EP2310790A2 - Design characteristics for heat exchanger distribution insert - Google Patents

Design characteristics for heat exchanger distribution insert

Info

Publication number
EP2310790A2
EP2310790A2 EP09794882A EP09794882A EP2310790A2 EP 2310790 A2 EP2310790 A2 EP 2310790A2 EP 09794882 A EP09794882 A EP 09794882A EP 09794882 A EP09794882 A EP 09794882A EP 2310790 A2 EP2310790 A2 EP 2310790A2
Authority
EP
European Patent Office
Prior art keywords
distribution
design
distribution insert
insert
heat exchanger
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.)
Withdrawn
Application number
EP09794882A
Other languages
German (de)
French (fr)
Other versions
EP2310790A4 (en
Inventor
Michael F. Taras
Satyam Bendapudi
Yirong Jiang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
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 Carrier Corp filed Critical Carrier Corp
Publication of EP2310790A2 publication Critical patent/EP2310790A2/en
Publication of EP2310790A4 publication Critical patent/EP2310790A4/en
Withdrawn legal-status Critical Current

Links

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.
  • Figure 1 illustrates an exemplary refrigeration system
  • Figure 2 illustrates a side view of an inlet portion of a manifold of a heat exchanger
  • Figure 3 illustrates a perspective view of the inlet portion of the manifold of the heat exchanger showing various dimensions.
  • Figure 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. From the condenser
  • 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. From the evaporator 30, 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).
  • Figure 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.
  • Figure 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 (O 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 o ⁇ flce ) and the external surface area of the distribution insert 32 (A inser t,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 o ⁇ flce ) to the external surface area of the distribution insert 32 (A inser t,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 o ⁇ flce ) and the cross-sectional area of the distribution insert 32 in the plane perpendicular to the axis X and based on the diameter (A insertiCross ).
  • the relationship is defined as a ratio of the total cross-sectional area of all distribution orifices 42 of the distribution insert 32 (A o ⁇ flce ) 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 inser t,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 o ⁇ f lce ) and the axial separation between centers of the distribution orifices 42 of the distribution insert 32 (Lo ⁇ fice).
  • the relationship is defined as the ratio of the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (D o ⁇ flce ) to the axial separation between centers of the distribution orifices 42 of the distribution insert 32 (L o ⁇ f lce ), 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 o ⁇ f lce ) and the external surface area of the distribution insert 32 (A insertiSurf ).
  • 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 o ⁇ f lce ) squared divided by external surface area of the distribution insert 32 (A insertiSurf ).
  • the second design characteristic is defined as the hydraulic diameter of the heat exchange tubes 36 (D tu be) squared divided by the cross- sectional area of the manifold 34 in the plane of the longitudinal axis X (A man ,i ong ).
  • 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 o ⁇ flce ) 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 o ⁇ flce ), 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 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 o ⁇ f lce ), 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 o ⁇ f lce ) squared.
  • the second design characteristic is defined by the length of the distribution insert 32 (L ins ) divided by the 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.

Landscapes

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

Abstract

A heat exchanger includes heat exchange tubes, a manifold, and a distribution insert incorporating 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, the value of which falls within a determined range of values.

