WO2012143751A2 - Condensateur/accumulateur et systèmes et procédés de commande - Google Patents

Condensateur/accumulateur et systèmes et procédés de commande Download PDF

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Publication number
WO2012143751A2
WO2012143751A2 PCT/IB2011/001465 IB2011001465W WO2012143751A2 WO 2012143751 A2 WO2012143751 A2 WO 2012143751A2 IB 2011001465 W IB2011001465 W IB 2011001465W WO 2012143751 A2 WO2012143751 A2 WO 2012143751A2
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
condenser
accumulator
condition
coolant
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.)
Ceased
Application number
PCT/IB2011/001465
Other languages
English (en)
Other versions
WO2012143751A3 (fr
Inventor
Michel Grabon
Gregory TERRAZ
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.)
Carrier Corp
Original Assignee
Carrier Corp
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.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Priority to EP11740718.9A priority Critical patent/EP2661593B1/fr
Priority to PCT/IB2011/001465 priority patent/WO2012143751A2/fr
Priority to US14/111,367 priority patent/US20140034275A1/en
Priority to CN201180070249.4A priority patent/CN103492821B/zh
Publication of WO2012143751A2 publication Critical patent/WO2012143751A2/fr
Publication of WO2012143751A3 publication Critical patent/WO2012143751A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
    • 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
    • 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
    • F28D7/163—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 conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—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 conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • 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
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter

