EP3336477B1 - Flow deviator in end tanks of heat exchangers for thermal stress reduction - Google Patents

Flow deviator in end tanks of heat exchangers for thermal stress reduction Download PDF

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Publication number
EP3336477B1
EP3336477B1 EP16398010.5A EP16398010A EP3336477B1 EP 3336477 B1 EP3336477 B1 EP 3336477B1 EP 16398010 A EP16398010 A EP 16398010A EP 3336477 B1 EP3336477 B1 EP 3336477B1
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EP
European Patent Office
Prior art keywords
flow
header tank
heat exchanger
fluid
header
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Active
Application number
EP16398010.5A
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German (de)
French (fr)
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EP3336477A1 (en
Inventor
Luís Neves
Eduardo Pimentel
João Carvalho
Elisabete Nunes
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.)
Joao de Deus e Filhos SA
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Joao de Deus e Filhos SA
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Priority to EP16398010.5A priority Critical patent/EP3336477B1/en
Publication of EP3336477A1 publication Critical patent/EP3336477A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • F28F9/0226—Header boxes formed by sealing end plates into covers with resilient gaskets
    • 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
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/10—Safety or protection arrangements; Arrangements for preventing malfunction for preventing overheating, e.g. heat shields

Definitions

  • the present invention relates generally to a heat exchanger, according to claim 1, particularly for automotive applications.
  • Heat exchangers are subjected to varying temperatures, sometimes quick temperature changes occur. These thermal loads affect the durability of the part.
  • An aim of the present invention is to provide a measure to reduce thermal stresses in particular areas of heat exchangers.
  • the invention proposes a heat exchanger according to claim 1.
  • the flow deviating projection is a feature added to the geometry of the fluid inlet chamber of the header tank. This feature reduces the mass flow of a fluid, and therefore the heat transfer on specific areas of the core, and therefore involves a thermal stress reduction on these areas.
  • Flow deviating features may be applied to different configurations of heat exchangers, such as U-flow heat exchangers, I-flow heat exchangers or multi-flow heat-exchangers.
  • FIG. 1 shows a U-flow heat exchanger, globally designated with 1, comprising a inlet/outlet header tank 10 and a return tank 20. Each tank 10, 20 is joined to a respective header plate 11, 21.
  • the heat exchanger 1 further comprises a core 30 comprising a plurality of parallel flat tubes 31 extending between the header tanks 10, 20. Each tube 31 has opposite ends inserted into openings or slots formed in one or the other of the header plate 11, 12, respectively.
  • the inlet/outlet header tank 10 comprises a fluid inlet duct 41 and a fluid outlet duct 42.
  • a fluid for example air, water, glycol, ecc., is designed to flow from the fluid inlet duct 41 in the inlet/outlet tank 10 to the return tank 20 through a first section of the core 30, and then flow back to the fluid outlet duct 42 in inlet/outlet tank 10 through a second section of the core 30, as indicated by the arrows in Figure 1 .
  • a further fluid for example air, is designed to flow perpendicularly to the core 30 and through gaps between the tubes 31, and exchange heat with the fluid flowing into the tubes 31.
  • the inlet/outlet header tank 10 comprises a plurality of external walls 10a, 10b, 10c, 10d.
  • the inlet/outlet header tank 10 cooperates with its respective header plate 11 to form a fluid inlet chamber 43 and a fluid outlet chamber 44, communicating with the fluid inlet duct 41 and the fluid outlet duct 42, respectively.
  • a separation wall 10e extending between opposite external walls 10a, 10c, is formed within the inlet/outlet header tank 10 to fluidically separate the fluid inlet chamber 43 from the fluid outlet chamber.
  • the header plate 11 is joined to the inlet/outlet header tank 10 at the level of a section 19 of the latter, which is indicated herein as interface section.
  • This interface section 19 has a hollow, substantially rectangular cross-section defined by the external walls 10a, 10b, 10c, 10d of the inlet/outlet header tank.
  • a portion of the interface section 19 having a hollow, substantially rectangular cross-section defined by the external walls 10a, 10c, 10d and the separation wall 10e can be identified as well in Figure 2 .
