WO2020123653A1 - Condenseur de fluide frigorigène - Google Patents

Condenseur de fluide frigorigène Download PDF

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Publication number
WO2020123653A1
WO2020123653A1 PCT/US2019/065729 US2019065729W WO2020123653A1 WO 2020123653 A1 WO2020123653 A1 WO 2020123653A1 US 2019065729 W US2019065729 W US 2019065729W WO 2020123653 A1 WO2020123653 A1 WO 2020123653A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
flat tube
tube sections
fluid manifold
header pipe
Prior art date
Application number
PCT/US2019/065729
Other languages
English (en)
Inventor
Mark 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 WO2020123653A1 publication Critical patent/WO2020123653A1/fr

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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
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers

Definitions

  • the present application relates to heat exchangers for use in refrigerant systems, including refrigerant evaporators and condensers, and relates particularly to such heat exchangers as used in vapor compression systems.
  • Vapor compression systems are commonly used for refrigeration and/or air conditioning, among other uses.
  • a refrigerant is circulated through 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. While such 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 the 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 a superheated vapor.
  • a thermodynamic state i.e., a pressure and enthalpy condition
  • the superheated vapor refrigerant is compressed to a high pressure and, at another point in the system, enters the condenser. 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 preferably the refrigerant exits the condenser as a fully condensed, subcooled liquid. The liquid refrigerant is subsequently expanded to the lower pressure thermodynamic state at which it enters the evaporator.
  • a variety of refrigerants can be used within such a vapor compression system, including chlorofluorocarbons, hydrochlorofluorocarbons,
  • hydrofluorocarbons hydrocarbons, organic refrigerants, and others. While chlorofluorocarbons such as R12 and hydrochlorofluorocarbons such as R22 were once popular refrigerants, their use has been restricted due to their ozone depletion effects on the earth’s atmosphere. In their stead, hydrofluorocarbons (which are not ozone-depleting) became more prevalent. In recent years, however, the use of such refrigerants has also been restricted by legislation and regulation due to their high global warming potential. Improvements in vapor compression systems and components that were previously optimized for such refrigerants have become necessary in order to achieve optimum performance with the use of newer low global warming potential refrigerants.
  • Low global warming potential refrigerants are often formulated as a zeotropic mixture of several refrigerant components that are themselves azeotropic. During evaporation and condensation of such a refrigerant, the various constituent refrigerants will vaporize or condense at different rates, resulting in a non-constant evaporation or condensation temperature at a constant pressure.
  • the temperature glide is referred to as the change in saturation temperature, at constant pressure, as the refrigerant varies between fully vapor and fully liquid.
  • a typical temperature glide within a condenser for a low global warming potential refrigerant can be more than ten degrees Fahrenheit, with the liquid saturation temperature at the condensing pressure being that amount lower than the vapor saturation temperature at that pressure. This temperature glide tends to make the condenser less efficient, as the reduced temperature of the liquid condensate makes the further removal of heat from the refrigerant more challenging.
  • a refrigerant condenser includes flat tube sections arranged into a first row and a parallel second row, with a one-to-one correspondence between the flat tube sections of the first row and the flat tube sections of the second row.
  • Each one of the flat tube sections of the second row is hydraulically connected to the corresponding flat tube section of the first row at one end of the refrigerant condenser.
  • At the opposing end of the refrigerant condenser are two cylindrical header pipes. Ends of the flat tube sections of the first row are received into one cylindrical header pipe, and ends of the flat tube sections of the second row are received into the other cylindrical header pipe.
  • Four fluid manifolds are arranged within the two header pipes, with ends of the flat tube sections extending into the fluid manifolds.
  • a connecting tube extends between a fluid manifold in one cylindrical header pipe and a fluid manifold in the other cylindrical header pipe.
  • each cylindrical header pipe contains two fluid manifolds.
  • a first subset of the flat tube sections of the first row extend into the first fluid manifold and a second subset of the flat tube sections of the first row extend into the second fluid manifold.
  • a first subset of the flat tube sections of the second row extend into the third fluid manifold and a second subset of the flat tube sections of the second row extend into the fourth fluid manifold.