Definitions

  • the disclosure relates to refrigeration. More particularly, the disclosure relates to accumulators for CO 2 refrigeration systems.
  • Refrigeration circuits which operate with significant capacity variation and which have large circuit volumes (e.g., due to long piping connections between main components) are subjected to relatively large variation of active refrigerant charge.
  • An accumulator may be used to remove and return refrigerant from the active charge in the remainder of the circuit.
  • FIG. 1 shows a prior art cooling unit 20 which receives chilled liquid (coolant, e.g., water or brine) from a chiller 22.
  • the chiller feeds a water supply circuit having a supply/feed/output l i ne 24 and a return line 26.
  • the unit 20 includes a refrigerant loop/flowpath/circuit 30 along which a refrigerant-air heat exchanger 32 is located.
  • the refrigerant-air heat exchanger 32 may be part of an air handling unit (AHU; fan 33 and airflow shown) and the refrigerant may consist essentially of carbon dioxide (CO 2 ).
  • the refrigerant circuit 30 also includes one or more heat exchangers such as a condenser 34 and a subcooler 36.
  • the refrigerant tends to migrate to the coldest point in the system which may typically be the condenser (more particularly, the coldest part of the condenser at the subcooler).
  • a pump 38 (not a compressor) draws the refrigerant from the condenser and drives the refrigerant flow through the circuit 36 in a downstream direction.
  • the pump requires a supply of sub-cooled liquid refrigerant to ensure proper pump operation (e.g., prevent cavitation).
  • the exemplary pump is a fixed volume pump which delivers the same amount of refrigerant regardless of the cooling load.
  • the exemplary refrigerant remains sub-cooled at the refrigerant inlet of the refrigerant-air heat exchanger 32.
  • the refrigerant While passing through the heat exchanger 32, the refrigerant is warmed by the airflow through the AHU. As refrigerant passes downstream within the heat exchanger 32, it thus progressively transitions from the sub-cooled liquid state to a two-phase and gas & liquid state and eventually to a saturated gas or superheated gas.
  • the actual state of refrigerant exiting the refrigerant outlet of the heat exchanger 32 will depend upon the actual cooling load.
  • a maximal load condition e.g., characterized by high air temperature entering the AHU
  • all refrigerant will evaporate while passing through the heat exchanger 32 and exit the refrigerant outlet of the heat exchanger 32 in the superheated state.
  • a more moderate load condition e.g., a lower temperature of air entering the AHU
  • not enough heat is absorbed to evaporate all refrigerant, thus two-phase refrigerant will exit the refrigerant outlet of the heat exchanger 32 and return to the condenser.
  • the exemplary system includes an accumulator 40 containing an accumulation 42 of refrigerant.
  • the exemplary accumulator is immediately downstream of the condenser 34 and upstream of the subcooler 36 along the flowpath 30.
  • the exemplary condenser 34 and subcooler 36 each are formed as refrigerant-water heat exchangers whose water legs 44 and 46 are in parallel with each other.
  • the exemplary pump, condenser, and subcooler are shown mounted in common on a skid 50.
  • FIG. 1 shows a relatively large accumulation 42 associated with a high load condition.
  • FIG. 2 shows a second condition wherein the accumulation has shrunk in a low load condition.
  • Exemplary use of the unit 20 is in data center cooling wherein each of one or more such units may have one or more such heat exchangers 32 for cooling computer servers or similar equipment.
  • the accumulator may need to hold up to 50% of the total refrigerant charge of the unit.
  • a low load condition there is a relative high amount of liquid refrigerant in the heat exchangers 32 which is thus not in the accumulator.
  • refrigerant in the heat exchangers 32 is more fully evaporated, thereby necessitating its accumulation in the accumulator.
  • the accumulator contains two-phase refrigerant (i.e., liquid and gas).
  • the volume of the accumulator 40 may be selected based upon an anticipated range of operating conditions.
  • a condenser/accumulator having a shell.
  • a coolant flowpath extends from a coolant inlet to a coolant outlet.
  • An upper tube bundle is within the shell, a first branch of the coolant flowpath passing through tubes of the upper tube bundle.
  • a lower tube bundle is within the shell, a second branch of the coolant flowpath passing through tubes of the lower tube bundle.
  • a refrigerant flowpath extends from a refrigerant inlet to a refrigerant outlet and is in heat transfer relation with the coolant flowpath.
  • There is a vertical gap between the upper tube bundle and the lower tube bundle and comprising at least 50% of a free volume of a refrigerant space within the shell.
  • the first branch may be in parallel to the second branch and rejoin to pass through the remaining tubes of the upper tube bundle.
  • the vertical gap may comprise 60-80% of the free volume.
  • a vertical height of the gap may be at least 50% (more narrowly, 80-120%) of a characteristic internal radius of the shell.
  • a refrigerant volume below the upper tube bundle and outside of a subcooling chamber around the lower tube bundle may represent at least 30% of a total free volume of the refrigerant space.
  • the lower tube bundle may be within a subcooler chamber having refrigerant inlet ports and having a refrigerant outlet port positioned upstream of the refrigerant outlet.
  • the coolant inlet and coolant outlet may be on a first end dome.
  • the shell may comprise a circular cylindrical body and a pair of end plates forming bolting flanges (easy for mounting a pair of end domes).
  • a cooling system may comprise such a condenser/accumulator, a pump coupled to the refrigerant outlet, and a heat exchanger having a refrigerant inlet coupled to the pump and a refrigerant outlet coupled to the refrigerant inlet of the condenser/accumulator.
  • a fan may be positioned to drive an airflow across the heat exchanger.
  • There may be a plurality of such heat exchangers coupled in parallel to a single such condenser/accumulator.
  • the refrigerant charge may comprise at least 50% carbon dioxide by weight.
