WO2013184522A1 - Échangeur de chaleur, et procédé de distribution de réfrigérant à l'intérieur de celui-ci - Google Patents

Échangeur de chaleur, et procédé de distribution de réfrigérant à l'intérieur de celui-ci Download PDF

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Publication number
WO2013184522A1
WO2013184522A1 PCT/US2013/043742 US2013043742W WO2013184522A1 WO 2013184522 A1 WO2013184522 A1 WO 2013184522A1 US 2013043742 W US2013043742 W US 2013043742W WO 2013184522 A1 WO2013184522 A1 WO 2013184522A1
Authority
WO
WIPO (PCT)
Prior art keywords
header
heat exchanger
flow
inlet
distributor tube
Prior art date
Application number
PCT/US2013/043742
Other languages
English (en)
Inventor
Mark W. Johnson
Original Assignee
Modine Manufacturing Company
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 Modine Manufacturing Company filed Critical Modine Manufacturing Company
Publication of WO2013184522A1 publication Critical patent/WO2013184522A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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

Definitions

  • the present application relates to heat exchangers.
  • Vapor compression systems are commonly used for refrigeration and/or air conditioning and/or heating, among other uses.
  • a refrigerant sometimes referred to as a working fluid
  • a continuous thermodynamic cycle in order to transfer heat energy to or from a temperature and/or humidity controlled environment and from or to an uncontrolled ambient environment.
  • vapor compression systems can vary in their implementation, they most often include at least one heat exchanger operating as an evaporator, and at least one other heat exchanger operating as a condenser.
  • a refrigerant typically enters an evaporator at a thermodynamic state (i.e., a pressure and enthalpy condition) in which it is a subcooled liquid or a partially vaporized two-phase fluid of relatively low vapor quality.
  • Thermal energy is directed into the refrigerant as it travels through the evaporator, so that the refrigerant exits the evaporator as either a partially vaporized two- phase fluid of relatively high vapor quality or a superheated vapor.
  • the refrigerant enters a condenser as a superheated vapor, typically at a higher pressure than the operating pressure of the evaporator. Thermal energy is rejected from the refrigerant as it travels through the condenser, so that the refrigerant exits the condenser in an at least partially condensed condition. Most often the refrigerant exits the condenser as a fully condensed, sub- cooled liquid.
  • Some vapor compression systems are reversing heat pump systems, capable of operating in either an air conditioning mode (such as when the temperature of the uncontrolled ambient environment is greater than the desired temperature of the controlled environment) or a heat pump mode (such as when the temperature of the uncontrolled ambient environment is less than the desired temperature of the controlled environment).
  • Such a system may require heat exchangers that are capable of operating as an evaporator in one mode and as a condenser in an other mode.
  • PF parallel flow
  • Such a heat exchanger can be characterized by having multiple, parallel arranged channels, especially micro-channels, for conducting the refrigerant through the heat transfer region from an inlet manifold to an outlet manifold.
  • PF parallel flow
  • Some embodiments of the invention provide a method for distributing refrigerant in a heat exchanger.
  • a flow of refrigerant is delivered to a fluid inlet and is directed through a distribution tube located within an inlet header, in a direction parallel to an axis of the header.
  • a first portion of the flow is diverted from the distributor tube to the internal volume of the header in a direction transverse to the axis.
  • a second portion is directed from an end of the distributor tube to the internal volume of the header in a direction parallel to the axis.
  • the refrigerant is directed from the internal volume of the header to tube ends received within the inlet header.
  • the second portion of the flow is directed through a flow constriction.
  • a third portion of the flow is diverted from the distributor tube to the internal volume of the header in a direction transverse to the axis.
  • the first and third portions are diverted through first and second flow orifices.
  • the first and second flow orifices are located in a common plane normal to the axis, while in other such embodiments the first orifice is located upstream of the second orifice with respect to the refrigerant flow.