  • the first subset of the second row corresponds to the first subset of the first row
  • the second subset of the second row corresponds to the seconds subset of the first row.
  • the connecting tube extends between the second fluid manifold and the third fluid manifold.
  • the first subset of the flat tube sections of the first row defines a first refrigerant pass through the refrigerant condenser
  • the first subset of the flat tube sections of the second row defines a second refrigerant pass
  • the second subset of the flat tube sections of the first row defines a third refrigerant pass
  • the second subset of the flat tube sections of the second row defines a fourth refrigerant pass through the condenser.
  • Refrigerant flows sequentially through the first, second, third, and fourth passes.
  • the refrigerant condenser includes a condenser section and a subcooler section.
  • Some embodiments include a refrigerant inlet that is connected to the first fluid manifold, and a refrigerant outlet that is connected to the fourth fluid manifold.
  • a return header is arranged the end of the refrigerant condenser opposite the cylindrical header pipes.
  • the return header fluidly connects corresponding ones of the first and second rows of flat tube sections.
  • each of the corresponding flat tube sections is part of a single flat tube that has been bent and/or twisted to define the two parallel flat sections.
  • each flat tube section of the first row is hydraulically connected to exactly one flat tube section of the second row at the end opposite the cylindrical header pipes.
  • the first and the second fluid manifolds are separated from each other by a baffle that is arranged within one cylindrical header pipe, and the third and the fourth fluid manifolds are separated from each other by a baffle that is arranged within the other cylindrical header pipe.
  • the connecting tube has a first end that extends through the cylindrical wall of one header pipe and a second end that extends through the cylindrical wall of the other header pipe. In some other embodiments at least one of the ends extends through an end cap of one of the cylindrical header pipes.
  • one or both ends of the connecting tube are defined by a fitting that is part of the connecting tube.
  • a refrigerant condenser includes a first and a second cylindrical header pipe.
  • the first and second cylindrical header pipes are arranged at a common end of the condenser.
  • a first flow baffle is arranged within the first cylindrical header pipe to separate an internal volume of the first cylindrical header pipe into a first fluid manifold and a second fluid manifold.
  • a second flow baffle is arranged within the second cylindrical header pipe to separate an internal volume of the second cylindrical header pipe into a third fluid manifold and a fourth fluid manifold.
  • the third fluid manifold is arranged adjacent to the first fluid manifold, and the fourth fluid manifold is arranged adjacent to the second fluid manifold.
  • the refrigerant condenser can include a first set of refrigerant conduits that provide a refrigerant flow path between the first fluid manifold and the third fluid manifold, and a second set of refrigerant conduits that provide a refrigerant flow path between the second fluid manifold and the fourth fluid manifold.
  • each one of the first and second sets of refrigerant conduits includes a first flat tube section with an end that is sealingly received into the first cylindrical header pipe, and a second flat tube section with an end that is sealingly received into the second cylindrical header pipe.
  • the refrigerant condenser can also include a refrigerant inlet port connected to the first cylindrical header pipe and in direct fluid communication with the first fluid manifold, and a refrigerant outlet port connected to the second cylindrical header pipe and in direct fluid communication with the fourth fluid manifold.
  • Refrigerant can enter the condenser through the refrigerant inlet port, and can exit the condenser through the refrigerant outlet port. Between the refrigerant inlet port and the refrigerant outlet port, the refrigerant can be directed to flow through the first and second sets of refrigerant conduits.
  • the refrigerant condenser can also include a connecting tube that connects the first and second cylindrical headers and that forms part of the refrigerant flow path between the inlet port and the outlet port.
  • a first end of the connecting tube can be joined to the first cylindrical header pipe and can be in direct fluid communication with the second fluid manifold.
  • a second end of the connecting tube can be joined to the second cylindrical header piper and can be in direct fluid communication with the third fluid manifold.
  • the first end of the connecting tube is arranged adjacent to the first baffle. In some embodiments, the second end of the connecting tube is arranged adjacent to the second baffle. In some embodiments, the first end of the connecting tube is arranged adjacent to the first baffle and the second end of the connecting tube is arranged adjacent to the second baffle.
