of the tubular outer shell 8 and in this embodiment the entrance hole 2 of the oil separator unit 3 is arrange in an endplate 21.
  • the oil-containing refrigerant vapour enters the oil separator unit 3 at the top of the condenser 1 as illustrated by the arrows.
  • oil will be separated from the refrigerant vapour which then will continue downwards through the plate stack 5 which will condense the refrigerant vapour to liquid refrigerant.
  • the liquid refrigerant will then continue downwards towards the bottom of the shell 8 from which it will be drained from the condenser 1 through the refrigerant exit hole 24.
  • the heat transfer plates 5 are welded (or bonded) back to back along the outer periphery to form so-called cassettes.
  • a number of these cassettes are then welded together around respective inlet openings and outlet openings to form a heat transfer plate pack 5.
  • a coolant flow is then established inside the cassettes by leading coolant into the stack 5 through a plate stack outlet opening 19 and out again through a plate stack inlet opening 20 arranged in an endplate 21. Inside the cassettes the coolant will flow from inlet opening to outlet opening (in alternate directions) while the refrigerant flows across the outside of (i.e. between) the cassettes.
  • the plate stack outlet opening 19 and the plate stack inlet opening 20 of the plate stack 5 are arranged in the same endplate 21 - as also illustrated in figure 1 - and in this embodiment the oil separator unit 3 is substantially symmetrically arranged inside the shell 8 so that the entrance hole 2, the plate stack outlet opening 19 and the plate stack inlet opening 20 are all substantially vertically aligned.
  • the entrance hole 2 the plate stack outlet opening 19 and the plate stack inlet opening 20 would not be aligned and/or one or more of the entrance hole 2, the plate stack outlet opening 19 and the plate stack inlet opening 20 would also or instead be arranged in the other endplate 21 and/or in the shell 8.
  • the plates 5 are formed substantially semi-circular to fit into a circular shell 8 and to allow room above the plate stack 5 for the oil separator unit 3 but in another embodiment the plates 5 could be formed differently e.g. if the oil separator unit was formed differently or to fit into a shell 8 of a different shape.
  • the plates 5 are provided with an embossed pattern of channels (not shown) so that when a cassette is formed the coolant can flow through these channels from the inlet opening to the outlet opening.
  • the embossed pattern also increases the surface area of the plates 5 thus increasing its heat transferring ability.
  • the oil separator unit 3, the shell 8, and the endplates 21 are all made from steel and all the plates 5 are made from stainless steel because of this materials strength and durability but in another embodiment all, some or parts of the condenser parts could be made from another material such as titanium, aluminium, a composite material or other.
  • the coolant flowing through the cassettes of the plate stack 5 is water e.g. circulating through an external air cooled heat exchanger or transporting the absorbed heat to a particular place where it can be utilised.
  • the coolant could be brine or another form of natural or artificial coolant suitable for flowing through a condenser 1.
  • the refrigerant being condensed in the condenser 1 is ammonia but in another embodiment the refrigerant could be carbon dioxide, Butane, a HFC gas, water vapour or another fluid suitable for acting as a refrigerant in a shell-and-plate condenser 1.
  • Fig. 3 shows an oil separator unit 3, as seen in perspective and fig. 4 shows an oil separator unit 3, as seen from the front.
  • the oil separator unit 3 comprises a flow distribution chamber 4 substantially extending the entire length of the oil separator unit 3 and a flow guide channel 9 formed around the flow distribution chamber 4.
  • the flow guide channel 9 will guide the refrigerant from the flow distribution chamber 4 and downwards to an impact surface 13 arranged at the bottom of the oil separator unit 3 from which the refrigerant will be flow upwards through one of two outflow demister elements 10 arranged substantially symmetrical on either sides of the flow distribution chamber 4 and the impact surface 13.
  • the outflow demister elements 10 are arranged in a demister part 11 of the flow guide channel 9 and in this embodiment the demister part 11 is formed with a demister part angle DA of approximately 45° upwards so that the refrigerant is directed upwards while passing through the outflow demister elements 10.
  • the demister part 11 could be formed with another angle such as 20°, 35°, 55°, 70° or other.
  • the substantially oil-free refrigerant will leave the oil separator unit 3 at the upper end of the demister part 11 and travel down through the plate stack 5 as illustrated by means of the arrows on fig. 2 .
  • the oil separator unit 3 could comprise only a single demister part 11 and/or a single outflow demister element 10 and/or in another embodiment the outflow demister element 10 could be arranged in more or less direct succession of the flow distribution chamber 4 e.g. if the outflow demister element 10 where surrounding or at least partly surrounding the flow distribution chamber 4 or at least only separated by a short flow guide channel 9.