  • the system may include a chiller coupled to the coolant inlet and coolant outlet so that the coolant flowpath is along a coolant loop of the chiller.
  • the system may be operated by running the pump to: draw into the pump and discharge from the pump a flow of the refrigerant as supercooled liquid; pass the flow of the refrigerant through the heat exchanger where it draws heat from an external flow and becomes vapor; and pass the flow of the refrigerant to the condenser/accumulator wherein the flow of the refrigerant discharges heat to the coolant and condenses back to liquid.
  • the method may comprise: operating in a first cond ition wherein a surface of a liquid accumulation of the refrigerant in the vessel is within the gap; operating in a second condition, at higher cooling load than the first condition, wherein the surface of the liquid accumulation of the refrigerant in the vessel is also within the gap but higher than in the first condition; and shutting down the pump to go into a third condition wherein the surface of the liquid accumulation of the refrigerant in the vessel is above the gap.
  • the buildup of liquid accumulation between the first condition and the second condition may be at least 30% of a free internal volume of the vessel.
  • a buildup of the liquid accumulation between the first and the third condition may be at least 150% of the buildup of the liquid accumulation between the first condition and the second condition.
  • the cooling system comprises: a condenser/accumulator having a coolant flowpath and a refrigerant flowpath; a refrigerant air heat exchanger along the refrigerant flowpath; and a pump along the refrigerant flowpath downstream of the condenser/accumulator and upstream of the refrigerant air heat exchanger.
  • the method comprises: operating in a first cond ition wherein a surface of a l iqu id accumu lation of the refrigerant with in the condenser/accumulator is at a first level; operating in a second condition, at higher cooling load than the first condition, wherein the surface of the liquid accumulation is at a second level higher than the first level; and shutting down the pump to go into a third condition wherein the surface of the liquid accumulation is at a third level, higher than the second level.
  • the first level and the second level may be below a condenser tube bundle and above a subcooler tube bundle while the third level may be above at least a bottom of the condenser tube bundle.
  • FIG. 1 is a schematic view of a prior art system in a high load condition.
  • FIG. 2 is a user system of FIG. 1 in a low load condition.
  • FIG. 3 is a schematic view of a system in a low load condition.
  • FIG. 4 is a view of the system of FIG. 3 in a high load condition.
  • FIG. 5 is a view of the system of FIG. 3 in an off condition.
  • FIG. 6 is a view of a condenser/accumulator unit.
  • FIG. 7 is a side view of the condenser/accumulator unit.
  • FIG. 8 is an end view of the condenser/accumulator unit.
  • FIG. 10 is a bottom view of the condenser/accumulator unit.
  • FIG. 1 1 is a central transverse vertical sectional view of the condenser/accumulator unit, taken along line 1 1 -1 1 of FIG. 7.
  • FIG. 12 is a transverse vertical cutaway view of a first end manifold area of the condenser/accumulator unit.
  • FIG. 3 shows a modified unit 58 wherein the condenser, subcooler, and accumulator are combined in a single condenser/accumulator unit 60.
  • the unit 58 may be used similarly to the unit 20 in data center cooling with a plurality of units 58 coupled in parallel to one or more chillers. Each unit 60 and its associated pump may be on an associated skid.
  • An exemplary data center cooling use is shown in PCT/FR201 1/000224, the disclosure of which is incorporated by reference in its entirety herein as if set forth at length.
  • the unit 60 has a shell 62 and has a refrigerant inlet 64 and a refrigerant outlet 66 along the refrigerant circuit 30.
  • the unit 60 includes an upper tube bundle 68 and a lower tube bundle 70. The lower tube bundle is located within a subcooler chamber 72 discussed further below.
  • the unit 60 includes a main interior volume 74 along the refrigerant flowpath between the inlet 64 and outlet 66. A portion of the volume 74 is represented by a vertical gap 76 between the tube bundles 68 and 70. By providing a sufficiently large gap and volume associated therewith, the unit 60 may serve as an accumulator.
  • FIG. 3 shows a liquid refrigerant accumulation 80 having a surface 82.
  • FIG. 3 represents a minimum load condition (e.g., essentially no load). It may be desirable to size the system so that the minimum load liquid accumulation at least fully covers the tubes of the lower bundle 70 and may also at least just cover the upper surface of the chamber 72. Sizing the system to maintain at least this minimum level of accumulation prevents gas bypass (e.g., maintains the pump inlet flow as sub-cooled liquid to prevent cavitation).
  • gas bypass e.g., maintains the pump inlet flow as sub-cooled liquid to prevent cavitation.
  • FIG. 4 represents an anticipated maximum load condition wherein the level 82 has risen.
  • the shell is advantageously sized so that the level 82 remains below the lowest tubes of the upper bundle 68 even in this max load condition. If the liquid reaches the upper tube bundle, then there is a "flooded condenser" condition with reduced tube surface area for condensing (thereby causing insufficient condensing) which causes a pressure increase and performance degradation.
  • the flow at the refrigerant inlet 64 may represent superheated gas and transition passing over the tubes of the upper bundle 68 to a region 90 of saturated gas.
  • the superheated gas is quickly cooled to the saturation temperature (within the first (upper) couple of tube rows). Thereafter it is two-phase transitioning from saturated gas to saturated liquid.
  • FIG. 5 shows a pump-off (shut down) condition wherein there is still a coolant flow through the unit 60 but no refrigerant flow.
  • This may represent a condition wherein the AHU(s) are being serviced or the pump is otherwise shut down.
  • the heat exchanger(s) 32 may equilibrate to ambient temperature and, therefore, may fully contain superheated gas. Upstream of the pump 38 along the refrigerant flowpath, there may still be sub-cooled liquid. With superheated vapor in the heat exchanger 32, the greatest amount of refrigerant must be maintained within the shell.