  • Each of the first and second sets of refrigerant conduits can include a first flat tube section with an end that is sealingly received into the first cylindrical header pipe and a second flat tube section with an end that is sealingly received into the second cylindrical header pipe.
  • the refrigerant condenser can have a return header arranged at an end of the refrigerant condenser opposite the first and second cylindrical header pipes. Ends of the first and second flat tube sections of each of the refrigerant conduits can be sealingly received into the return header.
  • the return header can provide a fluid connection between the first and second flat tube sections of each refrigerant conduit.
  • the first and second cylindrical header pipes can be arranged vertically when the refrigerant condenser is in an operating condition.
  • the arrangement can be such that the second and the fourth fluid manifolds are arranged below the first and the third fluid manifolds.
  • FIG. 1 is a perspective view of a refrigerant condenser according to some embodiments of the invention.
  • FIG. 2 is a planar section view through the refrigerant condenser of FIG. 1, depicting the flow of fluids through the refrigerant condenser.
  • FIG. 3 is a portion of FIG. 1 shown in greater detail.
  • FIG. 4 is a partial exploded view of select components of the refrigerant condenser of FIG. 1.
  • FIG. 5 is another planar section view through the refrigerant condenser of FIG. 1.
  • a refrigerant condenser 1 for use in a vapor-compression refrigeration system is depicted in FIG. 1.
  • a vapor-compression refrigeration system can be used for comfort cooling applications, as one non-limiting example.
  • the refrigerant condenser 1 can be particularly well-suited for such an application, wherein the refrigerant is compressed from a low-pressure vapor to a high-pressure vapor and is subsequently cooled and condensed to a sub-cooled liquid state within the refrigerant condenser 1.
  • such a condenser may be equally useful, such as for example freezing, refrigeration, process cooling, etc., the same principle can be used.
  • refrigerant condenser 1 Various types of refrigerants can be suitable for use in a refrigeration system employing the refrigerant condenser 1, including but not limited to chlorofluorocarbons, hydrofluorocarbons, hydrocarbons, organic refrigerants, etc.
  • the refrigerant condenser 1 is especially suitable for use with refrigerants that exhibit a high glide behavior. Unlike azeotropic refrigerants, which have a single saturation temperature for any given pressure value, a high glide refrigerant will have a saturation temperature that varies as the refrigerant transitions from fully vapor to fully liquid, or vice-versa, even when the pressure value is held constant.
  • That variance in saturation temperature is commonly referred to as the “temperature glide” of the refrigerant.
  • Refrigerants with a high glide behavior i.e. with a large variance in saturation temperature from being fully liquid to being fully vapor
  • the refrigerant condenser 1 is constructed using a core 2 of alternating tube sections 3 and serpentine air fins 4.
  • the tube sections 3 are provided by flat tubes with internal flow passages by way of which the refrigerant is conveyed through the condenser 1.
  • the air fins 4 are constructed from corrugated sheet material and are arranged between adjacent ones of the flat tube sections 3. Crests of the fins 4 are bonded to the flat surfaces of the tube sections 3 in order to efficiently transfer heat from the refrigerant passing through the tube sections 3 to a flow of cooling air that is directed through the air fins 4 in a direction generally perpendicular to the flow of refrigerant through the tube sections 3.
  • the tube sections 3 and air fins 4 are preferably constructed from aluminum alloys, and are joined together by a brazing operation.
  • the tube sections 3 are arranged to form two parallel rows 20, 21 of tube sections. Each of the two rows 20, 21 are defined by a like number of tube sections, so that tube sections 3 of the first row 20 are in one-to-one correspondence with tube sections 3 of the second row 21.
  • the flat tube sections 3 all extend from a first end 25 of the condenser 1 to a second opposing end 26. At the second end 26, each flat tube section of the row 20 is hydraulically connected to the corresponding flat tube section of the row 21.
  • each of the flat tube sections 3 of the second row 21 is serially connected with exactly one of the flat tube sections 3 of the first row 20, so that the refrigerant flowing through a given one of the flat tube sections of the first row 20 subsequently flow through the corresponding flat tube section of the second row 21.
  • both members of a pair of corresponding flat tube sections 3 can be provided by a single flat tube which is bent and/or twisted to define the two parallel arranged flat tube sections 3.
  • the flat surfaces of corresponding ones of the flat tube sections 3 are preferably arranged to be co-planar with one another, so that a single corrugated fin 4 can extend across, and be joined to, the flat tube sections of both rows 20, 21.
