Heat-radiating system

Patent metadata

Field	Value
Publication number	US-2016231069-A1
Application number	US-201315026055-A
Country	US
Kind code	A1
Filing date	Oct 2, 2013
Priority date	Oct 2, 2013
Publication date	Aug 11, 2016
Grant date	—

Abstract

The heat-radiating system which radiates heat by heat exchange between a substrate 22 and cooling fluid. The heat-radiating system has a cooling structure that includes a vortex flow generating portion C 1 on the surface of the substrate 22 in contact with the cooling fluid. The vortex flow generating portion C 1 is composed of a plurality of recesses 22 b that extend in the direction β intersecting the flow direction of the cooling fluid and causes a vortex flow depending on the flow condition of the cooling fluid. The recess depth H of the vortex flow generating portion and the laminar sub-layer thickness δ b near the wall surface satisfy the relation of H>δ b =63.5/(Re 7/8 )×d (where
Re is the Reynolds number, d is the characteristic length, and the Reynolds number is Re=ud/v where v is the kinematic viscosity of the cooling fluid, u is the flow velocity of the cooling fluid and d is the characteristic length), and operation of the heat radiating system is controlled such that the flow conditions of the cooling fluid fall within the range in which the relation of u/v≦206×d 1/7 (where u, v and d are as defined above) satisfied.

First claim

1 .- 5 . (canceled)

6 . A heat-radiating system that radiates heat by heat exchange between a substrate and a cooling fluid, comprising:
a cooling structure comprising a vortex flow generating portion on a surface of the substrate that is in contact with the cooling fluid, in which the vortex flow generating portion is constituted by a plurality of recesses that extend in a direction intersecting the flow direction of the cooling fluid and cause a vortex flow depending on a flow condition of the cooling fluid,
wherein a depth H of a recess of the vortex flow generating portion and a laminar sub-layer thickness δ b near a wall surface satisfy the following relation (1):
H>δ b =63.5/( Re 7/8 )×d  (1)

where Re is a Reynolds number, d is a characteristic length, and the Reynolds number is defined as Re=ud/v where v is a kinematic viscosity of the cooling fluid, u is a flow velocity of the cooling fluid and d is the characteristic length, and
operation of the heat-radiating system is controlled such that the flow condition of the cooling fluid falls within a range in which the following relation (2) is satisfied:
u/v≦ 206× d 1/7   (2)

where u, v and d are as defined above.

7 . The heat-radiating system according to claim 6 , wherein the flow condition of the cooling fluid falls within a range in which the following formula (3) is satisfied:
u/v≦ 455× d 1/7   (3)

where u, v and d are as defined above.

8 . The heat-radiating system according to claim 6 , wherein, in a condition that requires heat radiation, the kinematic viscosity and the flow velocity are determined so that a value W + =Wu τ /v fall within the range of from 25 to 300, the value W + being a nondimensionalized value of an opening width W of the recess of the vortex flow generating portion and is obtained by using a shear velocity u τ =(τ ω /ρ) 1/2 calculated from a shearing stress τ ω and a fluid density p, an empirical formula of pipe friction coefficient Cf=τ ω /(0.5 ρu 2 )=0.73 Re −0.25 calculated from the flow velocity u, a density ρ and the Reynolds number Re, and the kinematic viscosity v.

9 . The heat-radiating system according to claim 7 , wherein, in a condition that requires heat radiation, the kinematic viscosity and the flow velocity are determined so that a value W + =Wu τ /v fall within the range of from 25 to 300, the value W + being a nondimensionalized value of an opening width W of the recess of the vortex flow generating portion and is obtained by using a shear velocity u τ =(τ ω /ρ) 1/2 calculated from a shearing stress τ ω and a fluid density ρ, an empirical formula of pipe friction coefficient Cf=τ ω /(0.5 ρu 2 )= 0 . 73 Re −0.25 calculated from the flow velocity u, a density ρ and the Reynolds number Re, and the kinematic viscosity v.

10 . The heat-radiating system according to claim 6 , wherein a maximum depth H of the recess is small compared to a distance X from an opening plane of the recess to an opposing channel surface.

11 . The heat-radiating system according to claim 10 , wherein a characteristic length d=4 A/L is equal to or greater than 0.004, the characteristic length being calculated from a minimum channel cross-sectional area A of a channel cross-section perpendicular to the flow direction of the cooling fluid and a maximum wetted perimeter L.

12 . The heat-radiating system according to claim 7 , wherein a maximum depth H of the recess is small compared to a distance X from an opening plane of the recess to an opposing channel surface.

13 . The heat-radiating system according to claim 8 , wherein a maximum depth H of the recess is small compared to a distance X from an opening plane of the recess to an opposing channel surface.

14 . The heat-radiating system according to claim 9 , wherein a maximum depth H of the recess is small compared to a distance X from an opening plane of the recess to an opposing channel surface.

15 . The heat-radiating system according to claim 12 , wherein a characteristic length d=4 A/L is equal to or greater than 0.004, the characteristic length being calculated from a minimum channel cross-sectional area A of a channel cross-section perpendicular to the flow direction of the cooling fluid and a maximum wetted perimeter L.

16 . The heat-radiating system according to claim 13 , wherein a characteristic length d=4 A/L is equal to or greater than 0.004, the characteristic length being calculated from a minimum channel cross-sectional area A of a channel cross-section perpendicular to the flow direction of the cooling fluid and a maximum wetted perimeter L.

17 . The heat-radiating system according to claim 14 , wherein a characteristic length d=4 A/L is equal to or greater than 0.004, the characteristic length being calculated from a minimum channel cross-sectional area A of a channel cross-section perpendicular to the flow direction of the cooling fluid and a maximum wetted perimeter L.

Assignees

• Nissan Motor

Inventors

• Koizuka Yousuke
• Nakayama Tatsuomi

Classifications

• H10W40/47 Primary

  by flowing liquids, e.g. forced water cooling · CPC title

• F28F13/12 Primary

  by creating turbulence, e.g. by stirring, by increasing the force of circulation (F28F13/08 takes precedence) · CPC title

• F15D1/009

  by means of vortex rings · CPC title

• F28D15/00

  Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls {; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies (F28D17/00, F28D19/00, F28D20/00 take precedence)} · CPC title