US20110127023A1 - Design characteristics for heat exchangers distribution insert - Google Patents
Design characteristics for heat exchangers distribution insert Download PDFInfo
- Publication number
- US20110127023A1 US20110127023A1 US12/994,236 US99423609A US2011127023A1 US 20110127023 A1 US20110127023 A1 US 20110127023A1 US 99423609 A US99423609 A US 99423609A US 2011127023 A1 US2011127023 A1 US 2011127023A1
- Authority
- US
- United States
- Prior art keywords
- distribution
- design
- distribution insert
- insert
- characteristic
- 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.)
- Abandoned
Links
Images
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
- 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
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
Definitions
- Microchannel or minichannel heat exchangers of a refrigeration system or an air conditioning system include a plurality of parallel flat heat exchange tubes through which refrigerant is distributed.
- An inlet manifold is in fluid communication with the heat exchange tubes, and the heat exchange tubes are substantially perpendicular to the direction of refrigerant flow through the inlet manifold.
- the heat exchanger may have a multi-pass configuration to improve performance by balancing and optimizing heat transfer and pressure drop characteristics, typically by employing a plurality of parallel heat exchange tubes within each refrigerant pass.
- Single-pass configurations are typically more desirable in evaporator applications as the refrigerant pressure drop plays a dominant role in the evaporator performance.
- Maldistribution of refrigerant into the heat exchange tubes can occur, which can cause the performance of the heat exchanger to decrease as compared to the performance achievable if the refrigerant is uniformly distributed through the heat exchange tubes. Maldistribution typically occurs when the two-phase refrigerant enters the inlet manifold. A vapor phase of the two-phase refrigerant has significantly different properties, moves at different velocities and is subjected to different effects of internal and external forces than a liquid phase refrigerant. The vapor phase separates from the liquid phase and flows independently, causing maldistribution of the refrigerant.
- a distribution insert can be employed inside the inlet manifold of the heat exchanger to improve the distribution of the refrigerant.
- the refrigerant enters the heat exchanger through the distribution insert and flows into the inlet manifold through orifices in the distribution insert. Due to the nature of two-phase refrigerant flow, it is difficult to design a distribution insert.
- a heat exchanger includes heat exchange tubes, a manifold, and a distribution insert including orifices that communicate a fluid into the manifold for distribution into the heat exchange tubes.
- a design characteristic of the distribution insert and another design characteristic of at least one of the distribution insert, the manifold and the heat exchange tubes are employed to determine an essential design relationship.
- the essential design relationship defines a design parameter that falls within a determined range of values.
- a method of designing a heat exchanger includes the steps of determining a range of values and selecting at least one design characteristic of a distribution insert.
- the distribution insert includes orifices, and the distribution insert is received in a manifold.
- a fluid is communicated through the plurality of orifices and into the manifold for distribution into heat exchange tubes.
- the method further includes the step of determining a relationship between the at least one design characteristic of the distribution insert and another characteristic of at least one of the distribution insert, the manifold and the heat exchange tubes.
- the essential design relationship defines a design parameter that falls within the range of values.
- FIG. 1 illustrates an exemplary refrigeration system
- FIG. 2 illustrates a side view of an inlet portion of a manifold of a heat exchanger
- FIG. 3 illustrates a perspective view of the inlet portion of the manifold of the heat exchanger showing various dimensions.
- FIG. 1 illustrates a basic refrigeration or air conditioning system 20 including a compressor 22 that compresses a refrigerant and delivers it downstream to a condenser 24 .
- the refrigerant rejects heat to a secondary fluid.
- the refrigerant passes through an expansion device 26 and is expanded to a low pressure.
- the expanded refrigerant flows into an inlet refrigerant pipe 28 leading into an evaporator 30 .
- the refrigerant accepts heat from another secondary fluid.
- the refrigerant is returned to the compressor 22 , completing the closed-loop refrigerant circuit.
- the air conditioning system 20 can include a refrigerant flow control device, such as a four-way reversing valve, shown schematically at 35 , to reverse the direction of refrigerant flow throughout the refrigerant circuit, in order to accommodate heat pump configurations and applications.
- a refrigerant flow control device such as a four-way reversing valve, shown schematically at 35 , to reverse the direction of refrigerant flow throughout the refrigerant circuit, in order to accommodate heat pump configurations and applications.
- the four-way reversing valve 35 directs the refrigerant from the compressor 22 to the condenser 24 .
- the four-way valve 35 directs the refrigerant from the compressor 22 to the evaporator 28 (which operates as a condenser, in the heating mode).
- FIG. 2 illustrates a portion of the evaporator 30 .
- the evaporator 30 includes a manifold 34 .
- the manifold 34 is an inlet manifold or an intermediate manifold of the evaporator 30 .
- an inlet manifold of an evaporator 30 is described.
- the evaporator 30 is a microchannel heat exchanger.
- the features of the invention can extend to other types of heat exchangers, such as round tube and plate fin heat exchangers, and to other applications, such as condensers and reheat heat exchangers.
- the invention will be disclosed with reference to a manifold 34 of an evaporator 30
- an intermediate manifold of a condenser 24 also falls within the scope of the invention.
- the condenser 24 can also be a microchannel heat exchanger.
- the benefits of the invention will be disclosed with reference to a two-phase refrigerant flow passing through the evaporator 30 , single-phase refrigerant flows and refrigerant-oil mixtures are also within the scope and can benefit from the invention.
