EP1844288B1 - Échangeur de chaleur à détente du fluide dans le collecteur - Google Patents

Échangeur de chaleur à détente du fluide dans le collecteur Download PDF

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Publication number
EP1844288B1
EP1844288B1 EP05855856A EP05855856A EP1844288B1 EP 1844288 B1 EP1844288 B1 EP 1844288B1 EP 05855856 A EP05855856 A EP 05855856A EP 05855856 A EP05855856 A EP 05855856A EP 1844288 B1 EP1844288 B1 EP 1844288B1
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EP
European Patent Office
Prior art keywords
heat exchanger
recited
fluid flow
refrigerant
opening
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.)
Not-in-force
Application number
EP05855856A
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German (de)
English (en)
Other versions
EP1844288A4 (fr
EP1844288A2 (fr
Inventor
Mikhail B. Gorbounov
Steven A. Lozyniak
Parmesh Verma
Michael F. Taras
Robert A. Chopko
Allen C. Kirkwood
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
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Publication date
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Publication of EP1844288A4 publication Critical patent/EP1844288A4/fr
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Publication of EP1844288B1 publication Critical patent/EP1844288B1/fr
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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.
  • US - A 5 320 165 discloses a heat exchanger according to the preamble of claim 1.
  • Refrigerant vapor compression systems are well known in the art. 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 R12, R22, R134a, 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 multi-pass heat exchanger.
  • parallel tube heat exchangers used in such refrigerant compression systems have used round tubes, typically having a diameter of 1 ⁇ 2 inch, 3/8 inch or 7 millimeters.
  • multi-channel 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 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, multi-channel 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.
  • Japanese Patent No. 6241682 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
  • 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 collecting a fluid, at least one multi-channel heat exchange tube defining a plurality of discrete fluid flow channels extending longitudinally therethrough and having an inlet opening to said plurality of discrete fluid flow channels; and one or a plurality of connector(s) having an inlet end and an outlet end and defining a fluid flow path extending from said inlet end to said outlet end, said inlet end in fluid flow communication with the chamber of said header through a first opening and said outlet end in fluid communication with the inlet opening of one or all of said multi-channel heat exchange tube(s) through a second opening, said first opening being at least one flow restricting expansion orifice having a relatively small cross-sectional flow area.
  • 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 exchanger
  • a refrigerant vapor compression system in another aspect of the invention, includes a compressor, a condenser and an evaporative heat exchanger as described above 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.
  • 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 2 ;
  • 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 ;
  • FIG. 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 1 ⁇ 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 of the plurality of heat exchange tubes 40 of the heat exchanger 10 has its inlet end 43 inserted into a connector 50, rather than directly into the chamber 25 defined within the inlet header 20.
  • 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 10A, functioning as a condenser, and the heat exchanger 10B, 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 10A, and thence through the heat exchanger tubes 140 of the condenser 10A 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 10A and thence passes through refrigerant line 14 to the inlet header 20 of the evaporator 10B.
  • the refrigerant passes through the heat exchanger tubes 40 of the evaporator 10B 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 10B 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 10A directly to the evaporator 10B without traversing an expansion device.
  • the refrigerant typically enters the inlet header 20 of the evaporative heat exchanger 10B 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 10B 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 10A to the evaporator 10B.
  • 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 10B 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 10B 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 20A and a second chamber 20B
  • the outlet header is also partitioned into a first chamber 30A and a second chamber 30B
  • the heat exchange tubes 40 are divided into three banks 40A, 40B and 40C.
  • the tubes of the first tube bank 40A have inlet ends inserted into respective connectors 50A that are open into the first chamber 20A 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 40B have inlet ends inserted into respective connectors 50B that are open into the first chamber 30A of the outlet header 30 and outlet ends are open to the second chamber 20B of the inlet header 20.
  • the tubes of the third tube bank 40C have inlet ends inserted into respective connectors 50C that open into the second chamber 20B 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 40A, 40B and 40C 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 40A, but also as the refrigerant passes into the second tube bank 40B and into the third tube bank 40C, 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 50B 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 50B, 50C whereby the channels 42 of each of the tubes will receive a relatively uniform distribution of expanded refrigerant liquid/vapor mixture.
  • pressure drop through the openings 51 has to be limited to not exceed a predetermined threshold for the condenser applications, in order not to compromise the heat exchanger efficiency.
  • a person ordinarily skilled in the art would understand that other multi-pass arrangements for condensers and evaporators are also within the scope of the invention.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)