  • individual corrugated fin sections can be provided for each of the rows 20 and 21.
  • Two cylindrical header pipes 5 are arranged at the first end 25 of the condenser 1.
  • Each of the cylindrical header pipes 5 is provided with a series of tube slots 6 that are formed into the cylindrical wall surface of the header pipe 5. Ends of those ones of the flat tube sections 3 that make up the first row 20 are received into the tube slots 6 of a first one of the cylindrical header pipes 5a, while ends of those ones of the flat tube sections 3 that make up the second row 21 are received into the tube slots 6 of a second one of the cylindrical header pipes 5b.
  • the tube sections 3 are thereby placed in fluid communication with fluid manifolds 14 that are arranged within the cylindrical header pipes 5.
  • Each of the cylindrical header pipes 5 is further provided with a baffle 8 that is received into a baffle slot 7 formed into the cylindrical wall of the header pipe
  • the baffle slot 7 is preferably arranged between two adjacent ones of the tube slots
  • the baffle 8 is sealingly joined to the cylindrical header pipe 5 to divide the internal volume of the cylindrical header pipe 5 into two hydraulically separated fluid manifolds 14.
  • the baffles 8 of both of the cylindrical header pipes 5a, 5b are arranged at an equivalent location along the axial lengths of the header pipes 5.
  • a refrigerant inlet 9 is connected to cylindrical header pipe 5a, i.e. the cylindrical header pipe 5 that receives the ends of the flat tube sections 3 of the first row 20.
  • the refrigerant inlet 9 is arranged along the axial length of the cylindrical header pipe 5a at a location that is partway between the baffle 8 of the cylindrical header pipe 5a and a first one of the side plates 13.
  • a flow of compressed and superheated refrigerant is directed through the refrigerant inlet port 9 into a fluid manifold 14a within that cylindrical header pipe 5a, the fluid manifold 14a being that portion of the internal volume of the cylindrical header pipe 5 a between the baffle 8 and the end cap 11 adjacent that first one of the side plates 13.
  • a refrigerant outlet 10 is similarly connected to cylindrical header pipe 5b, i.e. the cylindrical header pipe 5 that receives the ends of the flat tube sections 3 of the second row 21.
  • the refrigerant outlet 10 is arranged along the axial length of the cylindrical header pipe 5b at a location that is partway between the baffle 8 of the cylindrical header pipe 5b and a second one of the side plates 13, that second one of the side plates 13 being the side plate 13 arranged at the opposite end, in the axial direction of the cylindrical header pipes 5, from the first one of the side plates 13.
  • the flow of refrigerant, having been condensed and subcooled to a liquid phase, is removed from a fluid manifold 14d by way of the refrigerant outlet 10, the fluid manifold 14d being that portion of the internal volume of the cylindrical header pipe 5b between the baffle 8 and the end cap 11 adjacent that second one of the side plates 13.
  • the remainder of the internal volume of the cylindrical header pipe 5a defines a fluid manifold 14c.
  • the remainder of the internal volume of the cylindrical header pipe 5b defines a fluid manifold 14b.
  • a connecting tube 17 is joined to both of the cylindrical header pipes 5 to provide a fluid connection between the fluid manifold 14b and the fluid manifold 14c.
  • the connecting tube includes an end fitting 18 arranged at one end of the connecting tube 17, and an end fitting 19 arranged at the opposite end of the connecting tube 17.
  • the connecting tube 17 is joined to the cylindrical header pipe 5b by way of the first end fitting 18, and is joined to the cylindrical header pipe 5a by way of the second end fitting 19.
  • both end fittings 18 and 19 may be arranged in close proximity to their respective cylindrical header pipe’s baffle 8, as depicted in FIGs. 1 and 3.
  • at least one of the end fittings 18, 19 may be arranged closer to an end cap 11 of the respective header pipe 5, or even to extend through one of the end caps 11.
  • the refrigerant condenser 1 includes a condenser section 15 and a subcooler section 16. During operation of the refrigerant condenser 1, the flow of refrigerant entering through the refrigerant inlet port 9 is first cooled and condensed to an at least partially liquid state within the condenser section 15. The liquid refrigerant is subsequently directed through the subcooler section 16 in order to be subcooled to a temperature that is below the saturation temperature of the refrigerant, and is removed as a subcooled liquid refrigerant through the refrigerant outlet port 10.
  • Each of the two sections 15, 16 include a pass 22 for the refrigerant and a pass 23 for the refrigerant, with the pass 23 being arranged downstream of the pass 22 with respect to the direction of refrigerant flow.
  • the pass 22 is defined by a portion of the flat tube sections 3 of the first row 20, while the pass 23 is defined by a portion of the flat tube sections 3 of the second row 21.
  • the direction of the cooling air flow through the refrigerant condenser is such that the air passes first over the tube sections of the second row 21 and subsequently over the tube sections of the first row 20, as indicated by the arrows 24.