- the inlet refrigerant pipe 28 fluidly communicates with a distribution insert 32 received within the manifold 34 , which provides a refrigerant flow path along a longitudinal axis X.
- the distribution insert 32 fluidly communicates with a plurality of heat exchange tubes 36 positioned generally perpendicular to the manifold 34 .
- the inlet refrigerant pipe 28 may be positioned at the end of the manifold 34 , in the middle of the manifold 34 , or at any intermediate location in between, and may have a single or multiple connections to the distribution insert 32 .
- Each heat exchange tube 36 can be a flat tube, and may have several ports for refrigerant to flow through. In one example, each port has a hydraulic diameter of less than 1 mm.
- a plurality of heat transfer fins 38 can be disposed between and rigidly attached to the heat exchange tubes 36 to enhance external heat transfer and provide structural rigidity for the evaporator 30 .
- the plurality of heat transfer fins 38 are attached to the heat exchange tubes 36 by a furnace braze process.
- the distribution insert 32 includes a plurality of refrigerant distribution orifices 42 to provide a refrigerant path from an internal cavity 50 of the distribution insert 32 to the manifold 34 .
- the distribution orifices 42 can have any shape.
- the distribution orifices 42 can have a round shape, a rectangular shape, an oval shape or any other suitable shape.
- the distribution insert 32 receives the two-phase refrigerant from the inlet refrigerant pipe 28 and uniformly delivers the refrigerant through the plurality of distribution orifices 42 and into the manifold 34 for distribution to the heat exchange tubes 36 .
- the relatively small size of the distribution insert 32 provides significant momentum for the refrigerant flow, preventing the phase separation of the two-phase refrigerant or promoting annual (in contrast to stratified) refrigerant flow pattern.
- FIG. 3 shows various design characteristics, such as diameters, lengths, positions and other dimensions of components of the evaporator 30 .
- the evaporator 30 is designed for optimal refrigerant distribution.
- At least one design characteristic of the distribution insert 32 is selected.
- An essential design relationship between the at least one design characteristic of the distribution insert 32 and another design characteristic of at least one of the distribution insert 32 , the manifold 34 and the heat exchange tubes 36 is determined and defines a design parameter. If the design parameter falls within a pre-determined range of values, this indicates that the evaporator 30 is designed for optimal refrigerant distribution to the heat exchange tubes 36 and to prevent or significantly reduce refrigerant maldistribution amongst the heat exchange tubes 36 .
- the essential design relationship is a ratio of a first design characteristic to a second design characteristic, that is, a first design characteristic divided by a second design characteristic.
- Optimal effectiveness of refrigerant distribution through the distribution insert 32 is achieved if the non-dimensional design parameter defined by essential design relationship falls within the given pre-determined range. At least one of the first design characteristic and the second design characteristic is associated with the distribution insert 32 .
- the characteristic of the distribution insert 32 is the inner diameter of the distribution insert 32 (D ins ).
- the relationship is defined as a ratio of the inner diameter of the distribution insert 32 (D ins ) to the inner diameter of the manifold 34 (D man ), and the ratio is then squared to define a non-dimensional design parameter.
- This non-dimensional design parameter represents the flow momentum within the distribution insert 32 versus the flow momentum within the manifold 34 without the distribution insert 32 .
- the value of the design parameter should be in the range of 0.02 to 0.95.
- the characteristics of the distribution insert 32 are the total cross-sectional area of all the distribution orifices 42 of the distribution insert 32 (A orifice ) and the external surface area of the distribution insert 32 (A insert,surf ).
- the relationship is defined as a ratio of the total cross-sectional area of all the distribution orifices 42 of the distribution insert 32 (A orifice ) to the external surface area of the distribution insert 32 (A insert,surf ), which defines a non-dimensional design parameter.
- This non-dimensional design parameter represents the density of the distribution orifices 42 of the distribution insert 32 .
- the value of the design parameter should be in the range of 50 to 5000.
- the characteristics of the distribution insert 32 are the total cross-sectional area of all the distribution orifices 42 of the distribution insert 32 (A orifice ) and the cross-sectional area of the distribution insert 32 in the plane perpendicular to the axis X and based on the diameter (A insert,cross ).
- the relationship is defined as a ratio of the total cross-sectional area of all distribution orifices 42 of the distribution insert 32 (A orifice ) to the cross-sectional area of the distribution insert 32 in the plane perpendicular to the axis X and based on the diameter D ins (A insert,cross ) which defines a non-dimensional design parameter.
- This non-dimensional design parameter represents the flow momentum through the distribution orifices 42 of the distribution insert 32 versus the flow momentum through the distribution insert 32 .
- the value of the design parameter should be in the range of 0.01 to 100.
- the characteristics of the distribution insert 32 are the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ) and the axial separation between centers of the distribution orifices 42 of the distribution insert 32 (L orifice ).
- the relationship is defined as the ratio of the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ) to the axial separation between centers of the distribution orifices 42 of the distribution insert 32 (L orifice ), which defines a non-dimensional design parameter.
- This non-dimensional design parameter represents the density of the distribution orifices 42 of the distribution insert 32 .
- the value of the design parameter should be in the range of 0.01 to 35.
- the characteristics of the distribution insert 32 are the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ) and the external surface area of the distribution insert 32 (A insert,surf ).
- the relationship is defined as the ratio of a first design characteristic to a second design characteristic.
- the first design characteristic is defined as the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ) squared divided by external surface area of the distribution insert 32 (A insert,surf ).