  • a subset of the tube ends is located between the inlet and the end of the distributor tube. In some such embodiments that subset of tube ends is no more than half of the tube ends.
  • the refrigerant is collected in an outlet header of the heat exchanger, and is removed through a fluid outlet adjacent to the fluid inlet.
  • Some other embodiments of the invention provide a heat exchanger having a header extending in a longitudinal direction, slots arranged along the longitudinal direction, and tube ends received in the slots.
  • An inlet is arranged to allow fluid to flow into the heat exchanger.
  • a distributor tube is at least partly within the header, is connected to the inlet, and extends from an end of the header to a terminating location.
  • a first subset of the slots is located between the end of the header and the terminating location, and a second subset of the slots is located between the opposite end of the header and the terminating location.
  • the distributor tube is circular, and in some embodiments
  • the distributor tube includes at least one outlet orifice for fluid flow between the inlet and the terminating location.
  • the outlet orifice at the terminating location is greater in diameter than the outlet orifice(s) between the inlet and the terminating location, and in some specific embodiments it is between three and four times greater.
  • FIG. 1 is a perspective view of a heat exchanger according to an embodiment of the invention.
  • FIG. 2 is a partial plan view of the heat exchanger of FIG. 1.
  • FIG. 3 is a partial section plan view along the lines III-III in FIG. 2.
  • FIG. 4 is a perspective view of selected parts of the heat exchanger of FIG. 1.
  • FIG. 5 is a partial perspective view of a fin and tube combination for use in the heat exchanger of FIG. 1.
  • FIGs. 6A-C are diagrams of thermal imaging data obtained by testing various heat exchangers according to embodiments of the invention.
  • FIGs. 1-5 illustrate an exemplary embodiment of a heat exchanger 1 according to the present invention.
  • a heat exchanger 1 may be used as an evaporator in a vapor compression based climate control system.
  • such a heat exchanger 1 may be used as a condenser in a vapor compression based climate control system.
  • such a heat exchanger 1 may operate both as a condenser in a first mode of operation, and as an evaporator in a second mode of operation.
  • the heat exchanger 1 may find utility in other types of systems such as, for example, a Rankine cycle power generation system.
  • the heat exchanger 1 includes a first flow pass comprising a plurality of parallel arranged tubes 10a, and a second flow pass comprising a plurality of parallel arranged tubes 10b.
  • the tubes 10a of the first flow pass extend from a first tubular header 2 at a first end of the heat exchanger 1 to an intermediate header structure 7 at a second end opposite the first end.
  • the tubes 10b extend from the intermediate header structure 7 to a second tubular header 3 at the first end of the heat exchanger 1.
  • a first fluid port 4 at the first tubular header 2 and a second fluid port 5 at the second tubular header 3 provide means for connecting the heat exchanger 1 into a vapor compression or similar system by, for example, connecting the fluid ports 4,5 to refrigerant plumbing 18 (FIG. 3).
  • the first and second flow passes are sequential to one another so that a fluid (for example, a refrigerant) may be directed to flow into the heat exchanger 1 by way of the fluid inlet port 4, flow through the tubes 10a of the first flow pass from the tubular inlet header 2 to the intermediate header structure 7, flow through the tubes 10b of the second flow pass from the intermediate header structure 7 to the tubular outlet header 3, and flow out of the heat exchanger 1 by way of the fluid outlet port 5.
  • a fluid for example, a refrigerant
  • the fluid might similarly enter the heat exchanger 1 by way of the port 5 and exit the heat exchanger 1 by way of the port 4, so that the flow through the heat exchanger 1 is reversed and the fluid encounters the flow passes in an order that is the reverse of the above.
  • Fins 11 are arranged between adjacent ones of the tubes 10. Although the exemplary fins 11 are of a serpentine convoluted type, any type of fins regularly used and known in the art can be similarly employed. The fins 11 can be used to provide surface area enhancement and/or flow turbulation in order to improve the rate of heat transfer between the fluid passing through the tubes 10 and another fluid, such as for example air, passing over the outer surfaces of the tubes 10. The fins 11 can alternatively, or in addition, provide beneficial spacing and/or structural support to the tubes 10.
