Classifications

• • 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
  • F28F9/02—Header boxes; End plates
• • 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
  • 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
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
• • 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
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
• • 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
• • 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
  • F28F9/02—Header boxes; End plates
  • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
  • F28F9/0224—Header boxes formed by sealing end plates into covers
• • 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
  • F28F9/02—Header boxes; End plates
  • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
  • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
• • 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
  • F28F9/02—Header boxes; End plates
  • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
  • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
• • 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
  • F28F9/02—Header boxes; End plates
  • F28F9/04—Arrangements for sealing elements into header boxes or end plates
  • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
  • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
  • F28F9/185—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding with additional preformed parts

Definitions

• This invention relates generally to heat exchangers having a plurality of parallel tubes extending between a first header and a second header, also sometimes referred to as manifolds, and, more particularly, to providing fluid expansion within the header of a heat exchanger for improving distribution of two- phase flow through the parallel tubes of the heat exchanger, for example a heat exchanger in a refrigerant compression system.
• Air conditioners and heat pumps employing refrigerant vapor compression cycles are commonly used for cooling or cooling/heating air supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility.
• Refrigeration vapor compression systems are also commonly used for cooling air or other secondary fluid to provide a refrigerated environment for food items and beverage products within, for instance, display cases in supermarkets, convenience stores, groceries, cafeterias, restaurants and other food service establishments.
• these refrigerant vapor compression systems include a compressor, a condenser, an expansion device, and an evaporator connected in refrigerant flow communication.
• the aforementioned basic refrigerant system components are interconnected by refrigerant lines in a closed refrigerant circuit and arranged in accord with the vapor compression cycle employed.
• An expansion device commonly an expansion valve or a fixed-bore metering device, such as an orifice or a capillary tube, is disposed in the refrigerant line at a location in the refrigerant circuit upstream, with respect to refrigerant flow, of the evaporator and downstream of the condenser.
• the expansion device operates to expand the liquid refrigerant passing through the refrigerant line running from the condenser to the evaporator to a lower pressure and temperature. In doing so, a portion of the liquid refrigerant traversing the expansion device expands to vapor.
• the refrigerant flow entering the evaporator constitutes a two-phase mixture.
• the particular percentages of liquid refrigerant and vapor refrigerant depend upon the particular expansion device employed and the refrigerant in use, for example Rl 2, R22, Rl 34a, R404A, R410A, R407C, R717, R744 or other compressible fluid.
• the evaporator is a parallel tube heat exchanger.
• Such heat exchangers have a plurality of parallel refrigerant flow paths therethrough provided by a plurality of tubes extending in parallel relationship between an inlet header and an outlet header.
• the inlet header receives the refrigerant flow from the refrigerant circuit and distributes it amongst the plurality of flow paths through the heat exchanger.
• the outlet header serves to collect the refrigerant flow as it leaves the respective flow paths and to direct the collected flow back to the refrigerant line for a return to the compressor in a single pass heat exchanger or through an additional bank of heat exchange tubes in a multipass heat exchanger.
• parallel tube heat exchangers used in such refrigerant compression systems have used round tubes, typically having a diameter of 1 A inch, 3/8 inch or 7 millimeters.
• multichannel tubes are being used in heat exchangers for refrigerant vapor compression systems.
• Each mutli-channel tube has a plurality of flow channels extending longitudinally in parallel relationship the length of the tube, each channel providing a small cross-sectional flow area refrigerant path.
• a heat exchanger with multi-channel tubes extending in parallel relationship between the inlet and outlet headers of the heat exchanger will have a relatively large number of small cross- sectional flow area refrigerant paths extending between the two headers.
• a parallel tube heat exchanger with conventional round tubes will have a relatively small number of large flow area flow paths extending between the inlet and outlet headers.
• Non-uniform distribution, also referred to as maldistibution, of two- phase refrigerant flow is a common problem in parallel tube heat exchangers which adversely impacts heat exchanger efficiency.
• Two-phase maldistribution problems are caused by the difference in density of the vapor phase refrigerant and the liquid phase refrigerant present in the inlet header due to the expansion of the refrigerant as it traversed the upstream expansion device.
• Japanese Patent No. 6241682, Massaki et al. discloses a parallel flow tube heat exchanger for a heat pump wherein the inlet end of each multichannel tube connecting to the inlet header is crushed to form a partial throttle restriction in each tube just downstream of the tube inlet.