  • the exemplary liquid surface 82 is within or above the upper tube bundle 68. This leaves the saturated vapor 90 thereabove.
  • the chamber 72 subcools the refrigerant so that saturated refrigerant enters the chamber 72 and is quickly subcooled and exits in a subcooled state.
  • the exemplary main interior volume 74 is circular cylindrical having a radius Ri from a central axis 500.
  • An exemplary height Hi of the gap 76 is at least 50% of Ri, more narrowly, at least 70% or 80- 120%.
  • the volume of the space 74 within the gap 76 may represent at least 50% of a total free volume of the space 74 (more particularly, at least 60% or 60-80%).
  • the free volume may be volume not occupied by the tubes (and their coolant) or other components.
  • the free volume of the space below the upper bundle may represent at least 30%, more narrowly 40-90% or 50-80% of a total free volume of the space 74 (e.g., excluding the subcooling chamber).
  • an exemplary buildup of the liquid accumulation between the minimum load condition and the maximum condition is at least 30% of a free internal volume of the vessel, more narrowly 35-70%.
  • An exemplary buildup of the liquid accumulation between the minimum load condition and the pump-off condition is at least 140% of the buildup of the liquid accumulation between the minimum load condition and the maximum load condition, more narrowly, at least 150% or 150-300% or 160-200%.
  • FIG. 6 shows the unit 60.
  • the exemplary unit has a shell 62 comprising a circular cylindrical pipe 120 having first and second ends at first and second end bolt flanges 122 and 124. Each of the end flanges bears a domed cover 126, 128 secured such as via bolt circles.
  • the exemplary unit 60 has a central longitudinal axis 500 (FIG. 7) which, in an exemplary embodiment, is maintained horizontal.
  • the exemplary refrigerant inlet 64 and outlet 66 are formed on respective fittings 134 and 136. In the exemplary embodiments, these fittings are positioned centrally along the sidewall of the pipe 120 at respective top and bottom locations and share a common axis 502.
  • FIG. 6 also shows respective upper and lower observation port fittings 140 and 142 (e.g., sight glasses).
  • the exemplary first end cover 126 bears the coolant inlet 144 and coolant outlet 146 receiving chilled water from the supply line 24 and returning warmed water to the return line 26, respectively.
  • the flanges are shown as being formed by peripheral portions of endplates 1 50 and 1 52 (e.g., welded to the pipe 1 20). Associated ends of the tubes of the upper and lower bundles are mounted in apertures of these endplates to communicate with plenums between the covers and the endplates.
  • FIG. 9 shows plenums 160 and 162 beneath the cover 126 and separated by a dividing wall 164 formed as a portion of the cover 126 such as via casting or machining of metal.
  • the plenum 160 is an inlet plenum communicating with the inlet port 144.
  • the plenum 162 is an outlet plenum communicating with the outlet port 146.
  • FIG. 12 shows the position of the wall 164 via a gasket portion 164'.
  • the wall subdivides the tubes of the upper bundle into a first subgroup 68- 1 and a second subgroup 68-2.
  • the first ends of the first subgroup and those of the lower bundle 70 are open to (at) the plenum 160.
  • the first ends of the tubes of the subgroup 68-2 are open to the outlet plenum 162.
  • FIG. 9 shows a single plenum 170 between the cover 128 and the wall 152.
  • the second ends of all the tubes are open to the plenum 70.
  • the inlet flow passing through the inlet 144 divides at the plenum 160 into two main branches: a first branch 200- 1 (FIG. 9) passing through the tubes of the first group 68- 1 ; and a second branch 200-2 passing through the tubes of the lower bundle 70 (with each of these two branches subdividing into sub-branches through the individual tubes.
  • the branches and sub-branches merge in the plenum 170 and then pass through the tubes of the second group into the plenum 162 and therefrom out the outlet 146.
  • FIG. 1 1 shows the subcooler chamber having a pair of lateral walls 220 and 222, an upper wall 224, and a lower wall 226.
  • An outlet conduit 228 extends from a central port/opening 230 in the lower wall.
  • the walls 220, 222, 224, and 226 extend between the endplates to surround an interior space 232 of the subcooler chamber.
  • FIG. 10 shows inlet ports 240 to the subcooler chamber formed as holes in the lower wall 230 in pairs adjacent the opposite endplates (which form end walls of the subcooler chamber). Refrigerant from the bottom of the shell interior flows upward through the ports 240 to be cooled by the water flowing through the bundle 70 and then exits via the pipe 228.
  • Refrigerant entering the inlet 64 may be spread via a baffle 250 (FIG. 9) spaced below the end of an inlet pipe/conduit 252. This may direct refrigerant over the upper bundle to be cooled by coolant (water) flowing: ( 1 ) through the first group 68-1 along the branch 200-1 ; and the merged coolant flow through the second group 68-2.
  • FIG. 9 further shows structural braces along inboard surfaces of the end walls 1 50 and 1 52 and a central tube template 260 for maintaining relative position of tubes of the upper bundle.
  • an air outlet temperature from the heat exchanger 32 is 22C.
  • a refrigerant inlet temperature to the unit 60 is 19C and the needed refrigerant outlet temperature is 12C.
  • An exemplary water inlet temperature is 7C.
  • the water is heated to I OC.
  • the water is heated to 8C.
  • the combined flows are at 9.5C in the mixing plenum.
  • the combined flow passing though the group 68-2 is then heated to a water outlet temperature of 12C.
  • the refrigerant passing through the upper bundle is cooled, reaching an exemplary 16C (e.g., 5- I OC less than the air outlet temperature to the space being cooled) within the two-phase section. Finally, in the subcooler, it cools down to the outlet temperature (e.g., 12C). With an exemplary/target air temperature other than 22C, the refrigerant and coolant temperatures would need to be correspondingly adjusted.
  • an exemplary/target air temperature other than 22C the refrigerant and coolant temperatures would need to be correspondingly adjusted.
  • Manufacture of the unit 60 may be of materials and techniques typical for condenser units used with C ( 1 ⁇ 4 refrigerant.