- the second design characteristic is defined as the hydraulic diameter of the heat exchange tubes 36 (D tube ) squared divided by the cross-sectional area of the manifold 34 in the plane of the longitudinal axis X (A man,long ).
- the ratio of the first design characteristic to the second design characteristic determines a non-dimensional design parameter.
- This non-dimensional design parameter represents the flow momentum through the heat exchange tubes 36 versus the flow momentum through the distribution orifices 42.
- the value of the design parameter should be in the range of 0.01 to 25.
- the characteristics of the distribution insert 32 are the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ) and the number of the distribution orifices 42 (N).
- the relationship is defined as the ratio of a first design characteristic to a second design characteristic.
- the first design characteristic is defined as the number of distribution orifices 42 (N) multiplied by the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ), which is then squared.
- the second design characteristic is defined as the number of heat exchange tubes 36 (M) multiplied by the hydraulic diameter of the heat exchange tubes 36 (D tube ), which is then squared.
- the ratio of the first design characteristic to the second design characteristic defines a non-dimensional design parameter. This design parameter represents the flow momentum through the heat exchange tubes 36 versus the flow momentum through the distribution orifices 42 . For optimal performance, the value of the design parameter should be in the range of 0.01 to 100.
- the characteristics of the distribution insert 32 are the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ), the length of the distribution insert 32 (L ins ), and the inner diameter of the distribution insert 32 (D ins ).
- the relationship is defined as the ratio of a first design characteristic to a second design characteristic.
- the first design characteristic is defined as the inner diameter of the manifold 34 (D man ) divided by the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D orifice ) squared.
- the second design characteristic is defined by the length of the distribution insert 32 (L ins ) divided by the inner diameter of the distribution insert 32 (D ins ) squared.
- the first design characteristic is divided by the second design characteristic to obtain the ratio.
- the ratio of the first design characteristic to the second design characteristic determines a non-dimensional design parameter.
- This non-dimensional design parameter represents the pressure differential across the manifold 34 versus the pressure differential along the manifold 34 .
- the value of the design parameter should be in the range of 0.01 to 20.
- the characteristic of the distribution insert 32 is the length of the distribution insert 32 (L ins ).
- the relationship is defined as the inner diameter of the manifold 34 (D man ) divided by the length of the distribution insert 32 (L ins ), which defines a non-dimensional design parameter.
- This non-dimensional design parameter represents the traveled distance along the distribution insert 32 compared to the distance across the manifold 34 .
- the value of the design parameter should be in the range of 1 to 1000.
Abstract
Description
- This application claims priority to U.S. Provisional Patent Application No. 61/079,521, which was filed Jul. 10, 2008.
- Microchannel or minichannel heat exchangers of a refrigeration system or an air conditioning system include a plurality of parallel flat heat exchange tubes through which refrigerant is distributed. An inlet manifold is in fluid communication with the heat exchange tubes, and the heat exchange tubes are substantially perpendicular to the direction of refrigerant flow through the inlet manifold. The heat exchanger may have a multi-pass configuration to improve performance by balancing and optimizing heat transfer and pressure drop characteristics, typically by employing a plurality of parallel heat exchange tubes within each refrigerant pass. Single-pass configurations are typically more desirable in evaporator applications as the refrigerant pressure drop plays a dominant role in the evaporator performance.
- Maldistribution of refrigerant into the heat exchange tubes can occur, which can cause the performance of the heat exchanger to decrease as compared to the performance achievable if the refrigerant is uniformly distributed through the heat exchange tubes. Maldistribution typically occurs when the two-phase refrigerant enters the inlet manifold. A vapor phase of the two-phase refrigerant has significantly different properties, moves at different velocities and is subjected to different effects of internal and external forces than a liquid phase refrigerant. The vapor phase separates from the liquid phase and flows independently, causing maldistribution of the refrigerant.
- A distribution insert can be employed inside the inlet manifold of the heat exchanger to improve the distribution of the refrigerant. The refrigerant enters the heat exchanger through the distribution insert and flows into the inlet manifold through orifices in the distribution insert. Due to the nature of two-phase refrigerant flow, it is difficult to design a distribution insert.
- A heat exchanger includes heat exchange tubes, a manifold, and a distribution insert including orifices that communicate a fluid into the manifold for distribution into the heat exchange tubes. A design characteristic of the distribution insert and another design characteristic of at least one of the distribution insert, the manifold and the heat exchange tubes are employed to determine an essential design relationship. The essential design relationship defines a design parameter that falls within a determined range of values.
- In still another exemplary embodiment, a method of designing a heat exchanger includes the steps of determining a range of values and selecting at least one design characteristic of a distribution insert. The distribution insert includes orifices, and the distribution insert is received in a manifold. A fluid is communicated through the plurality of orifices and into the manifold for distribution into heat exchange tubes. The method further includes the step of determining a relationship between the at least one design characteristic of the distribution insert and another characteristic of at least one of the distribution insert, the manifold and the heat exchange tubes. The essential design relationship defines a design parameter that falls within the range of values.