• Japanese Patent No. JP8233409, Hiroaki et al. discloses a parallel flow tube heat exchanger wherein a plurality of flat, multichannel tubes connect between a pair of headers, each of which has an interior which decreases in flow area in the direction of refrigerant flow as a means to uniformly distribute refrigerant to the respective tubes.
• JP2002022313 Yasushi discloses a parallel tube heat exchanger wherein refrigerant is supplied to the header through an inlet tube that extends along the axis of the header to terminate short of the end the header whereby the two phase refrigerant flow does not separate as it passes from the inlet tube into an annular channel between the outer surface of the inlet tube and the inside surface of the header. The two phase refrigerant flow thence passes into each of the tubes opening to the annular channel.
• a heat exchanger having a header defining a chamber for receiving a fluid and at least one heat exchange tube having a plurality of fluid flow paths therethrough from an inlet end to an outlet end of the tube and having an inlet opening to the plurality of fluid flow paths.
• a connector has an inlet end in fluid flow communication with the chamber of the header through a first opening and an outlet end in fluid communication with the inlet opening of said at least one heat exchange tube through a second opening.
• the connector defines a fluid flow path extending from its inlet end to its outlet end.
• the flow path through the connector may be divergent in the direction of fluid flow therethrough.
• the first opening has a relatively small flow area so as to provide a flow restriction through which fluid passes in flowing from the chamber of the header to the flow paths of the heat exchange tube.
• a refrigerant vapor compression system includes a compressor, a condenser and an evaporative heat exchanger connected in refrigerant flow communication whereby high pressure refrigerant vapor passes from the compressor to the condenser, high pressure refrigerant liquid passes from the condenser to the evaporative heat exchanger, and low pressure refrigerant vapor passes from the evaporative heat exchanger to the compressor.
• the evaporative heat exchanger includes an inlet header and an outlet header, and a plurality of heat exchange tubes extending between the headers.
• the inlet header defines a chamber for receiving liquid refrigerant from a refrigerant circuit.
• Each heat exchange tube has an inlet end, an outlet end, and a plurality of fluid flow paths extending from an inlet opening at the inlet end to an outlet opening at the outlet end of the tube.
• a connector has an inlet end in fluid flow communication with the chamber of the inlet header through a first opening and has an outlet end in fluid flow communication through a second opening with the inlet opening of a heat exchange tube.
• the connector defines a fluid flow path extending from its inlet end to its outlet end.
• the flow path through the connector may be divergent in the direction of fluid flow therethrough.
• the first opening has a relatively small cross-sectional flow area so as to provide a flow restriction through which fluid passes in flowing from the chamber of the header to the flow paths of the heat exchange tube.
• Figure 1 is a perspective view of an embodiment of a heat exchanger in accordance with the invention.
• Figure 2 is a perspective view, partly sectioned, taken along line 2-2 of Figure 1;
• Figure 3 is a sectioned elevation view taken along line 3-3 of
• Figure 4 is a sectioned view taken along line 4-4 of Figure 3;
• Figure 5 is a sectioned view taken along line 5-5 of Figure 3;
• Figure 6 is a perspective view, partly sectioned, of an another embodiment of a heat exchanger in accordance with the invention.
• Figure 7 is a sectioned view taken along line 7-7 of Figure 6;
• Figure 8 is a sectioned view taken along line 8-8 of Figure 7;
• Figure 9 is a schematic illustration of a refrigerant vapor compression system incorporating the heat exchanger of the invention.
• FIG. 10 is a schematic illustration of another refrigerant vapor compression system incorporating the heat exchanger of the invention.
• Figure 11 is an elevation view, partly in section, of an embodiment of a multi-pass evaporator in accordance with the invention.
• Figure 12 is an elevation view, partly in section, of an embodiment of a multi-pass condenser in accordance with the invention.
• the heat exchanger 10 of the invention will be described in general herein with reference to the illustrative single pass, parallel-tube embodiment of a mutli-channel tube heat exchanger as depicted in Figure 1.
• the heat exchange tubes 40 are shown arranged in parallel relationship extending generally vertically between a generally horizontally extending inlet header 20 and a generally horizontally extending outlet header 30.
• the depicted embodiment is illustrative and not limiting of the invention. It is to be understood that the invention described herein may be practiced on various other configurations of the heat exchanger 10.
• the heat exchange tubes may be arranged in parallel relationship extending generally horizontally between a generally vertically extending inlet header and a generally vertically extending outlet header.