  • two flow deviating projections 51, 52 protruding into the fluid inlet chamber 43, are formed in respective corners between the separation wall 10e and the external walls 10a and 10c, respectively, at the interface section 19 of the inlet/outlet header 10.
  • the flow deviating projections 51, 52 are hollow projections with cavities 51a, 52a, and are formed as 1 ⁇ 4 circle arc-shaped walls protruding from the separation wall 10e and the external walls 10a and 10c, respectively.
  • the flow deviating projections can also be solid structures, i.e. without cavities therein.
  • the flow deviating projections 51, 52 are dimensioned to cover - when viewed in plan view - respective end parts B1, B2 of the cross-section of at least one tube 31 adjacent to the corners at which the flow deviating projections 51, 52 are located. In this way, fluid flow to the tube(s) 31 located at positions axially aligned with the end parts B1, B2 is restricted.
  • the dashed line in Fig. 9 represents the position of the partition wall 10e of the header tank 10.
  • Figure 8 shows that the fluid flow velocity in a tube area L located below the flow deviating projection 51 is generally lower than the fluid flow velocities in tube areas H1 and H2 which does not have flow deviating features above them. Reducing fluid flow velocity entails heat transfer reduction in the involved areas, entailing thereby a reduction of the local thermal stresses.
  • FIG. 10 shows a I-flow heat exchanger, globally designated with 1', comprising an inlet header tank 10' and an outlet header tank 20'. Each tank 10', 20' is joined to a respective header plate 11', 21'.
  • the heat exchanger 1' further comprises a core 30' comprising a plurality of parallel flat tubes 31' extending between the header tanks 10', 20'. Each tube 31' has opposite ends inserted into openings or slots formed in one or the other of the header plate 11', 12', respectively.
  • the inlet header tank 10' comprises a fluid inlet duct 41' and the outlet header tank 20' comprises a fluid outlet duct 42'.
  • a fluid for example air, water, glycol, ecc., is designed to flow from the fluid inlet duct 41' in the inlet tank 10' to the fluid outlet duct 42' in the outlet header tank 20' through the core 30', as indicated by the arrow in Figure 10 .
  • a further fluid for example air, is designed to flow perpendicularly to the core 30' and through gaps between the tubes 31', and exchange heat with the fluid flowing into the tubes 31'.
  • the inlet header tank 10' comprises a plurality of external walls 10a', 10b', 10c', 10d'.
  • the inlet header tank 10' cooperates with its respective header plate 11' to form a fluid inlet chamber 43' communicating with the fluid inlet duct 41'.
  • the header plate 11' is joined to the inlet header tank 10' at the level of a section 19' of the latter, which is indicated herein as interface section.
  • This interface section 19' has a hollow, substantially rectangular cross-section defined by the external walls 10a', 10b', 10c', 10d' of the inlet header tank.
  • At least one flow deviating projection 51 protruding into the fluid inlet chamber 43' can be formed in at least one respective corner between adjacent external walls 10a' and 10b', 10b' and 10c', 10c' and 10d', and 10d', at the interface section 19' of the inlet header 10'.
  • These flow deviating projections 51' can be hollow projections with cavities, and be formed as 1 ⁇ 4 circle arc-shaped walls protruding from the external walls adjacent thereto. However, other shapes are possible.
  • the flow deviating projections can also be solid structures, i.e. without cavities therein.
  • the flow deviating projections 51 are dimensioned to cover - when viewed in plan view - respective end parts B1', B2', B3', B4' of the cross-section of at least one tube 31' adjacent to the corners at which the flow deviating projections 51' are located. In this way, fluid flow to the tube(s) 31' located at positions axially aligned with the end parts B1', B2', B3', B4' is restricted.
  • flow deviating projections can be used also in multi-flow heat exchangers, i.e. heat exchangers having different core sections, in which a fluid can make subsequent passages from one header tank to the other, and vice versa.
  • header tanks are divided in different fluid flow chambers by means of separation walls, similarly to the U-flow heat exchanger described above.
  • one or two flow deviating projections can be formed in respective corners between a separation wall and external walls of the header tank, in the hot (inlet) chamber of the header tank.