Claims (23)

  1. Echangeur de chaleur (10) comprenant :
    un réceptacle (20) définissant une chambre (25) permettant de collecter un fluide ;
    au moins un tube d'échange de chaleur multicanal (40) définissant une pluralité de canaux d'écoulement de fluide distincts (42) s'étendant longitudinalement au travers et comportant une ouverture d'admission (41) vers ladite pluralité de canaux d'écoulement de fluide distincts (42) ; et
    un raccord ou une pluralité de raccords (50) comportant une extrémité d'admission (52) et une extrémité de refoulement (54) et définissant un chemin d'écoulement de fluide (55) s'étendant de ladite extrémité d'admission (52) à ladite extrémité de refoulement (54), ladite extrémité d'admission étant en communication d'écoulement de fluide avec la chambre (25) dudit réceptacle (20) par l'intermédiaire d'une première ouverture (51) et ladite extrémité de refoulement (54) étant en communication de fluide avec l'ouverture d'admission (41) d'un ou de la totalité desdits tube(s) d'échange de chaleur multicanaux (40) par l'intermédiaire d'une seconde ouverture (53), caractérisé en ce que ladite première ouverture (51) est au moins un orifice de dilatation réducteur de débit ayant une superficie d'écoulement en coupe relativement petite.
  2. Echangeur de chaleur (10) selon la revendication 1, dans lequel le chemin d'écoulement de fluide (55) du ou de chacun desdits raccord(s) (50) comprend un chemin d'écoulement de fluide divergent se dilatant uniformément en section dans la direction d'écoulement de fluide en travers depuis ladite première ouverture (51) vers ladite seconde ouverture (53) pour distribuer uniformément un fluide à travers ledit chemin d'écoulement (55) vers chaque canal d'écoulement de fluide distinct (42) de ladite pluralité de canaux d'écoulement de fluide distincts (42)..
  3. Echangeur de chaleur (10) selon la revendication 1, dans lequel ledit au moins un tube d'échange de chaleur multicanal (40) a une section non ronde aplatie.
  4. Echangeur de chaleur (10) selon la revendication 3, dans lequel ledit au moins un tube d'échange de chaleur multicanal (40) a une section rectangulaire aplatie.
  5. Echangeur de chaleur (10) selon la revendication 3, dans lequel ledit au moins un tube d'échange de chaleur multicanal (40) a une section généralement ovale aplatie.
  6. Echangeur de chaleur (10) selon la revendication 1, dans lequel chacun de ladite pluralité de canaux d'écoulement de fluide distincts (42) définit un chemin d'écoulement ayant une section non circulaire.
  7. Echangeur de chaleur (10) selon la revendication 6, dans lequel chacun de ladite pluralité de canaux d'écoulement de fluide distincts (42) définit un chemin d'écoulement (55) choisi dans le groupe constitué par une section rectangulaire, triangulaire ou trapézoïdale.
  8. Echangeur de chaleur (10) selon la revendication 1, dans lequel chacun de ladite pluralité de canaux d'écoulement de fluide distincts (42) définit un chemin d'écoulement (55) ayant une section circulaire.
  9. Echangeur de chaleur (10) selon la revendication 1, dans lequel ladite première ouverture (51) comprend une pluralité d'ouvertures (51).
  10. Système de compression de vapeur à fluide frigorigène (100) comprenant :
    un compresseur (60), un condenseur (10A) et un échangeur de chaleur par évaporation (10B) tel que précisé dans la revendication 1, raccordés en communication de fluide dans un circuit de fluide frigorigène, où une vapeur de fluide frigorigène de haute pression passe dudit compresseur (60) audit condenseur (10A), un fluide frigorigène de haute pression passe dudit condenseur (10A) audit échangeur de chaleur par évaporation (10B), et une vapeur de fluide frigorigène de basse pression passe dudit échangeur de chaleur par évaporation (10B) audit compresseur (60).
  11. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel ladite première ouverture (51) dudit raccord (50) comprend un orifice de détente.
  12. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel le chemin d'écoulement de fluide (55) du ou de chacun desdits raccord(s) (50) comprend un chemin d'écoulement de fluide divergent se dilatant en section dans la direction d'écoulement de fluide en travers depuis ladite première ouverture (51) vers ladite seconde ouverture (53).
  13. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 12, dans lequel ladite première ouverture (51) du ou de chacun desdits raccord(s) (50) comprend un orifice de détente.
  14. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel ledit au moins un tube d'échange de chaleur multicanal (40) a une section non ronde aplatie.
  15. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 14, dans lequel ledit au moins un tube d'échange de chaleur multicanal (40) a une section rectangulaire aplatie.
  16. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 14, dans lequel ledit au moins un tube d'échange de chaleur multicanal (40) a une section généralement ovale aplatie.
  17. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel chacun de ladite pluralité de canaux d'écoulement de fluide distincts (42) définit un chemin d'écoulement ayant une section non circulaire.
  18. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel chacun de ladite pluralité de canaux d'écoulement de fluide distincts (42) définit un chemin d'écoulement (55) et est choisi dans le groupe constitué par une section rectangulaire, triangulaire ou trapézoïdale.
  19. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel chacun de ladite pluralité de canaux d'écoulement de fluide distincts (42) définit un chemin d'écoulement (55) ayant une section circulaire.
  20. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel ledit échangeur de chaleur (10B) comprend un échangeur de chaleur à passage unique.
  21. Système de compression de vapeur à fluide frigorigène (100) selon la revendication 10, dans lequel ledit échangeur de chaleur (10B) comprend un échangeur de chaleur à passages multiples.
  22. Echangeur de chaleur selon la revendication 1, dans lequel ledit échangeur de chaleur (10B) est un condenseur.
  23. Echangeur de chaleur selon la revendication 1, dans lequel ledit échangeur de chaleur (10B) est un évaporateur.
EP05855856A 2005-02-02 2005-12-28 Échangeur de chaleur à détente du fluide dans le collecteur Not-in-force EP1844288B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US64926905P 2005-02-02 2005-02-02
PCT/US2005/047363 WO2006083449A2 (fr) 2005-02-02 2005-12-28 Échangeur de chaleur à détente du fluide dans le collecteur