  • the fins 11 can be of sufficient depth to be common to both a tube 10a in the first flow pass and a tube 10b in the second flow pass. In other embodiments, the fins 11 can have a depth that is only sufficient for a single tube 10, so that separate fins 11 are used for the tubes 10a and the tubes 10b.
  • the fins 11 are optional, however, and need not be present at all in a heat exchanger 1 embodying the present invention.
  • the tubes 10 of the exemplary embodiment include two opposing broad flat sides joined by two opposing narrow sides.
  • Internal webs 15 can be provided inside the tubes 10 in order to divide the internal space of the tube 10 into a plurality of internal flow channels 14.
  • the webs 15 can provide heat transfer
  • Such structural support can be especially beneficial in vapor compression systems, wherein the fluid passing through the tubes 10 may be at an operating pressure that is substantially elevated in comparison to the pressure external to the tubes 10.
  • the internal flow channels 14 are open to receive or deliver fluid flow at tube ends 16 located at opposite ends of each tube 10.
  • FIG. 1 includes a flat intermediate header 7 arranged at an end opposing the tubular headers 2, 3. Fluid flow traveling through the first plurality of tubes 10a can be received within flow passages contained in the intermediate header 7, and can be transferred to the second plurality of tubes 10b, or vice versa.
  • An exemplary embodiment of such an intermediate header 7 is described in currently pending US patent application no. 13/076,607 to Mross et al., filed on March 31, 2011, the entire contents of which are incorporated by reference herein. It should be understood, however, that the intermediate header 7 can alternatively be of other constructions, and in some embodiments the intermediate header 7 can be eliminated altogether.
  • the tubular headers 2, 3 are each provided with a plurality of slots 17 arranged along their longitudinal lengths, in one-to-one correspondence with the tubes 10.
  • the tube ends 16 are sealingly received within the slots 17 in order to enable the flow of fluid between the internal volumes of the tubular headers 2, 3 and the internal flow channels 14 of the tubes 10. Slots can be similarly provided in the intermediate header 7 for the same purpose.
  • a fluid distributor tube 9 is connected to the fluid port 4 and penetrates through the cap 8 in order to deliver a flow of fluid received at the inlet port 4 to the internal volume of the tubular header 2 and, subsequently, to the tubes 10.
  • the distributor tube 9 can be formed integral with the fluid port 4, as in the exemplary embodiment, or it can be a separate component that is joined thereto.
  • the distributor tube 9 extends in a longitudinal direction parallel to the axis 19 of the tubular header 2, from the end of the tubular header 2 proximate the fluid port 4 to a terminating location partway along the length of the tubular header 2. In doing so, the distributor tube 9 extends past at least several of the slots 17. In the exemplary embodiment of FIG. 3 the distributor tube 9 extends past the first seven of the slots 17.
  • the slots 17 arranged along the longitudinal length of the tubular header 2 thereby comprise a first subset of the slots 17 located between the end of the tubular header 2 proximate the fluid port 4 and the terminating location, and a second subset of the slots 17 located between the terminating location and the opposing end of the tubular header 2. In preferable embodiments the first subset of the slots 17 includes no more than half of the slots 17 in the tubular header 2.
  • the distributor tube 9 is provided with a plurality of orifices 12 arranged along the cylindrical wall of the distributor tube 9. In the exemplary embodiment four such orifices are shown, but more or fewer orifices 12 may be provided in other embodiments. Additionally, an orifice 13 is provided at the terminating location of the distributor tube 9.
  • the number of orifices 12, the locations of the orifices 12 along the distributor tube 9, and the relative sizes of the orifice 13 and the orifices 12 can be adjusted in order to optimize the uniformity of flow distribution among the tubes 10.