  • the flow of refrigerant is in a cross-counter flow arrangement to the flow of air, leading to increased heat exchanger effectiveness.
  • the refrigerant is a high glide refrigerant, since the temperature of the refrigerant in the pass 23 will in such cases be lower than the temperature of the refrigerant in the pass 22. Since the flow of air will tend to increase in temperature as it passes through the refrigerant condenser 1, the heat exchanger effectiveness will be higher when the air that is to receive heat from the lower temperature refrigerant (i.e. the refrigerant in the pass 23) has not yet been heated by receiving thermal energy from the higher temperature refrigerant in the pass 22
  • a first pass of the refrigerant is defined by a first subset of the flat tube sections 3 of the first row 20, that subset being those flat tube sections of the first row 20 that communicate directly with the fluid manifold 14a.
  • a second pass of the refrigerant is defined by a first subset of the flat tube sections 3 of the second row 21, that subset being those flat tube sections of the second row 21 that communicate directly with the fluid manifold 14b.
  • the first subset of the tube sections of the second row 21 are those tube sections that correspond with the first subset of the tube sections of the first row 20.
  • the third pass of the refrigerant is defined by a second subset of the tube sections 3 of the first row 20 and the fourth pass of the refrigerant is defined by a second subset of the tube sections 3 of the second row 21.
  • the second subset of the first row 20 includes those tube sections that communicate directly with the fluid manifold 14c, and the second of the second row 20 includes those tube sections that communicate directly with the fluid manifold 14d.
  • the condensing section 15 is defined by the first subsets of the tube sections 3, and the subcooler section 16 is defined by the second subsets of the tube sections 3.
  • the first pass of refrigerant is a pass 22
  • the second pass of refrigerant is a pass 23
  • the third pass of refrigerant is again a pass 22
  • the fourth pass of refrigerant is again a pass 23.
  • the arrangement of refrigerant flow to air flow can be a cross-counter flow arrangement in both the condensing section 15 and the subcooler section 16.
  • the refrigerant By virtue of the refrigerant being at least partially condensed within the condensing section 15, the refrigerant enters the fluid manifold 14b in an at least partially liquid state. It is most preferable during operation for the refrigerant condenser 1 to be arranged such that the axial direction of the cylindrical header pipes 5 is generally aligned with the force of gravity (i.e. a vertical arrangement), with the fluid manifolds 14a, 14b arranged above the fluid manifolds 14c, 14d. In this way, when the refrigerant exiting the second pass has a vapor quality of between 0 and 1 (i.e.
  • the differing densities of the liquid and vapor phases will cause them to be separated from one another within the fluid manifold 14b, with the liquid portion occupying the bottom portion of the fluid manifold 14b and the vapor portion occupying the top portion of the fluid manifold 14b.
  • the saturated liquid refrigerant collecting at the bottom of the fluid manifold 14b is directed through the connecting tube 17 to the fluid manifold 14c. From there, the saturated liquid refrigerant flows through the passes 22 and 23 and is thereby cooled from a saturated liquid state to a subcooled liquid state by the flow of air passing through the subcooler section 16.
  • both the fittings 18 and 19 depicts both the fittings 18 and 19 as extending through a cylindrical wall of a header pipe 5, it may be preferable, in some alternative embodiments, to arrange the fitting 19 so that it extends through the bottom end cap 11 of the cylindrical header pipe 5 a, in order to provide more optimal flow distribution of the refrigerant in the third and fourth flow passes.
  • the refrigerant condenser 1 can be installed so that the cylindrical heaper pipes 5 are arranged vertically, as is shown in FIG. 5. With such an arrangement, the fluid manifold 14a is arranged above the fluid manifold 14c, and the fluid manifold 14b is arranged above the fluid manifold 14d.
  • the refrigerant passes firs through the condenser section 15 (located in the upper portion) and subsequently though the subcooler section 16 (located in the lower portion). As the refrigerant is transferred through the connecting tube 17, the direction of refrigerant travel is aligned with the gravitational direction.
  • the first end fitting 18 can be conveniently located adjacent to, and just above, the baffle 8 of the header pipe 5b. During operation, the liquid portion of the refrigerant exiting the first subsets of the tube sections 3 will collect by gravity in that region of the fluid manifold 14b that is immediately above the baffle 8. By locating the first end fitting 18 in that region, the refrigerant that is delivered to the subcooler section 16 by the connecting tube 17 will be mostly or completely liquid.