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EP1844288A2 EP1844288A2 (fr) 2007-10-17
EP1844288A4 EP1844288A4 (fr) 2010-07-21
EP1844288B1 true EP1844288B1 (fr) 2011-10-19

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KR (1) KR20070091201A (fr)
CN (1) CN101120225B (fr)
AT (1) ATE529717T1 (fr)
AU (1) AU2005326654B2 (fr)
BR (1) BRPI0519933A2 (fr)
CA (1) CA2596573A1 (fr)
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HK (1) HK1118331A1 (fr)
MX (1) MX2007009245A (fr)
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11713931B2 (en) 2019-05-02 2023-08-01 Carrier Corporation Multichannel evaporator distributor

Families Citing this family (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008064199A1 (fr) * 2006-11-22 2008-05-29 Johnson Controls Technology Company Évaporateur multicanaux comprenant un collecteur séparant l'écoulement
WO2008064238A1 (fr) 2006-11-22 2008-05-29 Johnson Controls Technology Company Échangeur de chaleur multicanaux à tubes multicanaux dissemblables
WO2009018150A1 (fr) 2007-07-27 2009-02-05 Johnson Controls Technology Company Echangeur thermique a multiples canaux
US20090025405A1 (en) 2007-07-27 2009-01-29 Johnson Controls Technology Company Economized Vapor Compression Circuit
US20100071880A1 (en) * 2008-09-22 2010-03-25 Chul-Ju Kim Evaporator for looped heat pipe system
ES2385767B1 (es) * 2009-04-15 2013-06-17 Bsh Electrodomesticos España S.A. Licuador así como también bomba de calor y aparato doméstico con un licuador de tal tipo.
US8439104B2 (en) 2009-10-16 2013-05-14 Johnson Controls Technology Company Multichannel heat exchanger with improved flow distribution
EP2383779B1 (fr) * 2010-04-29 2012-09-12 ABB Oy Base de montage
WO2013004276A1 (fr) * 2011-07-01 2013-01-10 Statoil Petroleum As Système de distribution multiphasique, échangeur de chaleur sous-marin et procédé de régulation de température pour hydrocarbures
JP5287949B2 (ja) * 2011-07-28 2013-09-11 ダイキン工業株式会社 熱交換器
JP5890705B2 (ja) * 2012-02-27 2016-03-22 株式会社日本クライメイトシステムズ 熱交換器
CN102661671A (zh) * 2012-04-28 2012-09-12 泰州市远望换热设备有限公司 换热器进气口缓冲结构
JP5790730B2 (ja) * 2012-12-25 2015-10-07 ダイキン工業株式会社 熱交換器
WO2015004720A1 (fr) * 2013-07-08 2015-01-15 三菱電機株式会社 Échangeur de chaleur, et appareil de conditionnement de l'air
CN103776282B (zh) * 2014-02-20 2015-08-05 丹佛斯微通道换热器（嘉兴）有限公司 换热器
US10072900B2 (en) * 2014-09-16 2018-09-11 Mahle International Gmbh Heat exchanger distributor with intersecting streams