  • oil will be separated from the refrigerant and the liquid oil will be pulled downwards by gravity towards the oil collection tray 22 at the bottom of the oil separator unit 3.
  • the bottom of the oil collection tray 22 is sloping to one side so that the liquid oil may be drained from the oil separator unit 3 through an oil drainage hole 23 arranged in one of the endplates 21 as illustrated in fig. 1 and 2 .
  • the drained oil can be lead back to the compressor for reuse.
  • a perforated flow distribution device 14 is arranged all the way across the flow guide channel 9 just before each of the two outflow demister elements 10.
  • the perforated flow distribution device 14 will distribute the refrigerant flow better before it enters the outflow demister elements 10.
  • the increased degree of perforation upwards of the perforated flow distribution device 14 is shown more clearly on fig. 5 .
  • centre 16 of the flow distribution chamber 4 is arranged above the centre 17 of the outflow demister elements 10 but in another embodiment the centre 16 of the flow distribution chamber 4 could be substantially horizontally aligned with the centre 17 of the outflow demister elements 10 or the centre 16 of the flow distribution chamber 4 could even be arranged below the centre 17 of the outflow demister elements 10.
  • Fig. 5 shows a cross section through an oil separator unit 3, as seen from the side.
  • the oil separator unit 3 is provided with an inflow demister element 12 arranged at the entrance hole end 15 inside the flow distribution chamber 4.
  • the inflow demister element 12 could be arranged to extend throughout substantially the entire length of the flow distribution chamber 4.
  • the perforated flow distribution device 14 is formed as a plate arranged at the bottom of the outflow demister element 10 and perforated by elongated holes.
  • the size of the holes increases upwards so that the degree of perforation of the perforated flow distribution device 14 is increased upwards to distribute the flow through the outflow demister element 10 better.
  • the condenser 1 is only provided with a single entrance hole 2 arranged in a single endplate 21 at the entrance hole end 15 of the flow distribution chamber 4.
  • entrance holes 2 could be provided in both endplates 21 enabling refrigerant inflow at both ends of the flow distribution chamber 4 and/or the shell 8 could be provided with a centrally arranged, entrance hole 2 or a number of entrance holes 2 distributed along the longitudinal length of the shell 8.
  • the cross sectional area of the flow distribution chamber 4 is around 9,500 mm 2 and the area is substantially constant throughout the entire longitudinal length of the flow distribution chamber 4 - thus, in this embodiment the inner volume of the flow distribution chamber 4 is substantially constant throughout the length of the flow distribution chamber 4.
  • the inner volume at the entrance hole end 15 could be larger than at the opposite end of the flow distribution chamber 4 e.g. to compensate for drop in pressure.
  • the inner volume of the flow distribution chamber 4 could be reduced by forming the flow distribution chamber 4 conically or by providing a solid body inside the flow distribution chamber 4 opposite the entrance hole end 15.
  • the pressure drop could be compensated by adjusting the size of the exit holes along the length of the flow distribution chamber 4.
  • cross sectional area of the flow distribution chamber 4 could be smaller or bigger e.g. depending on the specific use, the specific capacity, the specific refrigerant or other.
  • Fig. 6 shows a flow distribution chamber 4, as seen in perspective
  • the flow distribution chamber 4 is formed as a hollow circular tube comprising a number of elongated exit holes 7 arranged in the sidewall 6 substantially in the entire length of the flow distribution chamber 4.
  • the flow distribution chamber 4 could be formed differently such as square, triangular, oval, polygonal or with some other more or less complex shape.
  • the exit holes 7 could only be arranged in only one or some of the sidewalls 6 i.e. in two or three sidewalls 6.
  • the exit holes 7 constitute around 8 % of the total area of the effective area or the sidewall 6 of the flow distribution chamber 4 to ensure an efficient flow distribution along the length of the flow distribution chamber 4.
  • the exit holes 7 would have to constitute a corresponding larger percentage of the total area and vice versa if the cross sectional area was larger.
  • the perforation in the perforated flow distribution device 14 and/or the exit holes 7 in the sidewall 6 of the flow distribution chamber 4 could instead or also be formed differently such as circular, oval, polygonal or other or the perforated flow distribution device 14 and/or the flow distribution chamber 4 could be formed by or comprise some sort of mesh, nonwoven filament structure, latticework or other providing the same technical effect as the perforations and the exit holes 7.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (15)