Description

DESIGN CHARACTERISTICS FOR HEAT EXCHANGER DISTRIBUTION
INSERT
RELATED APPLICATIONS This application claims priority to United States Provisional Patent Application
Number 61/079,521, which was filed July 10, 2008.
BACKGROUND OF THE INVENTION
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. SUMMARY OF THE INVENTION
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.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 illustrates an exemplary refrigeration system; Figure 2 illustrates a side view of an inlet portion of a manifold of a heat exchanger; and
Figure 3 illustrates a perspective view of the inlet portion of the manifold of the heat exchanger showing various dimensions.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT
Figure 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. In the condenser 24, the refrigerant rejects heat to a secondary fluid. From the condenser
24, 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. In the evaporator 30, the refrigerant accepts heat from another secondary fluid. From the evaporator 30, 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. When the refrigeration system 20 is operating in a cooling mode, the four-way reversing valve 35 directs the refrigerant from the compressor 22 to the condenser 24. When the refrigeration system 20 is operating in a heating mode, 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).
Figure 2 illustrates a portion of the evaporator 30. The evaporator 30 includes a manifold 34. In one example, the manifold 34 is an inlet manifold or an intermediate manifold of the evaporator 30. In the below examples, an inlet manifold of an evaporator 30 is described. In one example, the evaporator 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 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. Additionally, although 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. In one example, 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. For example, 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. Typically, 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.
Figure 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.
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 the distribution insert 32.
Various characteristics of the evaporator 30 are defined as below:
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:
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 (Oman), 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. 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 the distribution orifices 42 of the distribution insert 32 (Aoπflce) 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 the distribution orifices 42 of the distribution insert 32 (Aoπflce) 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 the distribution orifices 42 of the distribution 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 the distribution orifices 42 of the distribution insert 32 (Aoπflce) and the cross-sectional area of the distribution insert 32 in the plane perpendicular to the axis X and based on the diameter (AinsertiCross). The relationship is defined as a ratio of the total cross-sectional area of all distribution orifices 42 of the distribution insert 32 (Aoπflce) to the cross-sectional area of the distribution 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 the distribution orifices 42 of the distribution insert 32 versus the flow momentum through the distribution 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 the distribution orifices 42 of the distribution insert 32 (Doπflce) and the axial separation between centers of the distribution orifices 42 of the distribution insert 32 (Loπfice). The relationship is defined as the ratio of the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (Doπflce) to the axial separation between centers of the distribution orifices 42 of the distribution insert 32 (Loπflce), 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. 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 the distribution orifices 42 of the distribution insert 32 (Doπflce) and the external surface area of the distribution insert 32 (AinsertiSurf). 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 (Doπflce) squared divided by external surface area of the distribution insert 32 (AinsertiSurf). 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,iong). 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. 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 the distribution orifices 42 of the distribution insert 32 (Doπflce) 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 (Doπflce), 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 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. Using Relationship 7, the characteristics of the distribution insert 32 are the hydraulic diameter of the distribution orifices 42 of the distribution insert 32 (Doπflce), 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 the distribution orifices 42 of the distribution insert 32 (Doπflce) squared. The second design characteristic is defined by the length of the distribution insert 32 (Lins) divided by the 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 the manifold 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 the distribution insert 32 compared to the distance across the manifold 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 the distribution insert 32 and the evaporator 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