Description

  • The present invention relates generally to a heat exchanger, according to claim 1, particularly for automotive applications.
  • Heat exchangers are subjected to varying temperatures, sometimes quick temperature changes occur. These thermal loads affect the durability of the part.
  • This problem is especially problematic for U-flow heat exchangers on the area that separates the inlet (hot) and outlet (cold) flows. Thermal stresses can lead with time to the formation of failures such as leaks.
  • US 2015/211812 A1 discloses a heat exchanger according to the preamble of claim 1.
  • An aim of the present invention is to provide a measure to reduce thermal stresses in particular areas of heat exchangers.
  • Accordingly, the invention proposes a heat exchanger according to claim 1.
  • The flow deviating projection is a feature added to the geometry of the fluid inlet chamber of the header tank. This feature reduces the mass flow of a fluid, and therefore the heat transfer on specific areas of the core, and therefore involves a thermal stress reduction on these areas.
  • Flow deviating features may be applied to different configurations of heat exchangers, such as U-flow heat exchangers, I-flow heat exchangers or multi-flow heat-exchangers.
  • Some preferred, but non-limiting, embodiments of the invention will now be described, with reference to the attached drawings, in which:
    • Figure 1 is a front elevation view showing a U-flow heat exchanger;
    • Figure 2 is a plan view of a header tank of the heat exchanger of Figure 1;
    • Figure 3 is a perspective view showing a detail of the header tank of Figure 2;
    • Figure 4 is a front elevation view of the header tank of Figure 2;
    • Figure 5 is a cross-sectioned view taken along the line V-V of Figure 4;
    • Figure 6 is a cross-sectioned view taken along the line VI-VI of Figure 5;
    • Figure 7 is a cross-sectioned view taken along the line VII-VII of Figure 5;
    • Figure 8 is a diagram showing fluid velocity distribution at the cross-section of Figure 7;
    • Figure 9 is a plan view showing a header plate of the heat exchanger of Figure 1;
    • Figure 10 is a front elevation view showing a I-flow heat exchanger;
    • Figure 11 is a plan view showing a header tank of the heat exchanger of Figure 10; and
    • Figure 12 is a plan view showing a header plate of the heat exchanger of Figure 10.
  • Figure 1 shows a U-flow heat exchanger, globally designated with 1, comprising a inlet/outlet header tank 10 and a return tank 20. Each tank 10, 20 is joined to a respective header plate 11, 21. The heat exchanger 1 further comprises a core 30 comprising a plurality of parallel flat tubes 31 extending between the header tanks 10, 20. Each tube 31 has opposite ends inserted into openings or slots formed in one or the other of the header plate 11, 12, respectively.
  • The inlet/outlet header tank 10 comprises a fluid inlet duct 41 and a fluid outlet duct 42. A fluid, for example air, water, glycol, ecc., is designed to flow from the fluid inlet duct 41 in the inlet/outlet tank 10 to the return tank 20 through a first section of the core 30, and then flow back to the fluid outlet duct 42 in inlet/outlet tank 10 through a second section of the core 30, as indicated by the arrows in Figure 1. A further fluid, for example air, is designed to flow perpendicularly to the core 30 and through gaps between the tubes 31, and exchange heat with the fluid flowing into the tubes 31.
  • With reference also to Figure 2, the inlet/outlet header tank 10 comprises a plurality of external walls 10a, 10b, 10c, 10d. The inlet/outlet header tank 10 cooperates with its respective header plate 11 to form a fluid inlet chamber 43 and a fluid outlet chamber 44, communicating with the fluid inlet duct 41 and the fluid outlet duct 42, respectively. A separation wall 10e, extending between opposite external walls 10a, 10c, is formed within the inlet/outlet header tank 10 to fluidically separate the fluid inlet chamber 43 from the fluid outlet chamber.
  • The header plate 11 is joined to the inlet/outlet header tank 10 at the level of a section 19 of the latter, which is indicated herein as interface section. This interface section 19 has a hollow, substantially rectangular cross-section defined by the external walls 10a, 10b, 10c, 10d of the inlet/outlet header tank. A portion of the interface section 19 having a hollow, substantially rectangular cross-section defined by the external walls 10a, 10c, 10d and the separation wall 10e can be identified as well in Figure 2.
  • With reference also to Figures 3 to 7, two flow deviating projections 51, 52, protruding into the fluid inlet chamber 43, are formed in respective corners between the separation wall 10e and the external walls 10a and 10c, respectively, at the interface section 19 of the inlet/outlet header 10. In the illustrated embodiment, the flow deviating projections 51, 52 are hollow projections with cavities 51a, 52a, and are formed as ¼ circle arc-shaped walls protruding from the separation wall 10e and the external walls 10a and 10c, respectively. However, other shapes are possible. Furthermore, the flow deviating projections can also be solid structures, i.e. without cavities therein.