  1. Condenseur à calandre et à plaques (1) comprenant une pile de plaques de transfert de chaleur ondulées (5) disposées à l'intérieur d'une calandre extérieure tubulaire (8), ladite calandre extérieure (8) comprenant au moins un trou d'entrée (2) pour conduire un réfrigérant contenant de l'huile dans ledit condenseur (1), ledit condenseur (1) comprenant en outre une unité de séparation d'huile (3) intégrée disposée au-dessus de ladite pile de plaques (5), caractérisé en ce que ladite unité de séparation d'huile (3) comprend au moins une chambre de distribution d'écoulement (4) reliée à au moins un desdits trous d'entrée (2), ladite chambre de distribution d'écoulement (4) s'étendant sensiblement dans une direction longitudinale de ladite calandre extérieure tubulaire (8) et ladite chambre de distribution d'écoulement (4) comprenant au moins une paroi latérale (6) comprenant une pluralité de trous de sortie (7) à travers lesquels ledit réfrigérant contenant de l'huile quitte ladite chambre de distribution d'écoulement (4) dans une direction sensiblement transversale à ladite direction longitudinale de ladite calandre extérieure (8) et s'écoule dans un canal de guidage d'écoulement (9) de ladite unité de séparation d'huile (3), ladite unité de séparation d'huile (3) comprenant en outre au moins un élément de désembuage d'écoulement sortant (10) disposé dans une partie de désembuage (11) dudit canal de guidage d'écoulement (9).
  2. Condenseur à calandre et à plaques (1) selon la revendication 1, ladite partie de désembuage (11) dudit canal de guidage d'écoulement (9) étant disposée selon un angle (DA) compris entre 5° et 85°, de préférence entre 15° et 75° et de manière plus préférée entre 30° et 60° vers le haut par rapport à un plan horizontal.
  3. Condenseur à calandre et à plaques (1) selon la revendication 1 ou 2, lesdits trous de sortie (7) constituant entre 1 % et 90 %, de préférence entre 2 % et 50 %, et de manière plus préférée entre 3 % et 25 % de la surface totale de ladite chambre de distribution d'écoulement (4).
  4. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, ladite chambre de distribution d'écoulement (4) comprenant un élément de désembuage d'écoulement entrant (12) disposé à l'intérieur de ladite chambre de distribution d'écoulement (4).
  5. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, ledit condenseur à calandre et à plaques (1) comprenant un élément de désembuage d'écoulement entrant (12) disposé au niveau dudit au moins un trou d'entrée (2).
  6. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, la longueur de ladite chambre de distribution d'écoulement dans ladite direction longitudinale étant sensiblement la même que la longueur de ladite pile de plaques dans ladite direction longitudinale.
  7. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, la longueur dudit élément de désembuage d'écoulement sortant dans ladite direction longitudinale étant sensiblement la même que la longueur de ladite pile de plaques dans ladite direction longitudinale.
  8. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, le canal de guidage d'écoulement (9) étant conçu pour guider ledit réfrigérant contenant de l'huile vers le bas vers une surface d'impact (13) avant que ledit réfrigérant contenant de l'huile ne soit conduit à travers ledit élément de désembuage d'écoulement sortant (10).
  9. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, un dispositif de distribution d'écoulement (14) perforé étant disposé en travers dudit canal de guidage d'écoulement (9) entre ladite chambre de distribution d'écoulement (4) et ladite partie de désembuage d'écoulement sortant (11) dudit canal de guidage d'écoulement (9).
  10. Condenseur à calandre et à plaques (1) selon la revendication 10, le degré de perforation de ladite plaque de distribution d'écoulement (14) étant augmenté vers le haut dans ladite plaque de distribution d'écoulement (14).
  11. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, ledit trou d'entrée (2) étant situé au niveau d'une extrémité de trou d'entrée (15) de ladite chambre de distribution d'écoulement (4) et le volume intérieur de ladite chambre de distribution d'écoulement (4) étant plus grand au niveau de ladite extrémité de trou d'entrée (15) qu'au niveau de l'extrémité opposée de ladite chambre de distribution d'écoulement (4).
  12. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, ladite unité de séparation d'huile (3) comprenant au moins deux éléments de désembuage d'écoulement sortant (10) disposés de part et d'autre de ladite chambre de distribution d'écoulement (4).
  13. Condenseur à calandre et à plaques (1) selon une ou plusieurs des revendications précédentes, un centre (16) de ladite chambre de distribution d'écoulement (4) étant situé au-dessus d'un centre (17) dudit élément de désembuage d'écoulement sortant (10).
  14. Procédé pour extraire l'huile d'un réfrigérant au moyen d'une unité de séparation d'huile (3) disposée à l'intérieur d'une calandre extérieure tubulaire (8) d'un condenseur à calandre et à plaques (1), ledit condenseur à calandre et à plaques (1) étant un condenseur à calandre et à plaques selon l'une quelconque des revendications 1 à 13, ledit procédé comprenant les étapes consistant à :
    • conduire le réfrigérant contenant de l'huile dans une chambre de distribution d'écoulement (4) de ladite unité de séparation d'huile (3), ladite unité de séparation d'huile (3) étant disposée au niveau d'une partie supérieure (18) de ladite calandre extérieure tubulaire (8) et ladite chambre de distribution d'écoulement (4) changeant la direction d'écoulement générale dudit réfrigérant contenant de l'huile d'une direction sensiblement parallèle à une direction longitudinale de ladite calandre extérieure tubulaire (8) à une direction sensiblement transversale à ladite direction longitudinale de ladite calandre extérieure tubulaire (8),
    • conduire ledit réfrigérant contenant de l'huile à travers un élément de désembuage d'écoulement sortant (10) de ladite unité de séparation d'huile (3), ledit élément de désembuage d'écoulement sortant (10) étant disposé dans ledit chemin d'écoulement sensiblement transversal pour séparer l'huile dudit réfrigérant, et
    • conduire ledit réfrigérant sensiblement exempt d'huile vers le bas à travers une pile de plaques de transfert de chaleur ondulées (5) disposées sous ladite unité de séparation d'huile (3).
  15. Utilisation d'un condenseur à calandre et à plaques (1) selon l'une quelconque des revendications 1 à 13 pour extraire l'huile d'un réfrigérant et pour condenser ledit réfrigérant dans un cycle de réfrigération comprenant également un évaporateur (19) et un compresseur (20).
EP14199301.4A 2014-12-19 2014-12-19 Condenseur bloc et plaque, procédé d'extraction d'huile à partir d'un fluide frigorigène et utilisation d'un tel condenseur Active EP3034965B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DK14199301.4T DK3034965T3 (da) 2014-12-19 2014-12-19 Skal- og pladekondensator, fremgangsmåde til fjernelse af olie fra et kølemiddel og anvendelse af en skal- og pladekondensator
EP14199301.4A EP3034965B1 (fr) 2014-12-19 2014-12-19 Condenseur bloc et plaque, procédé d'extraction d'huile à partir d'un fluide frigorigène et utilisation d'un tel condenseur
PCT/DK2015/050368 WO2016095919A1 (fr) 2014-12-19 2015-12-01 Condenseur à enveloppe et à plaques, procédé d'élimination d'huile d'un fluide frigorigène et utilisation d'un condenseur à enveloppe et à plaques