- These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
-
FIG. 1 illustrates an exemplary refrigeration system; -
FIG. 2 illustrates a side view of an inlet portion of a manifold of a heat exchanger; and -
FIG. 3 illustrates a perspective view of the inlet portion of the manifold of the heat exchanger showing various dimensions. -
FIG. 1 illustrates a basic refrigeration orair conditioning system 20 including acompressor 22 that compresses a refrigerant and delivers it downstream to acondenser 24. In thecondenser 24, the refrigerant rejects heat to a secondary fluid. From thecondenser 24, the refrigerant passes through anexpansion device 26 and is expanded to a low pressure. The expanded refrigerant flows into aninlet refrigerant pipe 28 leading into anevaporator 30. In theevaporator 30, the refrigerant accepts heat from another secondary fluid. From theevaporator 30, the refrigerant is returned to thecompressor 22, completing the closed-loop refrigerant circuit. - The
air conditioning system 20 can include a refrigerant flow control device, such as a four-way reversing valve, shown schematically at 35, to reverse the direction of refrigerant flow throughout the refrigerant circuit, in order to accommodate heat pump configurations and applications. When therefrigeration system 20 is operating in a cooling mode, the four-way reversing valve 35 directs the refrigerant from thecompressor 22 to thecondenser 24. When therefrigeration system 20 is operating in a heating mode, the four-way valve 35 directs the refrigerant from thecompressor 22 to the evaporator 28 (which operates as a condenser, in the heating mode). -
FIG. 2 illustrates a portion of theevaporator 30. Theevaporator 30 includes amanifold 34. In one example, themanifold 34 is an inlet manifold or an intermediate manifold of theevaporator 30. In the below examples, an inlet manifold of anevaporator 30 is described. In one example, theevaporator 30 is a microchannel heat exchanger. - However, the features of the invention can extend to other types of heat exchangers, such as round tube and plate fin heat exchangers, and to other applications, such as condensers and reheat heat exchangers. Further, although the invention will be disclosed with reference to a
manifold 34 of anevaporator 30, an intermediate manifold of acondenser 24 also falls within the scope of the invention. Thecondenser 24 can also be a microchannel heat exchanger. Additionally, although the benefits of the invention will be disclosed with reference to a two-phase refrigerant flow passing through theevaporator 30, single-phase refrigerant flows and refrigerant-oil mixtures are also within the scope and can benefit from the invention. - The
inlet refrigerant pipe 28 fluidly communicates with adistribution insert 32 received within themanifold 34, which provides a refrigerant flow path along a longitudinal axis X. The distribution insert 32 fluidly communicates with a plurality ofheat exchange tubes 36 positioned generally perpendicular to themanifold 34. Theinlet refrigerant pipe 28 may be positioned at the end of themanifold 34, in the middle of themanifold 34, or at any intermediate location in between, and may have a single or multiple connections to the distribution insert 32. Eachheat exchange tube 36 can be a flat tube, and may have several ports for refrigerant to flow through. In one example, each port has a hydraulic diameter of less than 1 mm. - A plurality of
heat transfer fins 38 can be disposed between and rigidly attached to theheat exchange tubes 36 to enhance external heat transfer and provide structural rigidity for theevaporator 30. In one example, the plurality ofheat transfer fins 38 are attached to theheat exchange tubes 36 by a furnace braze process. - The
distribution insert 32 includes a plurality ofrefrigerant distribution orifices 42 to provide a refrigerant path from aninternal cavity 50 of the distribution insert 32 to themanifold 34. Thedistribution orifices 42 can have any shape. For example, thedistribution orifices 42 can have a round shape, a rectangular shape, an oval shape or any other suitable shape. - The
distribution insert 32 receives the two-phase refrigerant from theinlet refrigerant pipe 28 and uniformly delivers the refrigerant through the plurality ofdistribution orifices 42 and into themanifold 34 for distribution to theheat exchange tubes 36. Typically, the relatively small size of thedistribution insert 32 provides significant momentum for the refrigerant flow, preventing the phase separation of the two-phase refrigerant or promoting annual (in contrast to stratified) refrigerant flow pattern. -
FIG. 3 shows various design characteristics, such as diameters, lengths, positions and other dimensions of components of theevaporator 30. Theevaporator 30 is designed for optimal refrigerant distribution. At least one design characteristic of thedistribution insert 32 is selected. An essential design relationship between the at least one design characteristic of the distribution insert 32 and another design characteristic of at least one of the distribution insert 32, themanifold 34 and theheat exchange tubes 36 is determined and defines a design parameter. If the design parameter falls within a pre-determined range of values, this indicates that theevaporator 30 is designed for optimal refrigerant distribution to theheat exchange tubes 36 and to prevent or significantly reduce refrigerant maldistribution amongst theheat exchange tubes 36. - In one example, the essential design relationship is a ratio of a first design characteristic to a second design characteristic, that is, a first design characteristic divided by a second design characteristic. Optimal effectiveness of refrigerant distribution through the
distribution insert 32 is achieved if the non-dimensional design parameter defined by essential design relationship falls within the given pre-determined range. At least one of the first design characteristic and the second design characteristic is associated with thedistribution insert 32. - Various characteristics of the
evaporator 30 are defined as below: -
Dins inner diameter of the distribution insert 32 Dman inner diameter of the manifold 34 Dorifice hydraulic diameter of the distribution orifices 42 of the distribution insert 32 Dtube hydraulic diameter of the heat exchange tubes 36 Lins length of the distribution insert 32 Lman length of the manifold 34 Lorifice axial separation between centers of the distribution orifices 42 of the distribution insert 32Ainsert, surf external surface area of the distribution insert 32 Ainsert, cross cross-sectional area of the distribution insert 32 in the planeperpendicular to the axis X and based on the diameter Dins Aorifice total cross-sectional area of all the distribution orifices 42 of the distribution insert 32 Aman, dia cross-sectional area of the manifold 34 in the plane perpendicular to the axis X and based on the diameter Dman Aman, long cross-sectional area of the manifold 34 in the plane of the longitudinal axis X M number of the heat exchange tubes 36 N number of the distribution orifices 42 - By employing these design characteristics within the below defined relationships/ratios, several non-dimensional design parameters can be defined. A list of these design parameters and the desired pre-determined ranges of their values are defined below:
-
Relationship Lower Upper No. Relationships limit limit 1 (Dins/Dman)2 0.02 0.95 2 Aorifice/ A insert, surf50 5000 3 Aorifice/Ainsert, cross 0.01 100 4 Dorifice/Lorifice 0.01 35 5 (Dorifice 2/Ainsert, surf)/ 0.01 25 (Dtube 2/Aman, long) 6 [(N* Dorifice)2]/[(M* Dtube)2] 0.1 100 7 (Dman/Dorifice 2)/(Lins/Dins)2 0.01 20 8 Dman/Lins 1 1000 - Using Relationship 1, the characteristic of the