CLAIMSWhat is claimed is:
1. A heat exchanger comprising: a plurality of heat exchange tubes; a manifold; and a distribution insert at least partially received in the manifold, wherein the distribution insert includes a plurality of orifices that can distribute a fluid into the manifold for distribution into the plurality of heat exchange tubes, wherein at least one design characteristic of the distribution insert and another design characteristic of at least one of the distribution insert, the manifold and the plurality of heat exchange tubes are employed to determine an essential design relationship, and the essential design relationship defines a design parameter with a value that falls within a determined range of values.
2. The heat exchanger as recited in claim 1 wherein the heat exchanger is an evaporator, and the manifold is at least one of an inlet manifold and an intermediate manifold of the evaporator.
3. The heat exchanger as recited in claim 1 wherein the heat exchanger is a condenser or a reheat heat exchanger, and the manifold is an intermediate manifold of the condenser or the reheat heat exchanger.
4. The heat exchanger as recited in claim 1 wherein the heat exchanger is a microchannel heat exchanger.
5. The heat exchanger as recited in claim 1 wherein the essential design relationship is a non-dimensional ratio.
6. The heat exchanger as recited in claim 1 wherein the at least one design characteristic of the distribution insert is one of a length of the distribution insert, a diameter of the distribution insert, a hydraulic diameter of the plurality of orifices of the distribution insert, a separation distance between centers of the plurality of orifices of the distribution insert, a surface area of the distribution insert, a cross-sectional area of the distribution insert, a total cross-sectional area of the plurality of orifices of the distribution insert, and a number of the distribution orifices.
7. The heat exchanger as recited in claim 1 wherein the at least one design characteristic is an inner diameter of the distribution insert and the another design characteristic is an inner diameter of the manifold, and the essential design relationship is defined by a ratio of the inner diameter of the distribution insert to the inner diameter of the manifold, wherein the ratio is squared to define the design parameter.
8. The heat exchanger as recited in claim 7 wherein the range of values for the design parameter is between 0.02 and 0.95.
9. The heat exchanger as recited in claim 1 wherein the another design characteristic is a characteristic of the distribution insert, and the at least one design characteristic is a total cross-sectional area of the plurality of distribution orifices of the distribution insert and an external surface area of the distribution insert, and the essential design relationship is defined by a ratio of the total cross-sectional area of the plurality of distribution orifices of the distribution insert to the external surface area of the distribution insert, wherein the ratio defines the design parameter.
10. The heat exchanger as recited in claim 9 wherein the range of values for the design parameter is between 50 and 5000.
11. The heat exchanger as recited in claim 1 wherein the another design characteristic is a characteristic of the distribution insert, and the at least one design characteristic is a total cross-sectional area of the plurality of distribution orifices of the distribution insert and a cross-sectional area of the distribution insert, and the essential design relationship is defined by a ratio of the total cross-sectional area of the plurality of distribution orifices of the distribution insert to the cross-sectional area of the distribution insert, wherein the ratio defines the design parameter.
12. The heat exchanger as recited in claim 11 wherein the range of values for the design parameter is between 0.01 to 100.
13. The heat exchanger as recited in claim 1 wherein the another design characteristic is a characteristic of the distribution insert, and the at least one design characteristic is a hydraulic diameter of the plurality of distribution orifices of the distribution insert and a separation between centers of the plurality of distribution orifices of the distribution insert, and the essential design relationship is defined by a ratio of the hydraulic diameter of the plurality of the distribution orifices of the distribution insert to the separation between the centers of the plurality of distribution orifices of the distribution insert, wherein the ratio defines the design parameter.
14. The heat exchanger as recited in claim 13 wherein the range of values for the design parameter is between 0.01 to 35.
15. The heat exchanger as recited in claim 1 wherein the at least one design characteristic is a hydraulic diameter of the plurality of distribution orifices of the distribution insert and a surface area of the distribution insert, the another design characteristic is a hydraulic diameter of the plurality of heat exchange tubes and a cross- sectional area of the manifold, and the essential design relationship is defined as a first design characteristic divided by a second design characteristic, wherein the first design characteristic is a ratio of the hydraulic diameter of the plurality of distribution orifices of the distribution insert squared to the external surface area of the distribution insert, and the second design characteristic is a ratio of the hydraulic diameter of the plurality of heat exchange tubes squared to the cross-sectional area of the manifold, and the ratio of the first design characteristic to the second design characteristic defines the design parameter.
16. The heat exchanger as recited in claim 15 wherein the range of values for the design parameter is 0.01 to 25.
17. The heat exchanger as recited in claim 1 wherein the at least one design characteristic is a hydraulic diameter of the plurality of distribution orifices of the distribution insert and a number of the plurality of distribution orifices of the distribution insert, the another design characteristic is a number of the plurality of heat exchange tubes and a hydraulic diameter of the plurality of heat exchange tubes, and the essential design relationship is defined as a first design characteristic divided by a second design characteristic, wherein the first design characteristic is defined by the number of the plurality of distribution orifices of the distribution insert multiplied by the hydraulic diameter of the plurality of distribution orifices of the distribution insert, which is then squared, and the second design characteristic is the number of the plurality of heat exchange tubes multiplied by the hydraulic diameter of the plurality of heat exchange tubes, which is then squared, and the ratio of the first design characteristic to the second design characteristic defines the design parameter.
18. The heat exchanger as recited in claim 17 wherein the range of values for the design parameter is 0.01 to 100.
19. The heat exchanger as recited in claim 1 wherein the at least one design characteristic is a hydraulic diameter of the plurality of distribution orifices of the distribution insert, a length of the distribution insert and an inner diameter of the distribution insert, the another design characteristic is a diameter of the manifold, and the essential design relationship is defined as a first design characteristic divided by a second design characteristic, wherein the first design characteristic is the diameter of the manifold divided by the hydraulic diameter of the plurality of distribution orifices of the distribution insert squared divided by the length of the distribution insert divided by the diameter of the distribution insert squared, and the ratio of the first design characteristic to the second design characteristic defines the design parameter.
20. The heat exchanger as recited in claim 19 wherein the range of values for the design parameter is 0.01 to 20.
21. The heat exchanger as recited in claim 1 wherein the at least one design characteristic is a length of the distribution insert, the another design characteristic is an inner diameter of the manifold, and the essential design relationship is defined as a ratio of the inner diameter of the manifold to the length of the distribution insert, wherein the ratio defines the design parameter.
22. The heat exchanger as recited in claim 21 wherein the range of values for the design parameter is 1 to 1000.
23. A method of designing a heat exchanger, the method comprising the steps of: determining a range of values; selecting at least one design characteristic of a distribution insert, wherein the distribution insert includes a plurality of orifices, at least a portion of the distribution insert is received in a manifold, and a fluid can be communicated through the plurality of orifices and into the manifold for distribution into a plurality of heat exchange tubes; and determining an essential design relationship between the at least one design characteristic of the distribution insert and another design characteristic of at least one of the distribution insert, the manifold and the plurality of heat exchange tubes, wherein the essential design relationship defines a design parameter with a value that falls within the range of values.
24. The method as recited in claim 23 wherein the essential design relationship is a non-dimensional ratio.
25. The method as recited in claim 23 wherein the at least one design characteristic of the distribution insert is one of a length of the distribution insert, a diameter of the distribution insert, a hydraulic diameter of the plurality of orifices of the distribution insert, a separation distance between centers of the plurality of orifices of the distribution insert, a surface area of the distribution insert, a cross-sectional area of the distribution insert, a total cross-sectional area of the plurality of orifices of the distribution insert, and a number of the distribution orifices.
EP09794882.2A 2008-07-10 2009-06-12 Design characteristics for heat exchanger distribution insert Withdrawn EP2310790A4 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US7952108P 2008-07-10 2008-07-10
PCT/US2009/047141 WO2010005676A2 (en) 2008-07-10 2009-06-12 Design characteristics for heat exchanger distribution insert