  • multiple orifices 12 are located in a common plane normal to the axis 19.
  • one or more first orifices 12 are located upstream of one or more second orifices 12.
  • the orifice 13 provides a flow constriction.
  • the diameter of the orifice 13 is three to four times larger than the diameter of the orifices 12.
  • a distributor tube 9 can be especially beneficial when the outlet port 5 is located at an end of the tubular header 3, as in the embodiment of FIG. 1.
  • liquid or two-phase (liquid and vapor) refrigerant is vaporized and superheated as it travels through the tubes 10, by receiving heat from air passing over the outer surfaces of the tubes 10.
  • the superheated vapor is discharged from the tubes 10 into the internal volume of the tubular header 3 and is removed from the heat exchanger by way of the fluid port 5.
  • the location of the fluid port 5 can have a substantial impact on the uniformity of refrigerant distribution among the tubes 10b.
  • FIG. 6A shows the location of the superheat front in the second pass of an evaporator 20, as evidenced by infrared thermal imaging of the evaporator during performance testing.
  • the evaporator 20 is similar in construction to the heat exchanger 1 , except that the outlet fluid port 5 is located at the center (in the longitudinal direction) of the tubular header 2, and the distribution tube used in the inlet tubular header (not shown) is of a typical construction, extending the full length of the inlet tubular header and having orifices along the cylindrical wall only.
  • the refrigerant flows from the intermediate header 7 to the tubular header 3 through a plurality of tubes (not shown). As the refrigerant flows through the tubes, heat is transferred from air passing over the tubes to the refrigerant, vaporizing the refrigerant and, eventually, superheating the vapor once the entire amount of refrigerant in a given tube has been vaporized. As vaporization is an isothermal process, the thermal imaging can be used to plot out the region 18 wherein the refrigerant is in a superheated state.
  • the latent heat capacity of the refrigerant in each tube is directly related to the mass flow of refrigerant in each tube, and consequently, the uniformity of refrigerant flow distribution between the tubes can be inferred from the shape of the superheat region 18.
  • the refrigerant appears to be fairly uniformly distributed among the tubes, with the exception of the outermost tubes at each side of the evaporator 18.
  • FIG. 6B the thermal image of an evaporator 20' during thermal performance testing is shown.
  • the evaporator 20' is identical to the evaporator 20, except that the outlet port 5 has been relocated to the end of the tubular header 3 adjacent to the refrigerant inlet (not shown).
  • a large superheated region extends the full length of the flow pass in more than half of the tubes, indicating that a significant number of the tubes (more than half) are starved of refrigerant.
  • a relatively small number of tubes have refrigerant flow that is sufficient to provide vaporizing heat transfer over a substantial length of the tubes in the second pass.
  • FIG. 6C shows the thermal image of an evaporator 20" during thermal performance testing, where the evaporator 20" is similar to the evaporator 20' except that it includes the distributor tube 9 as shown in the embodiments of FIGs. 3 and 4.
  • the flow of refrigerant is overall much better distributed than in evaporator 20' . While not wishing to be bound by theory, it is believed that a substantial portion of the refrigerant flowing through the distributor tube 9 is directed as a submerged jet from the orifice 13 down the length of the tubular header 2 in order to feed refrigerant to those tubes located at the left side (as viewed in FIG. 6C) of the evaporator 20". It is further believed that the orifices 12 arranged along the cylindrical wall of the distributor tube 9 allow for some of the refrigerant to exit the distributor tube 9 through those orifices 12, thereby creating a turbulent region near the first few tubes.
  • the heat transfer capacities of the evaporators 20' and 20" were evaluated through testing at various air flow rates. This testing showed that the evaporator 20" had a heat transfer capacity that was 8-10% greater than the heat transfer capacity of the evaporator 20' over the range of air flow rates. In addition, the evaporator 20" showed improved system stability (decreased set-point hunting by the thermal expansion valve) and more uniform conditioning of the entire air stream.