• the heat exchanger could have a toroidal inlet header and a toroidal outlet header of a different diameter with the heat exchange tubes extend either somewhat radially inwardly or somewhat radially outwardly between the toroidal headers.
• the heat exchange tubes may also be arranged in parallel tube, multi-pass embodiments, as will be discussed in further detail later herein with reference to Figures 11 and 12.
• the heat exchanger 10 includes an inlet header 20, an outlet header 30, and a plurality of longitudinally extending multi-channel heat exchanger tubes 40 thereby providing a plurality of fluid flow paths between the inlet header 20 and the outlet header 30.
• Each heat exchange tube 40 has an inlet 43 at one end in fluid flow communication to the inlet header 20 through a connector 50 and an outlet at its other end in fluid flow communication to the outlet header 30.
• Each heat exchange tube 40 has a plurality of parallel flow channels 42 extending longitudinally, i.e. along the axis of the tube, the length of the tube thereby providing multiple, independent, parallel flow paths between the inlet of the tube and the outlet of the tube.
• Each multi-channel heat exchange tube 40 is a "flat" tube of, for instance, rectangular or oval cross-section, defining an interior which is subdivided to form a side-by-side array of independent flow channels 42.
• the flat, multi-channel tubes 40 may, for example, have a width of fifty millimeters or less, typically twelve to twenty-five millimeters, and a height of about two millimeters or less, as compared to conventional prior art round tubes having a diameter of V 2 inch, 3/8 inch or 7 mm.
• the tubes 40 are shown in drawings hereof, for ease and clarity of illustration, as having twelve channels 42 defining flow paths having a circular cross-section.
• each multi-channel tube 40 will typically have about ten to twenty flow channels 42, but may have a greater or a lesser multiplicity of channels, as desired.
• each flow channel 42 will have a hydraulic diameter, defined as four times the flow area divided by the perimeter, in the range from about 200 microns to about 3 millimeters.
• the channels 42 may have a rectangular, triangular, trapezoidal cross- section or any other desired non-circular cross-section.
• each connector 50 has an inlet end 52 and an outlet end 54 and defines a fluid flow path 55 extending from the inlet end 52 to the outlet end 54.
• the inlet end 52 is in fluid flow communication with the chamber 25 of the inlet header 20 through a first opening 51.
• the outlet end 54 is in fluid communication through a second opening 53 with the inlet openings 41 of the channels 42 at the inlet end of the associated heat transfer tube 40 received therein.
• the first opening 51 at the inlet end 52 of each connector 50 has a relatively small cross-sectional flow area.
• the connectors 50 provide a plurality of flow restrictions, at least one associated with each heat transfer tube 40, that provide uniformity in pressure drop in the fluid flowing from the chamber 25 of the header 20 into the fluid flow path 55 within the connector 50, thereby ensuring a relatively uniform distribution of fluid amongst the individual tubes 40 operatively associated with the header 20.
• the inlet header 20 comprises a longitudinally elongated, hollow, closed end cylinder having a circular cross-section.
• the inlet end 52 of each connector 50 is mated with a corresponding slot 26 provided in and extending through the wall of the inlet header 20 with the inlet end 52 of the connector 50 inserted into its corresponding slot.
• Each connector may be brazed, welded, soldered, adhesively bonded, diffusion bonded or otherwise secured in a corresponding mating slot in the wall of the header 20.
• the inlet header 20 is not limited to the depicted configuration.
• the header 20 might comprise a longitudinally elongated, hollow, closed end cylinder having an elliptical cross-section or a longitudinally elongated, hollow, closed end pipe having a square, rectangular, hexagonal, octagonal, or other cross-section.
• the inlet header 20 comprises a longitudinally elongated, hollow, closed end, half cylinder shell having a generally semi-circular cross-section and a block-like insert 58 that is brazed, welded, adhesively bonded or otherwise secured to the open face of the half cylinder shell.
• the longitudinally, extending block-like insert 58 forms a single connector 50.
• a plurality of longitudinally spaced, parallel flow paths 55 is formed within the block-like structure of the connector 50.
• Each flow path 55 has an inlet end 52 having at least one relatively small flow area inlet opening 51 in fluid communication with a fluid chamber 25 defined within the header 20 and an outlet end 54 having an opening 53 adapted to receive the inlet end 42 of a heat exchange tube 40. Therefore, in this embodiment, a plurality of heat exchange tubes 40 are connected to the header by means of a single block-like connector 50.