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14199301.4A EP3034965B1 (fr) 2014-12-19 2014-12-19 Condenseur bloc et plaque, procédé d'extraction d'huile à partir d'un fluide frigorigène et utilisation d'un tel condenseur

Publications (2)

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EP3034965A1 EP3034965A1 (fr) 2016-06-22
EP3034965B1 true EP3034965B1 (fr) 2021-06-16

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EP (1) EP3034965B1 (fr)
DK (1) DK3034965T3 (fr)
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CN106150599A (zh) * 2016-08-29 2016-11-23 四川齐飞铝业有限公司 一种卧式油分离与冷却装置
CN106766398B (zh) * 2017-02-23 2018-09-18 大连冷冻机股份有限公司 适用于降膜蒸发器的迷宫式挡液结构
CN106802033A (zh) * 2017-03-14 2017-06-06 烟台冰轮股份有限公司 一种兼具油气分离及油冷却功能的冷凝器
CN106895612A (zh) * 2017-03-22 2017-06-27 刘焓 一种内置油分离器的冷凝器
CN107940838A (zh) * 2017-12-21 2018-04-20 珠海格力电器股份有限公司 油分离装置、冷凝器及制冷系统
CN107940836A (zh) * 2017-12-21 2018-04-20 珠海格力电器股份有限公司 冷凝器组装方法、油分组件、冷凝器和制冷装置
CN109323486B (zh) * 2018-11-07 2024-07-30 珠海格力电器股份有限公司 冷凝设备和空调系统
CN113280537B (zh) * 2021-06-28 2025-02-07 珠海格力电器股份有限公司 冷凝器和制冷设备
CN113623906B (zh) * 2021-07-26 2024-11-22 珠海格力电器股份有限公司 油分离装置、冷凝器及空调系统
CN115978846B (zh) * 2023-02-17 2024-11-22 珠海格力电器股份有限公司 内置油分、冷凝器和制冷装置
CN116182435A (zh) * 2023-02-17 2023-05-30 珠海格力电器股份有限公司 冷凝器的去过热组件、冷凝器和制冷系统
CN116336700A (zh) * 2023-03-30 2023-06-27 约克（无锡）空调冷冻设备有限公司 内设油分离结构的冷凝器

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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ITPD20130091A1 (it) * 2013-04-10 2014-10-11 Ocs Cold S R L Separatore olio con elemento integrato denominato elemento separatore olio retex inverter formato da un tubo con taglio o fori, lana metallica, rete metallica

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Publication number Priority date Publication date Assignee Title
US12460846B2 (en) 2022-01-19 2025-11-04 Carrier Corporation Multi-level oil vaporizer for refrigeration system

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WO2016095919A1 (fr) 2016-06-23
EP3034965A1 (fr) 2016-06-22

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