  • With reference also to Figures 8 and 9, the flow deviating projections 51, 52 are dimensioned to cover - when viewed in plan view - respective end parts B1, B2 of the cross-section of at least one tube 31 adjacent to the corners at which the flow deviating projections 51, 52 are located. In this way, fluid flow to the tube(s) 31 located at positions axially aligned with the end parts B1, B2 is restricted. The dashed line in Fig. 9 represents the position of the partition wall 10e of the header tank 10.
  • Reduction of fluid flow in the tubes(s) 31 located on the hot side of the heat exchanger, close to the interface between hot side (first section) and cold side (second section) of the core, entails a reduction of the local thermal stresses. In fact, it has been measured that the most severe temperature gradients are found in areas located at the interface between the hot side and the cold side, close to the inlet/outlet header tank 10'. Placing flow deviating projections 51, 52 at the corners of the inlet section of the inlet/outlet header tank 10', close to the interface between hot side and cold side, will reduce fluid flow velocity in these areas. Figure 8 shows that the fluid flow velocity in a tube area L located below the flow deviating projection 51 is generally lower than the fluid flow velocities in tube areas H1 and H2 which does not have flow deviating features above them. Reducing fluid flow velocity entails heat transfer reduction in the involved areas, entailing thereby a reduction of the local thermal stresses.
  • Figure 10 shows a I-flow heat exchanger, globally designated with 1', comprising an inlet header tank 10' and an outlet header tank 20'. Each tank 10', 20' is joined to a respective header plate 11', 21'. The heat exchanger 1' further comprises a core 30' comprising a plurality of parallel flat tubes 31' extending between the header tanks 10', 20'. Each tube 31' has opposite ends inserted into openings or slots formed in one or the other of the header plate 11', 12', respectively.
  • The inlet header tank 10' comprises a fluid inlet duct 41' and the outlet header tank 20' comprises a fluid outlet duct 42'. A fluid, for example air, water, glycol, ecc., is designed to flow from the fluid inlet duct 41' in the inlet tank 10' to the fluid outlet duct 42' in the outlet header tank 20' through the core 30', as indicated by the arrow in Figure 10. A further fluid, for example air, is designed to flow perpendicularly to the core 30' and through gaps between the tubes 31', and exchange heat with the fluid flowing into the tubes 31'.
  • With reference also to Figure 11, the inlet header tank 10' comprises a plurality of external walls 10a', 10b', 10c', 10d'. The inlet header tank 10' cooperates with its respective header plate 11' to form a fluid inlet chamber 43' communicating with the fluid inlet duct 41'.
  • The header plate 11' is joined to the inlet header tank 10' at the level of a section 19' of the latter, which is indicated herein as interface section. This interface section 19' has a hollow, substantially rectangular cross-section defined by the external walls 10a', 10b', 10c', 10d' of the inlet header tank.
  • With reference also to Figure 11, at least one flow deviating projection 51 (sketched with dashed lines in Fig. 11) protruding into the fluid inlet chamber 43' can be formed in at least one respective corner between adjacent external walls 10a' and 10b', 10b' and 10c', 10c' and 10d', and 10d', at the interface section 19' of the inlet header 10'. These flow deviating projections 51' can be hollow projections with cavities, and be formed as ¼ circle arc-shaped walls protruding from the external walls adjacent thereto. However, other shapes are possible. Furthermore, the flow deviating projections can also be solid structures, i.e. without cavities therein.
  • With reference also to Figure 12, the flow deviating projections 51 are dimensioned to cover - when viewed in plan view - respective end parts B1', B2', B3', B4' of the cross-section of at least one tube 31' adjacent to the corners at which the flow deviating projections 51' are located. In this way, fluid flow to the tube(s) 31' located at positions axially aligned with the end parts B1', B2', B3', B4' is restricted.
  • Placing flow deviating projections 51' at the corners of the inlet section header tank 10' has similar effects on reduction of local thermal stresses as explained in connection with Figure 8 above.
  • Furthermore, flow deviating projections can be used also in multi-flow heat exchangers, i.e. heat exchangers having different core sections, in which a fluid can make subsequent passages from one header tank to the other, and vice versa. In these heat exchangers header tanks are divided in different fluid flow chambers by means of separation walls, similarly to the U-flow heat exchanger described above. Analogously to the U-flow heat exchanger, one or two flow deviating projections can be formed in respective corners between a separation wall and external walls of the header tank, in the hot (inlet) chamber of the header tank.