• the block-like insert 58 provides a connector 50 having a plurality of flow restrictions, with at least one relatively small flow area opening 51 in operative association with each heat transfer tube 40, that provide uniformity in pressure drop in the fluid flowing from the chamber 25 of the header 20 into the fluid flow path 55 within the connector 50, thereby ensuring a relatively uniform distribution of fluid amongst the individual tubes 40 operatively associated with the header 20.
• first opening 51 of relatively small flow area is provided in the inlet end 52 of each connector 50.
• more than one first opening 51 of relatively small flow area may be provided at the inlet end 52 of the connector 50.
• the fluid flow path 55 extending from the inlet opening 51 at the inlet end 52 of the connector 50 to the outlet opening 53 at the outlet end 54 of the connector 50 may, as best depicted in Figure 3 and in Figure 7, diverge in the direction of fluid flow from the inlet opening 51 to the outlet opening 53.
• a divergent flow path assists in distributing the fluid flowing through the flow path 55 uniformly amongst the various flow channels 42 of the heat exchange tube 40 inserted into the outlet end 54 of the connector 50, particularly in refrigerant flow applications wherein the fluid is a liquid refrigerant and vapor refrigerant mixture or expands to a liquid refrigerant/vapor refrigerant mixture as the fluid passes through the relatively small flow area opening or openings 51.
• FIG. 9 there is depicted schematically a refrigerant vapor compression system 100 having a compressor 60, the heat exchanger 1OA, functioning as a condenser, and the heat exchanger 1OB, functioning as an evaporator, connected in a closed loop refrigerant circuit by refrigerant lines 12, 14 and 16.
• the compressor 60 circulates hot, high pressure refrigerant vapor through refrigerant line 12 into the inlet header 120 of the condenser 1OA, and thence through the heat exchanger tubes 140 of the condenser 1OA wherein the hot refrigerant vapor condenses to a liquid as it passes in heat exchange relationship with a cooling fluid, such as ambient air which is passed over the heat exchange tubes 140 by a condenser fan 70.
• the high pressure, liquid refrigerant collects in the outlet header 130 of the condenser 1OA and thence passes through refrigerant line 14 to the inlet header 20 of the evaporator 1OB.
• the refrigerant passes through the heat exchanger tubes 40 of the evaporator 1OB wherein the refrigerant is heated as it passes in heat exchange relationship with air to be cooled which is passed over the heat exchange tubes 40 by an evaporator fan 80.
• the refrigerant vapor collects in the outlet header 30 of the evaporator 1OB and passes therefrom through refrigerant line 16 to return to the compressor 60 through the suction inlet thereto.
• the exemplary refrigerant vapor compression cycles illustrated in Figures 9 and 10 are simplified air conditioning cycles, it is to be understood that the heat exchanger of the invention may be employed in refrigerant vapor compression systems of various designs, including, without limitation, heat pump cycles, economized cycles and refrigeration cycles.
• the condensed refrigerant liquid passes from the condenser 1OA directly to the evaporator 1OB without traversing an expansion device.
• the refrigerant typically enters the inlet header 20 of the evaporative heat exchanger 1OB as a high pressure, liquid refrigerant, not as a fully expanded, low pressure, refrigerant liquid/vapor mixture, as in conventional refrigerant compression systems.
• expansion of the refrigerant occurs within the evaporator 1OB of the invention as the refrigerant passes through the relatively small area opening or openings 51 at the inlet end 52 into the flow path 55 of the connector 50, thereby ensuring that expansion occurs only after the distribution has been achieved in a substantially uniform manner.
• the condensed refrigerant liquid passes through an expansion valve 50 operatively associated with the refrigerant line 14 as it passes from the condenser 1OA to the evaporator 1OB.
• the expansion valve 50 the high pressure, liquid refrigerant is partially expanded to lower pressure and lower temperature, liquid refrigerant or a liquid/vapor refrigerant mixture.
• the final expansion of the refrigerant is completed within the evaporator 1OB as the refrigerant passes through the relatively small flow area opening or openings 51 at the inlet end 52 into the flow path 55 of the connector 50.
• Partial expansion of the refrigerant in an expansion valve upstream of the inlet header 20 to the evaporator 1OB may be advantageous when the cross- sectional flow area of the openings 51, can not be made small enough to ensure complete expansion as the liquid passes through the openings 51 or when an expansion valve is used as a flow control device.
• the heat exchanger 10 of the invention is depicted in a multi-pass, evaporator embodiment.