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

Abstract

L'invention porte sur un condensateur/accumulateur (60) qui comprend une carcasse (62). Un trajet d'écoulement de fluide de refroidissement s'étend d'une entrée de refroidissement (144) à une sortie de fluide de refroidissement (146). Un faisceau de tubes supérieur (68) est inclus dans la carcasse, une première branche du trajet d'écoulement de fluide de refroidissement passant dans les tubes du faisceau de tubes supérieur. Un faisceau de tubes inférieur (70) se trouve dans la carcasse, une seconde branche du trajet d'écoulement du fluide de refroidissement passant dans les tubes du faisceau de tubes inférieur. Un trajet d'écoulement de fluide de refroidissement s'étend d'une entrée de fluide de refroidissement (64) à une sortie de fluide de refroidissement (66) et est en relation de transfert de chaleur avec le trajet d'écoulement de fluide de refroidissement. Une fente verticale (76) est intercalée entre le faisceau de tubes supérieur et le faisceau de tubes inférieur et représente au moins 50 % du volume libre de l'espace de fluide de refroidissement à l'intérieur de la carcasse.
PCT/IB2011/001465 2011-04-21 2011-04-21 Condensateur/accumulateur et systèmes et procédés de commande Ceased WO2012143751A2 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP11740718.9A EP2661593B1 (fr) 2011-04-21 2011-04-21 Condensateur/accumulateur et systèmes et procédés de commande
PCT/IB2011/001465 WO2012143751A2 (fr) 2011-04-21 2011-04-21 Condensateur/accumulateur et systèmes et procédés de commande
US14/111,367 US20140034275A1 (en) 2011-04-21 2011-04-21 Condenser/Accumulator and Systems and Operation Methods
CN201180070249.4A CN103492821B (zh) 2011-04-21 2011-04-21 冷凝器/集液器和系统以及操作方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IB2011/001465 WO2012143751A2 (fr) 2011-04-21 2011-04-21 Condensateur/accumulateur et systèmes et procédés de commande

Publications (2)

Publication Number Publication Date
WO2012143751A2 true WO2012143751A2 (fr) 2012-10-26
WO2012143751A3 WO2012143751A3 (fr) 2013-03-07

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Country Status (4)

Country Link
US (1) US20140034275A1 (fr)
EP (1) EP2661593B1 (fr)
CN (1) CN103492821B (fr)
WO (1) WO2012143751A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105980803A (zh) * 2013-12-05 2016-09-28 林德股份公司 具有用于排放液相的收集通道的换热器
CN106766401A (zh) * 2016-12-27 2017-05-31 天津商业大学 双水程卧式直接接触凝结换热器
CN111426221A (zh) * 2020-05-18 2020-07-17 安徽东能换热装备有限公司 对半式上下组装换热器及其组装方法

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US20140034275A1 (en) 2014-02-06
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EP2661593A2 (fr) 2013-11-13
EP2661593B1 (fr) 2016-08-17

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