Claims (3)

  1. A heat exchanger comprising:
    a core (30; 30') comprising a plurality of parallel tubes (31; 31'),
    a header plate (11; 11') having a plurality of openings, into which ends of the tubes (31; 31') are inserted, and
    a header tank (10; 10') joined to the header plate (11; 11') and cooperating with the header plate (11; 11') to form a fluid inlet chamber (43; 43'), said header tank (10; 10') comprising at least one fluid inlet duct (41; 41') communicating with the fluid inlet chamber (43; 43') and an interface section (19; 19') at which the header tank (10; 10') is joined to the header plate (11; 11'), wherein the interface section (19; 19') has a hollow, substantially rectangular cross-section defined by a plurality of walls (10a, 10e, 10c, 10d; 10a', 10b', 10c', 10d') of the header tank (10; 10'),
    characterised in that at least one flow deviating projection (51, 52; 51'), protruding into the fluid inlet chamber (43; 43'), is formed on at least one corner between adjacent walls of the header tank (10; 10') at the interface section (19; 19') thereof, said flow deviating projection (51, 52; 51') restricting fluid flow to at least one tube (31; 31') of the core (30; 30') adjacent to said corner.
  2. A heat exchanger according to claim 1, wherein the heat exchanger is a I-flow heat exchanger, and said at least one flow deviating projection (51') is formed on at least one corner of the fluid inlet chamber (43') between adjacent external walls (10a', 10b', 10c', 10d') of the header tank (10').
  3. A heat exchanger according to claim 1, wherein the heat exchanger is a U-flow or multi-flow heat exchanger, and said at least one flow deviating projection (51, 52) is formed on at least one corner of the fluid inlet chamber (43) between an external wall (10a, 10c) of the header tank (10) and a separation wall (10e) between the fluid inlet chamber (43) and an adjacent fluid flow chamber (44) of the header tank (10).
EP16398010.5A 2016-12-13 2016-12-13 Flow deviator in end tanks of heat exchangers for thermal stress reduction Active EP3336477B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16398010.5A EP3336477B1 (en) 2016-12-13 2016-12-13 Flow deviator in end tanks of heat exchangers for thermal stress reduction

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16398010.5A EP3336477B1 (en) 2016-12-13 2016-12-13 Flow deviator in end tanks of heat exchangers for thermal stress reduction

Publications (2)

Publication Number Publication Date
EP3336477A1 EP3336477A1 (en) 2018-06-20
EP3336477B1 true EP3336477B1 (en) 2020-05-27

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EP16398010.5A Active EP3336477B1 (en) 2016-12-13 2016-12-13 Flow deviator in end tanks of heat exchangers for thermal stress reduction

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Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7152669B2 (en) * 2003-10-29 2006-12-26 Delphi Technologies, Inc. End cap with an integral flow diverter
SE528412C2 (en) * 2005-03-15 2006-11-07 Scania Cv Ab Cooling device in which a first tank is provided with outer surface magnifying elements and an inner field-conducting element
BR102013014855B1 (en) * 2013-06-13 2020-12-01 Valeo Sistemas Automotivos Ltda vehicle heat exchanger
US20150211812A1 (en) * 2014-01-28 2015-07-30 Halla Visteon Climate Control Corp. Heat exchanger inlet tank with inmolded inlet radius feature

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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