Abstract

L'invention concerne un échangeur de chaleur possédant une en-tête qui s'étend dans une direction longitudinale, des fentes disposées le long de la direction longitudinale, et des extrémités de tube reçues dans les fentes. Une entrée est agencée pour permettre au fluide de s'écouler dans l'échangeur de chaleur. Un tube de distribution se trouve au moins partiellement à l'intérieur de l'en-tête, est relié à l'entrée, et s'étend à partir d'une extrémité de l'en-tête vers un emplacement final. Un premier sous-ensemble de fentes est situé entre l'extrémité de l'en-tête et l'emplacement final, et un second sous-ensemble des fentes est situé entre l'extrémité opposée de l'en-tête et l'emplacement final. Le flux peut être dirigé du tube de distributeur dans l'en-tête à travers un orifice de l'emplacement final, et/ou à travers des orifices le long du tube de distribution.
PCT/US2013/043742 2012-06-08 2013-05-31 Échangeur de chaleur, et procédé de distribution de réfrigérant à l'intérieur de celui-ci WO2013184522A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201261657354P 2012-06-08 2012-06-08
US61/657,354 2012-06-08

Publications (1)

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WO2013184522A1 true WO2013184522A1 (fr) 2013-12-12

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3423764A4 (fr) * 2016-03-04 2020-02-26 Modine Manufacturing Company Système de chauffage et de refroidissement et échangeur de chaleur associé
CN113970258A (zh) * 2020-07-22 2022-01-25 丹佛斯有限公司 换热器
WO2022017117A1 (fr) * 2020-07-22 2022-01-27 丹佛斯有限公司 Échangeur de chaleur
WO2024041594A1 (fr) * 2022-08-25 2024-02-29 浙江盾安人工环境股份有限公司 Échangeur de chaleur et dispositif de climatisation

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5465783A (en) * 1994-03-04 1995-11-14 Fedco Automotive Components Company, Inc. Sacrificial erosion bridge for a heat exchanger
US20110030934A1 (en) * 2008-06-10 2011-02-10 Carrier Corporation Integrated Flow Separator and Pump-Down Volume Device for Use in a Heat Exchanger
US20110139422A1 (en) * 2009-12-15 2011-06-16 Delphi Technologies, Inc. Fluid distribution device
US20110203308A1 (en) * 2008-01-17 2011-08-25 Robert Hong-Leung Chiang Heat exchanger including multiple tube distributor
US20110240271A1 (en) * 2010-03-31 2011-10-06 Greg Mross Heat exchanger
US20110290465A1 (en) * 2010-06-01 2011-12-01 Delphi Technologies, Inc. Orientation insensitive refrigerant distributor tube

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5465783A (en) * 1994-03-04 1995-11-14 Fedco Automotive Components Company, Inc. Sacrificial erosion bridge for a heat exchanger
US20110203308A1 (en) * 2008-01-17 2011-08-25 Robert Hong-Leung Chiang Heat exchanger including multiple tube distributor
US20110030934A1 (en) * 2008-06-10 2011-02-10 Carrier Corporation Integrated Flow Separator and Pump-Down Volume Device for Use in a Heat Exchanger
US20110139422A1 (en) * 2009-12-15 2011-06-16 Delphi Technologies, Inc. Fluid distribution device
US20110240271A1 (en) * 2010-03-31 2011-10-06 Greg Mross Heat exchanger
US20110290465A1 (en) * 2010-06-01 2011-12-01 Delphi Technologies, Inc. Orientation insensitive refrigerant distributor tube

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3423764A4 (fr) * 2016-03-04 2020-02-26 Modine Manufacturing Company Système de chauffage et de refroidissement et échangeur de chaleur associé
US10907865B2 (en) 2016-03-04 2021-02-02 Modine Manufacturing Company Heating and cooling system, and heat exchanger for the same
CN113970258A (zh) * 2020-07-22 2022-01-25 丹佛斯有限公司 换热器
WO2022017117A1 (fr) * 2020-07-22 2022-01-27 丹佛斯有限公司 Échangeur de chaleur
WO2024041594A1 (fr) * 2022-08-25 2024-02-29 浙江盾安人工环境股份有限公司 Échangeur de chaleur et dispositif de climatisation

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