• the inlet header 20 is partitioned into a first chamber 2OA and a second chamber 2OB
• the outlet header is also partitioned into a first chamber 3OA and a second chamber 3OB
• the heat exchange tubes 40 are divided into three banks 4OA, 4OB and 4OC.
• the tubes of the first tube bank 4OA have inlet ends inserted into respective connectors 50A that are open into the first chamber 2OA of the inlet header 20 and outlet ends are open to the first chamber 30A of the outlet header 30.
• the tubes of the second tube bank 4OB have inlet ends inserted into respective connectors 5OB that are open into the first chamber 3OA of the outlet header 30 and outlet ends are open to the second chamber 2OB of the inlet header 20.
• the tubes of the third tube bank 40C have inlet ends inserted into respective connectors 5OC that open into the second chamber 2OB of the inlet header 20 and outlet ends are open to the second chamber 30B of the outlet header 30.
• the inlet end 43 of each of the tubes of the first, second and third tube banks 4OA, 4OB and 4OC is inserted into the outlet end 54 of its associated connector 50 whereby the channels 42 of each of the tubes 40 will receive a relatively uniform distribution of expanded refrigerant liquid/vapor mixture.
• Distribution and expansion of the refrigerant occurs as the refrigerant passes from the header into the connector through the relatively small cross-sectional flow area opening 51, not only as the refrigerant passes into the first tube bank 4OA, but also as the refrigerant passes into the second tube bank 40B and into the third tube bank 4OC, thereby ensuring more uniform distribution of the refrigerant liquid/vapor upon entering the flow channels of the tubes of each tube bank.
• the heat exchanger 10 of the invention is depicted in a multi-pass, condenser embodiment.
• the inlet header 120 is partitioned into a first chamber 120A and a second chamber 120B
• the outlet header 130 is also partitioned into a first chamber 130A and a second chamber 130B
• the heat exchange tubes 140 are divided into three banks 140A, 140B and 140C.
• the tubes of the first tube bank 140A have inlet end openings into the first chamber 120A of the inlet header 120 and outlet end openings to the first chamber 130A of the outlet header 130.
• the tubes of the second tube bank 140B have inlet ends inserted into respective connectors 5OB that are open into the first chamber 130A of the outlet header 130 and outlet ends that are open to the second chamber 120B of the inlet header 120.
• the tubes of the third tube bank 140C have inlet ends inserted into respective connectors 50C that are open into the second chamber 120B of the inlet header 120 and outlet ends are open to the second chamber 130B of the outlet header 130.
• the refrigerant entering the first chamber 120A of the inlet header 120 is entirely high pressure, refrigerant vapor directed from the compressor outlet via refrigerant line 14.
• the refrigerant entering the second tube bank and the third tube bank typically will be a liquid/vapor mixture as refrigerant partially condenses in passing through the first and second tube banks.
• the inlet end of each of the tubes of the second and third tube banks 140B, 140C is inserted into the outlet ends of their associated connectors 5OB, 5OC whereby the channels 42 of each of the tubes will receive a relatively uniform distribution of expanded refrigerant liquid/vapor mixture.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Thermal Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Geometry (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Steam Or Hot-Water Central Heating Systems (AREA)
• Details Of Heat-Exchange And Heat-Transfer (AREA)
• Separation By Low-Temperature Treatments (AREA)

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• 2005
  • 2005-12-28 AT AT05855856T patent/ATE529717T1/de not_active IP Right Cessation
  • 2005-12-28 KR KR1020077016474A patent/KR20070091201A/ko not_active Ceased
  • 2005-12-28 CA CA002596573A patent/CA2596573A1/en not_active Abandoned
  • 2005-12-28 MX MX2007009245A patent/MX2007009245A/es unknown
  • 2005-12-28 CN CN2005800475300A patent/CN101120225B/zh not_active Expired - Fee Related
  • 2005-12-28 US US11/793,880 patent/US20080092587A1/en not_active Abandoned
  • 2005-12-28 AU AU2005326654A patent/AU2005326654B2/en not_active Ceased
  • 2005-12-28 ES ES05855856T patent/ES2373964T3/es not_active Expired - Lifetime
  • 2005-12-28 JP JP2007554092A patent/JP2008528943A/ja not_active Withdrawn
  • 2005-12-28 BR BRPI0519933-6A patent/BRPI0519933A2/pt not_active IP Right Cessation
  • 2005-12-28 EP EP05855856A patent/EP1844288B1/de not_active Expired - Lifetime
  • 2005-12-28 WO PCT/US2005/047363 patent/WO2006083449A2/en not_active Ceased

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