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

Abstract

Cette invention concerne un condenseur de fluide frigorigène qui assure une performance de sous-refroidissement améliorée pour des fluides frigorigènes zéotropes. Le condenseur comporte des sections de tube planes agencées en une première rangée et une seconde rangée, chacune des sections de tube planes de la seconde rangée étant reliée hydrauliquement à une section de tube plane correspondante de la première rangée. Les extrémités des sections de tube planes de la première rangée sont reçues dans premier un tuyau collecteur cylindrique, et les extrémités des sections de tube planes de la seconde rangée sont reçues dans un autre tuyau collecteur cylindrique. Quatre collecteurs de fluide sont disposés à l'intérieur des deux tuyaux collecteurs, les extrémités des sections de tube planes s'étendant dans les collecteurs de fluide. Un tube de raccordement s'étend entre un collecteur de fluide dans un premier tuyau collecteur cylindrique et un collecteur de fluide dans l'autre tuyau collecteur cylindrique.
PCT/US2019/065729 2018-12-14 2019-12-11 Condenseur de fluide frigorigène WO2020123653A1 (fr)

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US201862779598P 2018-12-14 2018-12-14
US62/779,598 2018-12-14

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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5348081A (en) * 1993-10-12 1994-09-20 General Motors Corporation High capacity automotive condenser
US5529116A (en) * 1989-08-23 1996-06-25 Showa Aluminum Corporation Duplex heat exchanger
US6189604B1 (en) * 1999-01-19 2001-02-20 Denso Corporation Heat exchanger for inside/outside air two-passage unit
EP1643202A1 (fr) * 2004-10-04 2006-04-05 Behr GmbH & Co. KG Echangeur de chaleur
US20080135222A1 (en) * 2006-12-06 2008-06-12 Philippe Biver Pipe connecting structure for a heat exchanger
US20160033182A1 (en) * 2013-03-15 2016-02-04 Carrier Corporation Heat exchanger for air-cooled chiller
US20160138871A1 (en) * 2013-05-24 2016-05-19 Sanden Holdings Corporation Duplex heat exchanger
US9995513B2 (en) * 2012-10-31 2018-06-12 Denso Corporation Refrigerant evaporator

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5529116A (en) * 1989-08-23 1996-06-25 Showa Aluminum Corporation Duplex heat exchanger
US5348081A (en) * 1993-10-12 1994-09-20 General Motors Corporation High capacity automotive condenser
US6189604B1 (en) * 1999-01-19 2001-02-20 Denso Corporation Heat exchanger for inside/outside air two-passage unit
EP1643202A1 (fr) * 2004-10-04 2006-04-05 Behr GmbH & Co. KG Echangeur de chaleur
US20080135222A1 (en) * 2006-12-06 2008-06-12 Philippe Biver Pipe connecting structure for a heat exchanger
US9995513B2 (en) * 2012-10-31 2018-06-12 Denso Corporation Refrigerant evaporator
US20160033182A1 (en) * 2013-03-15 2016-02-04 Carrier Corporation Heat exchanger for air-cooled chiller
US20160138871A1 (en) * 2013-05-24 2016-05-19 Sanden Holdings Corporation Duplex heat exchanger

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