US20170307301A1 (en) * 2014-11-11 2017-10-26 Dantherm Cooling A/S Thermosiphon blocks and thermosiphon systems for heat transfer
US10161685B2 (en) * 2015-01-09 2018-12-25 Trane International Inc. Heat exchanger with partitioned inlet header for enhanced flow distribution and refrigeration system using the heat exchanger
US10533291B2 (en) * 2015-01-13 2020-01-14 Craig A. Perkins Snow melting mat
DK3101339T3 (da) * 2015-06-03 2021-07-26 Alfa Laval Corp Ab Samleanordning til et varmevekslersystem, et varmevekslersystem og en fremgangsmåde til opvarmning af et fluid
EP3358287B1 (fr) 2015-09-30 2019-08-28 Mitsubishi Electric Corporation Échangeur de chaleur et dispositif à cycle de réfrigération doté de ce dernier
WO2017066717A2 (fr) * 2015-10-14 2017-04-20 Mark Miles Échangeur de chaleur à convection induite
DE102015225684A1 (de) * 2015-12-17 2017-06-22 Mahle International Gmbh Wärmeübertrager und Adapterstück
JP2017116152A (ja) * 2015-12-22 2017-06-29 サンデンホールディングス株式会社 熱交換器
JP2017125633A (ja) * 2016-01-12 2017-07-20 住友精密工業株式会社 熱交換器
JP6615316B2 (ja) * 2016-03-16 2019-12-04 三菱電機株式会社 フィンレス型の熱交換器、そのフィンレス型の熱交換器を備えた空気調和機の室外機、及びそのフィンレス型の熱交換器を備えた空気調和機の室内機
EP3926258B1 (fr) * 2016-10-26 2022-09-14 Mitsubishi Electric Corporation Distributeur et échangeur de chaleur
US10563895B2 (en) * 2016-12-07 2020-02-18 Johnson Controls Technology Company Adjustable inlet header for heat exchanger of an HVAC system
CN106765211B (zh) * 2016-12-07 2024-01-09 洛阳明远石化技术有限公司 催化裂化烟气处理装置
CN106855367B (zh) * 2017-02-28 2024-01-26 郑州大学 具有分布性出入口的管壳式换热器
CN106679467B (zh) * 2017-02-28 2019-04-05 郑州大学 具有外接管箱的管壳式换热器
WO2019152506A1 (fr) * 2018-01-31 2019-08-08 The Penn State Research Foundation Enveloppe monocoque et échangeur de chaleur tubulaire
US11022382B2 (en) 2018-03-08 2021-06-01 Johnson Controls Technology Company System and method for heat exchanger of an HVAC and R system
US11047625B2 (en) * 2018-05-30 2021-06-29 Johnson Controls Technology Company Interlaced heat exchanger
CN112567178B (zh) * 2018-08-23 2022-04-08 三菱电机株式会社 热交换器单元及制冷循环装置
US11536496B2 (en) * 2018-10-29 2022-12-27 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus
EP3922941A4 (fr) * 2019-02-04 2022-02-16 Mitsubishi Electric Corporation Échangeur de chaleur et conditionneur d'air équipé de celui-ci
US11098962B2 (en) * 2019-02-22 2021-08-24 Forum Us, Inc. Finless heat exchanger apparatus and methods