distribution insert 32 is the inner diameter of the distribution insert 32 (Dins). The relationship is defined as a ratio of the inner diameter of the distribution insert 32 (Dins) to the inner diameter of the manifold 34 (Dman), and the ratio is then squared to define a non-dimensional design parameter. This non-dimensional design parameter represents the flow momentum within thedistribution insert 32 versus the flow momentum within the manifold 34 without thedistribution insert 32. For optimal performance, the value of the design parameter should be in the range of 0.02 to 0.95. - Using Relationship 2, the characteristics of the
distribution insert 32 are the total cross-sectional area of all thedistribution orifices 42 of the distribution insert 32 (Aorifice) and the external surface area of the distribution insert 32 (Ainsert,surf). The relationship is defined as a ratio of the total cross-sectional area of all thedistribution orifices 42 of the distribution insert 32 (Aorifice) to the external surface area of the distribution insert 32 (Ainsert,surf), which defines a non-dimensional design parameter. This non-dimensional design parameter represents the density of thedistribution orifices 42 of thedistribution insert 32. For optimal performance, the value of the design parameter should be in the range of 50 to 5000. - Using Relationship 3, the characteristics of the
distribution insert 32 are the total cross-sectional area of all thedistribution orifices 42 of the distribution insert 32 (Aorifice) and the cross-sectional area of thedistribution insert 32 in the plane perpendicular to the axis X and based on the diameter (Ainsert,cross). The relationship is defined as a ratio of the total cross-sectional area of alldistribution orifices 42 of the distribution insert 32 (Aorifice) to the cross-sectional area of thedistribution insert 32 in the plane perpendicular to the axis X and based on the diameter Dins (Ainsert,cross) which defines a non-dimensional design parameter. This non-dimensional design parameter represents the flow momentum through thedistribution orifices 42 of thedistribution insert 32 versus the flow momentum through thedistribution insert 32. For optimal performance, the value of the design parameter should be in the range of 0.01 to 100. - Using Relationship 4, the characteristics of the
distribution insert 32 are the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice) and the axial separation between centers of thedistribution orifices 42 of the distribution insert 32 (Lorifice). The relationship is defined as the ratio of the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice) to the axial separation between centers of thedistribution orifices 42 of the distribution insert 32 (Lorifice), which defines a non-dimensional design parameter. This non-dimensional design parameter represents the density of thedistribution orifices 42 of thedistribution insert 32. For optimal performance, the value of the design parameter should be in the range of 0.01 to 35. - Using Relationship 5, the characteristics of the
distribution insert 32 are the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice) and the external surface area of the distribution insert 32 (Ainsert,surf). The relationship is defined as the ratio of a first design characteristic to a second design characteristic. The first design characteristic is defined as the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice) squared divided by external surface area of the distribution insert 32 (Ainsert,surf). The second design characteristic is defined as the hydraulic diameter of the heat exchange tubes 36 (Dtube) squared divided by the cross-sectional area of the manifold 34 in the plane of the longitudinal axis X (Aman,long). The ratio of the first design characteristic to the second design characteristic determines a non-dimensional design parameter. This non-dimensional design parameter represents the flow momentum through theheat exchange tubes 36 versus the flow momentum through thedistribution orifices 42. For optimal performance, the value of the design parameter should be in the range of 0.01 to 25. - Using Relationship 6, the characteristics of the
distribution insert 32 are the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice) and the number of the distribution orifices 42 (N). The relationship is defined as the ratio of a first design characteristic to a second design characteristic. The first design characteristic is defined as the number of distribution orifices 42 (N) multiplied by the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice), which is then squared. The second design characteristic is defined as the number of heat exchange tubes 36 (M) multiplied by the hydraulic diameter of the heat exchange tubes 36 (Dtube), which is then squared. The ratio of the first design characteristic to the second design characteristic defines a non-dimensional design parameter. This design parameter represents the flow momentum through theheat exchange tubes 36 versus the flow momentum through thedistribution orifices 42. For optimal performance, the value of the design parameter should be in the range of 0.01 to 100. - Using Relationship 7, the characteristics of the
distribution insert 32 are the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice), the length of the distribution insert 32 (Lins), and the inner diameter of the distribution insert 32 (Dins). The relationship is defined as the ratio of a first design characteristic to a second design characteristic. The first design characteristic is defined as the inner diameter of the manifold 34 (Dman) divided by the hydraulic diameter of thedistribution orifices 42 of the distribution insert 32 (Dorifice) squared. The second design characteristic is defined by the length of the distribution insert 32 (Lins) divided by the inner diameter of the distribution insert 32 (Dins) squared. The first design characteristic is divided by the second design characteristic to obtain the ratio. The ratio of the first design characteristic to the second design characteristic determines a non-dimensional design parameter. This non-dimensional design parameter represents the pressure differential across the manifold 34 versus the pressure differential along themanifold 34. For optimal performance, the value of the design parameter should be in the range of 0.01 to 20. - Using Relationship 8, the characteristic of the
distribution insert 32 is the length of the distribution insert 32 (Lins). The relationship is defined as the inner diameter of the manifold 34 (Dman) divided by the length of the distribution insert 32 (Lins), which defines a non-dimensional design parameter. This non-dimensional design parameter represents the traveled distance along thedistribution insert 32 compared to the distance across themanifold 34. For optimal performance, the value of the design parameter should be in the range of 1 to 1000. - By calculating a relationship or ratio employing at least one essential design characteristic of the
distribution insert 32 and determining if the calculated value of a defined non-dimensional design parameter falls within a pre-determined range of values, it can be determined if the distribution effectiveness of thedistribution insert 32 and theevaporator 30 is optimized. - The foregoing description is only exemplary of the principles of the invention. Many modifications and variations of the present invention are possible in light of the above teachings. The preferred embodiments of this invention have been disclosed, however, so that one of ordinary skill in the art would recognize that certain modifications would come within the scope of this invention. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described. For that reason the following claims should be studied to determine the true scope and content of this invention.