Publications (2)

Publication Number Publication Date
EP2310790A2 true EP2310790A2 (en) 2011-04-20
EP2310790A4 EP2310790A4 (en) 2014-10-08

Family

ID=41507648

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09794882.2A Withdrawn EP2310790A4 (en) 2008-07-10 2009-06-12 Design characteristics for heat exchanger distribution insert

Country Status (4)

Country Link
US (1) US20110127023A1 (en)
EP (1) EP2310790A4 (en)
CN (1) CN102089612A (en)
WO (1) WO2010005676A2 (en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011133216A (en) * 2009-11-27 2011-07-07 Toshiba Corp Heat exchanger
US20110290465A1 (en) * 2010-06-01 2011-12-01 Delphi Technologies, Inc. Orientation insensitive refrigerant distributor tube
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
WO2013161038A1 (en) * 2012-04-26 2013-10-31 三菱電機株式会社 Heat exchanger and heat exchange method
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
DE102012217340A1 (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
US9746255B2 (en) * 2012-11-16 2017-08-29 Mahle International Gmbh Heat pump heat exchanger having a low pressure drop distribution tube
KR20140116626A (en) 2013-03-25 2014-10-06 엘지전자 주식회사 A heat exchanger
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
US10563895B2 (en) 2016-12-07 2020-02-18 Johnson Controls Technology Company 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
DE102019002738A1 (en) * 2019-04-15 2020-10-15 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
US11408688B2 (en) * 2020-06-17 2022-08-09 Mahle International Gmbh Heat exchanger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040026072A1 (en) * 2002-08-06 2004-02-12 Visteon Global Technologies, Inc. Serrated tube-flow distributor
US20050132744A1 (en) * 2003-12-22 2005-06-23 Hussmann Corporation Flat-tube evaporator with micro-distributor
WO2006083426A1 (en) * 2005-02-02 2006-08-10 Carrier Corporation Tube inset and bi-flow arrangement for a header of a heat pump
US20070039724A1 (en) * 2005-08-18 2007-02-22 Trumbower Michael W Evaporating heat exchanger
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 (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2534442A1 (en) * 1975-08-01 1977-02-10 Linde Ag HEAT EXCHANGER IN SPIRAL SHEET METAL DESIGN
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
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
JPH08128793A (en) * 1994-10-28 1996-05-21 Toshiba Corp Heat transfer tube with internal fins and manufacture thereof
JPH09166368A (en) * 1995-12-14 1997-06-24 Sanden Corp Heat exchanger
DE10212249A1 (en) * 2002-03-20 2003-10-02 Behr Gmbh & Co Heat exchanger and cooling system
US7281387B2 (en) * 2004-04-29 2007-10-16 Carrier Commercial Refrigeration Inc. Foul-resistant condenser using microchannel tubing
JP4199719B2 (en) * 2004-10-18 2008-12-17 株式会社興研 Automatic lifting control method and automatic lifting control system for mobile power generator
US7806171B2 (en) * 2004-11-12 2010-10-05 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
US7398819B2 (en) * 2004-11-12 2008-07-15 Carrier Corporation Minichannel heat exchanger with restrictive inserts
US20060101850A1 (en) * 2004-11-12 2006-05-18 Carrier Corporation Parallel flow evaporator with shaped manifolds
JP2007178048A (en) * 2005-12-27 2007-07-12 Calsonic Kansei Corp Header tank for heat exchanger
US7484555B2 (en) * 2006-07-25 2009-02-03 Delphi Technologies, Inc. Heat exchanger assembly
US20080023185A1 (en) * 2006-07-25 2008-01-31 Henry Earl Beamer Heat exchanger assembly