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7427716U (de) * 1974-11-21 Wieland Werke Ag Vorrichtung zur Verteilung von Flüssigkeits-Dampfgemischen bei Einspritzverdampfern
US2297633A (en) * 1940-02-26 1942-09-29 Nash Kelvinator Corp Refrigerating apparatus
US2591109A (en) * 1948-07-15 1952-04-01 Bohn Aluminium & Brass Corp Refrigerant evaporator
US3920069A (en) * 1974-03-28 1975-11-18 Modine Mfg Co Heat exchanger
US4088182A (en) * 1974-05-29 1978-05-09 The United States Of America As Represented By The United States Department Of Energy Temperature control system for a J-module heat exchanger
US4201263A (en) * 1978-09-19 1980-05-06 Anderson James H Refrigerant evaporator
US4497363A (en) * 1982-04-28 1985-02-05 Heronemus William E Plate-pin panel heat exchanger and panel components therefor
JPS59122803A (ja) * 1982-12-27 1984-07-16 株式会社東芝 蒸気タ−ビンの再熱装置
US4724904A (en) * 1984-11-23 1988-02-16 Westinghouse Electric Corp. Nuclear steam generator tube orifice for primary temperature reduction
US4580414A (en) * 1985-08-15 1986-04-08 Engelhard Friedrick R Refrigeration system
US4998580A (en) * 1985-10-02 1991-03-12 Modine Manufacturing Company Condenser with small hydraulic diameter flow path
US4688311A (en) * 1986-03-03 1987-08-25 Modine Manufacturing Company Method of making a heat exchanger
US4709689A (en) * 1986-12-02 1987-12-01 Environmental Resources, Inc. Solar heat exchange system
US5046555A (en) * 1990-09-06 1991-09-10 General Motors Corporation Extended surface tube-to-header connection for condenser
CA2092935A1 (fr) * 1992-09-03 1994-03-04 Gregory G. Hughes Echangeur de chaleur haute pression, longue duree, en aluminium
US5415223A (en) * 1993-08-02 1995-05-16 Calsonic International, Inc. Evaporator with an interchangeable baffling system
JPH0755386A (ja) * 1993-08-18 1995-03-03 Sanden Corp 熱交換器
DE4439801C2 (de) * 1994-11-08 1996-10-31 Gea Power Cooling Systems Inc Luftbeaufschlagter Trockenkühler
IT1276990B1 (it) * 1995-10-24 1997-11-03 Tetra Laval Holdings & Finance Scambiatore di calore a piastre
US5632239A (en) * 1996-04-16 1997-05-27 Chrysler Corporation Method of distributing air in an engine intake manifold
US5826649A (en) * 1997-01-24 1998-10-27 Modine Manufacturing Co. Evaporator, condenser for a heat pump
US5967228A (en) * 1997-06-05 1999-10-19 American Standard Inc. Heat exchanger having microchannel tubing and spine fin heat transfer surface
US5842351A (en) * 1997-10-24 1998-12-01 American Standard Inc. Mixing device for improved distribution of refrigerant to evaporator
US5941303A (en) * 1997-11-04 1999-08-24 Thermal Components Extruded manifold with multiple passages and cross-counterflow heat exchanger incorporating same
US6216776B1 (en) * 1998-02-16 2001-04-17 Denso Corporation Heat exchanger
JP4026277B2 (ja) * 1999-05-25 2007-12-26 株式会社デンソー 熱交換器
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
KR100382523B1 (ko) * 2000-12-01 2003-05-09 엘지전자 주식회사 마이크로 멀티채널 열교환기의 튜브 구조
US6688137B1 (en) * 2002-10-23 2004-02-10 Carrier Corporation Plate heat exchanger with a two-phase flow distributor
CN100398969C (zh) * 2003-10-30 2008-07-02 乐金电子(天津)电器有限公司 超细管道热交换器

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11713931B2 (en) 2019-05-02 2023-08-01 Carrier Corporation Multichannel evaporator distributor

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EP1844288A4 (fr) 2010-07-21
BRPI0519933A2 (pt) 2009-08-18
ATE529717T1 (de) 2011-11-15
WO2006083449A2 (fr) 2006-08-10
HK1118331A1 (en) 2009-02-06
CA2596573A1 (fr) 2006-08-10
AU2005326654B2 (en) 2010-08-12
CN101120225B (zh) 2010-12-15
MX2007009245A (es) 2007-08-23
WO2006083449A3 (fr) 2007-03-22
JP2008528943A (ja) 2008-07-31
AU2005326654A1 (en) 2006-08-10
EP1844288A2 (fr) 2007-10-17
ES2373964T3 (es) 2012-02-10
US20080092587A1 (en) 2008-04-24
CN101120225A (zh) 2008-02-06
KR20070091201A (ko) 2007-09-07

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