Claims (22)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/994,236 US20110127023A1 (en) | 2008-07-10 | 2009-06-10 | Design characteristics for heat exchangers distribution insert |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US7952108P | 2008-07-10 | 2008-07-10 | |
US12/994,236 US20110127023A1 (en) | 2008-07-10 | 2009-06-10 | Design characteristics for heat exchangers distribution insert |
PCT/US2009/047141 WO2010005676A2 (en) | 2008-07-10 | 2009-06-12 | Design characteristics for heat exchanger distribution insert |
Publications (1)
Publication Number | Publication Date |
---|---|
US20110127023A1 true US20110127023A1 (en) | 2011-06-02 |
Family
ID=41507648
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/994,236 Abandoned US20110127023A1 (en) | 2008-07-10 | 2009-06-10 | Design characteristics for heat exchangers distribution insert |
Country Status (4)
Country | Link |
---|---|
US (1) | US20110127023A1 (en) |
EP (1) | EP2310790A4 (en) |
CN (1) | CN102089612A (en) |
WO (1) | WO2010005676A2 (en) |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110155357A1 (en) * | 2009-11-27 | 2011-06-30 | Kabushiki Kaisha Toshiba | Heat exchanger |
US20110290465A1 (en) * | 2010-06-01 | 2011-12-01 | Delphi Technologies, Inc. | Orientation insensitive refrigerant distributor tube |
US20140083665A1 (en) * | 2012-09-25 | 2014-03-27 | Behr Gmbh & Co. Kg | Heat exchanger |
US20140096944A1 (en) * | 2012-10-09 | 2014-04-10 | Samsung Electronics Co., Ltd. | Heat exchanger |
US20150083383A1 (en) * | 2012-04-26 | 2015-03-26 | Mitsubishi Electric Corporation | Heat exchanger and heat exchange method |
US20150122470A1 (en) * | 2012-11-16 | 2015-05-07 | Delphi Technologies, Inc. | Heat pump heat exchanger having a low pressure drop distribution tube |
US20160091253A1 (en) * | 2014-09-30 | 2016-03-31 | Valeo Climate Control Corp. | Heater core |
US10072900B2 (en) * | 2014-09-16 | 2018-09-11 | Mahle International Gmbh | Heat exchanger distributor with intersecting streams |
JP2019066132A (en) * | 2017-10-04 | 2019-04-25 | パナソニックIpマネジメント株式会社 | Multi-path type heat exchanger and refrigeration system using the same |
US10563895B2 (en) | 2016-12-07 | 2020-02-18 | Johnson Controls Technology Company | Adjustable inlet header for heat exchanger of an HVAC system |
US20220196342A1 (en) * | 2019-04-15 | 2022-06-23 | Uhrig Energie Gmbh | Heat exchanger module, heat exchanger system and method for producing the heat exchanger system |
US20220333876A1 (en) * | 2020-06-17 | 2022-10-20 | Mahle International Gmbh | Heat exchanger |
US11713931B2 (en) * | 2019-05-02 | 2023-08-01 | Carrier Corporation | Multichannel evaporator distributor |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102313400A (en) * | 2011-07-21 | 2012-01-11 | 广东美的电器股份有限公司 | Microchannel parallel-flow heat exchanger |
WO2013190617A1 (en) * | 2012-06-18 | 2013-12-27 | 三菱電機株式会社 | Heat exchanger |
CN103542646B (en) * | 2012-07-13 | 2016-07-06 | 苏州三星电子有限公司 | Throttling arrangement and heat-exchange system |
KR20140116626A (en) | 2013-03-25 | 2014-10-06 | 엘지전자 주식회사 | A heat exchanger |
Citations (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4124069A (en) * | 1975-08-01 | 1978-11-07 | Linde Aktiengesellschaft | Heat exchanger with spirally wound sheets |
US4287945A (en) * | 1979-07-03 | 1981-09-08 | The A.P.V. Company Limited | Plate heat exchanger |
US4709689A (en) * | 1986-12-02 | 1987-12-01 | Environmental Resources, Inc. | Solar heat exchange system |
US4884629A (en) * | 1988-02-10 | 1989-12-05 | Bronnert Herve X | High pressure multiple tube and shell type heat exchanger |
US5372188A (en) * | 1985-10-02 | 1994-12-13 | Modine Manufacturing Co. | Heat exchanger for a refrigerant system |
US6173763B1 (en) * | 1994-10-28 | 2001-01-16 | Kabushiki Kaisha Toshiba | Heat exchanger tube and method for manufacturing a heat exchanger |
US20040026072A1 (en) * | 2002-08-06 | 2004-02-12 | Visteon Global Technologies, Inc. | Serrated tube-flow distributor |
US20050092475A1 (en) * | 2002-03-20 | 2005-05-05 | Behr Gmbh & Co. Kg | Heat exchanger and cooling system |
US20060102432A1 (en) * | 2004-10-18 | 2006-05-18 | Kouken Company, Limited | Method for controlling automatic lifting-and-lowering-motion of mobile power generating apparatus, and automatic lift-and-lower-type stand controlling apparatus |