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040026072A1 (en) * 2002-08-06 2004-02-12 Visteon Global Technologies, Inc. Serrated tube-flow distributor
US20050132744A1 (en) * 2003-12-22 2005-06-23 Hussmann Corporation Flat-tube evaporator with micro-distributor
WO2006083426A1 (en) * 2005-02-02 2006-08-10 Carrier Corporation Tube inset and bi-flow arrangement for a header of a heat pump
US20070039724A1 (en) * 2005-08-18 2007-02-22 Trumbower Michael W Evaporating heat exchanger
WO2008048251A2 (en) * 2006-10-13 2008-04-24 Carrier Corporation Method and apparatus for improving distribution of fluid in a heat exchanger

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2010005676A2 *

Also Published As

Publication number Publication date
US20110127023A1 (en) 2011-06-02
CN102089612A (en) 2011-06-08
WO2010005676A2 (en) 2010-01-14
EP2310790A4 (en) 2014-10-08
WO2010005676A3 (en) 2010-03-25

Similar Documents

Publication Publication Date Title
EP2310790A2 (en) Design characteristics for heat exchanger distribution insert
US7806171B2 (en) Parallel flow evaporator with spiral inlet manifold
AU2006211653B2 (en) Parallel flow heat exchanger for heat pump applications
EP2082181B1 (en) Parallel flow heat exchanger
KR100830301B1 (en) Heat exchanger with multiple stage fluid expansion in header
US8333088B2 (en) Heat exchanger design for improved performance and manufacturability
US20080105420A1 (en) Parallel Flow Heat Exchanger With Crimped Channel Entrance
JP4358981B2 (en) Air conditioning condenser
WO2006055297A2 (en) Parallel flow evaporator with variable channel insertion depth
US20100071392A1 (en) Parallel flow evaporator with shaped manifolds
US10302341B2 (en) Ejector-integrated heat exchanger
WO2021050426A1 (en) Heat exchanger assembly
WO2013184522A1 (en) Heat exchanger, and method of distributing refrigerant therein
JP2002228299A (en) Composite heat exchanger
CN113646597B (en) Refrigeration cycle device
US20220099343A1 (en) Heat exchanger and refrigeration cycle apparatus
CN115111953A (en) Micro-channel heat exchanger
WO2019142444A1 (en) Heat exchanger

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20101203

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA RS

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20140910

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 9/02 20060101ALI20140904BHEP

Ipc: F25B 39/02 20060101ALI20140904BHEP

Ipc: F28F 9/24 20060101ALI20140904BHEP

Ipc: F28F 9/22 20060101AFI20140904BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20160115