US20060102332A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Minichannel heat exchanger with restrictive inserts |
US20060101850A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with shaped manifolds |
US20060102331A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with spiral inlet manifold |
US20060101849A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with variable channel insertion depth |
US7143605B2 (en) * | 2003-12-22 | 2006-12-05 | Hussman Corporation | Flat-tube evaporator with micro-distributor |
US7281387B2 (en) * | 2004-04-29 | 2007-10-16 | Carrier Commercial Refrigeration Inc. | Foul-resistant condenser using microchannel tubing |
US20080023186A1 (en) * | 2006-07-25 | 2008-01-31 | Henry Earl Beamer | Heat exchanger assembly |
US20080023185A1 (en) * | 2006-07-25 | 2008-01-31 | Henry Earl Beamer | Heat exchanger assembly |
WO2008048251A2 (en) * | 2006-10-13 | 2008-04-24 | Carrier Corporation | Method and apparatus for improving distribution of fluid in a heat exchanger |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH06159983A (en) * | 1992-11-20 | 1994-06-07 | Showa Alum Corp | Heat exchanger |
JPH0886591A (en) * | 1994-07-22 | 1996-04-02 | Nippondenso Co Ltd | Heat exchanger and refrigerant evaporator |
JPH09166368A (en) * | 1995-12-14 | 1997-06-24 | Sanden Corp | Heat exchanger |
AU2005326694B2 (en) * | 2005-02-02 | 2010-07-22 | Carrier Corporation | Tube inset and bi-flow arrangement for a header of a heat pump |
US7967060B2 (en) * | 2005-08-18 | 2011-06-28 | Parker-Hannifin Corporation | Evaporating heat exchanger |
JP2007178048A (en) * | 2005-12-27 | 2007-07-12 | Calsonic Kansei Corp | Header tank for heat exchanger |
-
2009
- 2009-06-10 US US12/994,236 patent/US20110127023A1/en not_active Abandoned
- 2009-06-12 EP EP09794882.2A patent/EP2310790A4/en not_active Withdrawn
- 2009-06-12 WO PCT/US2009/047141 patent/WO2010005676A2/en active Application Filing
- 2009-06-12 CN CN2009801267159A patent/CN102089612A/en active Pending
Patent Citations (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4124069A (en) * | 1975-08-01 | 1978-11-07 | Linde Aktiengesellschaft | Heat exchanger with spirally wound sheets |
US4287945A (en) * | 1979-07-03 | 1981-09-08 | The A.P.V. Company Limited | Plate heat exchanger |
US5372188A (en) * | 1985-10-02 | 1994-12-13 | Modine Manufacturing Co. | Heat exchanger for a refrigerant system |
US4709689A (en) * | 1986-12-02 | 1987-12-01 | Environmental Resources, Inc. | Solar heat exchange system |
US4884629A (en) * | 1988-02-10 | 1989-12-05 | Bronnert Herve X | High pressure multiple tube and shell type heat exchanger |
US6173763B1 (en) * | 1994-10-28 | 2001-01-16 | Kabushiki Kaisha Toshiba | Heat exchanger tube and method for manufacturing a heat exchanger |
US20050092475A1 (en) * | 2002-03-20 | 2005-05-05 | Behr Gmbh & Co. Kg | Heat exchanger and cooling system |
US20040026072A1 (en) * | 2002-08-06 | 2004-02-12 | Visteon Global Technologies, Inc. | Serrated tube-flow distributor |
US7143605B2 (en) * | 2003-12-22 | 2006-12-05 | Hussman Corporation | Flat-tube evaporator with micro-distributor |
US7281387B2 (en) * | 2004-04-29 | 2007-10-16 | Carrier Commercial Refrigeration Inc. | Foul-resistant condenser using microchannel tubing |
US20060102432A1 (en) * | 2004-10-18 | 2006-05-18 | Kouken Company, Limited | Method for controlling automatic lifting-and-lowering-motion of mobile power generating apparatus, and automatic lift-and-lower-type stand controlling apparatus |
US20060102331A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with spiral inlet manifold |
US20060101849A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with variable channel insertion depth |
US20060101850A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with shaped manifolds |
US20060102332A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Minichannel heat exchanger with restrictive inserts |
US20080023186A1 (en) * | 2006-07-25 | 2008-01-31 | Henry Earl Beamer | Heat exchanger assembly |
US20080023185A1 (en) * | 2006-07-25 | 2008-01-31 | Henry Earl Beamer | Heat exchanger assembly |
WO2008048251A2 (en) * | 2006-10-13 | 2008-04-24 | Carrier Corporation | Method and apparatus for improving distribution of fluid in a heat exchanger |
Cited By (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110155357A1 (en) * | 2009-11-27 | 2011-06-30 | Kabushiki Kaisha Toshiba | Heat exchanger |
US9482475B2 (en) * | 2009-11-27 | 2016-11-01 | Kabushiki Kaisha Toshiba | Heat exchanger |
US20110290465A1 (en) * | 2010-06-01 | 2011-12-01 | Delphi Technologies, Inc. | Orientation insensitive refrigerant distributor tube |
US20150083383A1 (en) * | 2012-04-26 | 2015-03-26 | Mitsubishi Electric Corporation | Heat exchanger and heat exchange method |
US9709338B2 (en) * | 2012-09-25 | 2017-07-18 | Mahle International Gmbh | Heat exchanger |
US20140083665A1 (en) * | 2012-09-25 | 2014-03-27 | Behr Gmbh & Co. Kg | Heat exchanger |
US20140096944A1 (en) * | 2012-10-09 | 2014-04-10 | Samsung Electronics Co., Ltd. | Heat exchanger |
US20150122470A1 (en) * | 2012-11-16 | 2015-05-07 | Delphi Technologies, Inc. | Heat pump heat exchanger having a low pressure drop distribution tube |
US9746255B2 (en) * | 2012-11-16 | 2017-08-29 | Mahle International Gmbh | Heat pump heat exchanger having a low pressure drop distribution tube |
US10072900B2 (en) * | 2014-09-16 | 2018-09-11 | Mahle International Gmbh | Heat exchanger distributor with intersecting streams |
US10113817B2 (en) * | 2014-09-30 | 2018-10-30 | Valeo Climate Control Corp. | Heater core |
US20160091253A1 (en) * | 2014-09-30 | 2016-03-31 | Valeo Climate Control Corp. | Heater core |
US10563895B2 (en) | 2016-12-07 | 2020-02-18 | Johnson Controls Technology Company | Adjustable inlet header for heat exchanger of an HVAC system |
US11506434B2 (en) | 2016-12-07 | 2022-11-22 | Johnson Controls Tyco IP Holdings LLP | Adjustable inlet header for heat exchanger of an HVAC system |
JP2019066132A (en) * | 2017-10-04 | 2019-04-25 | パナソニックIpマネジメント株式会社 | Multi-path type heat exchanger and refrigeration system using the same |
US20220196342A1 (en) * | 2019-04-15 | 2022-06-23 | Uhrig Energie Gmbh | Heat exchanger module, heat exchanger system and method for producing the heat exchanger system |
US11713931B2 (en) * | 2019-05-02 | 2023-08-01 | Carrier Corporation | Multichannel evaporator distributor |
US20220333876A1 (en) * | 2020-06-17 | 2022-10-20 | Mahle International Gmbh | Heat exchanger |
Also Published As
Publication number | Publication date |
---|---|
WO2010005676A2 (en) | 2010-01-14 |
WO2010005676A3 (en) | 2010-03-25 |
EP2310790A4 (en) | 2014-10-08 |
EP2310790A2 (en) | 2011-04-20 |
CN102089612A (en) | 2011-06-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20110127023A1 (en) | Design characteristics for heat exchangers distribution insert | |
US8171987B2 (en) | Minichannel heat exchanger header insert for distribution | |
KR100830301B1 (en) | Heat exchanger with multiple stage fluid expansion in header | |
AU2006211653B2 (en) | Parallel flow heat exchanger for heat pump applications | |
US8302673B2 (en) | Parallel flow evaporator with spiral inlet manifold | |
US8333088B2 (en) | Heat exchanger design for improved performance and manufacturability | |
JP6202451B2 (en) | Heat exchanger and air conditioner | |
US20080105420A1 (en) | Parallel Flow Heat Exchanger With Crimped Channel Entrance | |
US20100071392A1 (en) | Parallel flow evaporator with shaped manifolds | |
JP4358981B2 (en) | Air conditioning condenser | |
US20060101849A1 (en) | Parallel flow evaporator with variable channel insertion depth | |
US10378833B2 (en) | Stacking-type header, heat exchanger, and air-conditioning apparatus | |
JP2002228299A (en) | Composite heat exchanger | |
WO2021050426A1 (en) | Heat exchanger assembly | |
WO2021214849A1 (en) | Air conditioner, freezer, and distributor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: CARRIER CORPORATION, CONNECTICUT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TARAS, MICHAEL F.;BENDAPUDI, SAYTAM;JIANG, YIRONG;REEL/FRAME:025396/0900 Effective date: 20080711 |
|
AS | Assignment |
Owner name: CARRIER CORPORATION, CONNECTICUT Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE TITLE PREVIOUSLY RECORDED ON REEL 025396 FRAME 0900. ASSIGNOR(S) HEREBY CONFIRMS THE TITLE SHOULD BE --DESIGN CHARACTERISTICS FOR HEAT EXCHANGER DISTRIBUTION INSERT--;ASSIGNORS:TARAS, MICHAEL F.;BENDAPUDI, SAYTAM;JIANG, YIRONG;REEL/FRAME:026265/0874 Effective date: 20080711 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |