Distributor for plate type heat exchangers having end headers

Claim 2

An elongated plate type heat exchanger core comprising: a plurality of plates of similar generally rectangular peripheral configuration contraposed in spaced substantially parallel relationship wherein the distances between adjacent plates individually are substantially less than the width of said plates thereby defining a plurality of relatively thin spatial layers therebetween; sealing means sealingly bridging between and extending along the margins of adjacent plates whereby said spatial layers are enclosed to define a plurality of elongated passages each having a thickness less than its width and a width less than its length; means defining a port having a face substantially normal to the longitudinal axis of said core communicating with one of said passages; a corrugated fin fluid distributor disposed in said one passage between said port face and a plane substantially normal to said longitudinal axis traversing said core; said distributor including a first generally triangular port portion of corrugated first fin material having an edge of its triangular configuration abutting said port face and the apex opposite said edge coinciding with said plane and at least a second portion of corrugated second fin material disposed in said pasSage laterally of said first triangular port portion between said plane and said first portion wherein the relationship between the width of said one passage in inches CW, the width of said port face in inches PW, and the distance between said port face and said plane in inches DL is substantially as follows: where D1 the hydraulic diameter in feet for the fin material of said first portion; D2 the hydraulic diameter in feet for the fin material of said second portion; Ac1 is the free area factor for the fin material of the first portion; Ac2 is the free area factor for the fin material of the second portion; phi f1/f2 where f1 and f2 respectively are the drag friction coefficients for the fin materials of said first and second portions at a common Reynolds number in the turbulent flow range.

Claim 3

The apparatus as defined by claim 1 wherein the length of said one passage exceeds its width by a factor in excess of 6.

Claim 4

An elongated plate type heat exchanger core comprising: a plurality of plates of similar generally rectangular peripheral configuration contraposed in spaced substantially parallel relationship wherein the distances between adjacent plates individually are substantially less than the width of said plates thereby defining a plurality of relatively thin spatial layers therebetween; sealing means sealingly bridging between and extending along the margins of adjacent plates whereby said spatial layers are enclosed to define a plurality of elongated passages each having a thickness less than its width and a width less than its length; means defining a port having a face substantially normal to the longitudinal axis of said core communicating with one of said passages; a corrugated fin fluid distributor disposed in said one passage between said port face and a plane substantially normal to said longitudinal axis traversing said core; said distributor including a first generally triangular port portion of currugated first fin material having an edge of its triangular configuration abutting said port face and the apex opposite said edge coinciding with said plane and at least a second portion of corrugated second fin material disposed in said passage laterally of said first triangular port portion between said plane and said first portion wherein the relationship between the width of said one passage in inches CW, the width of said port face in inches PW, and the distance between said port face and said plane in inches DL is as follows: where D1 the effective hydraulic diameter in feet for the fin material of said first position; D2 the effective hydraulic diameter in feet for the fin material of said second portion; Ac1 is the effective free area factor for the fin material of the first portion; Ac2 is the effective free area factor for the fin material of the second portion; phi f1/f2 where f1 and f2 respectively are the effective drag friction coefficients for the fin materials of said first and second portions at a common Reynolds number in the turbulent flow range.

Claim 5

An elongated plate type heat exchanger core comprising: a plurality of plates of similar generally rectangular peripheral configuration contraposed in spaced substantially parallel relationship wherein the distances between adjacent plates individually are substantially less than the width of said plates thereby defining a plurality of relatively thin spatial layers therebetween; sealing means sealingly bridging between and extending along the margins of adjacent plates whereby said spatial layers are enclosed to define a plurality of elongated passages each having a thickness less than its width and a width less than its length; means defining a port having a face substantially normal to the longitudinal axis of said core communicating with one of said passages; a corrugated fin fluid distributor disposed in said one passage between said port face and a plane substantially normal to said longitudinal axis traversing said core; said distributor including a first generally triangular port portion of currugated first fin material having an edge of its triangular configuration abutting said port face and the apex opposite said edge coinciding with said plane and at least a second portion of corrugated second fin material disposed in said passage laterally of said first triangular port portion between said plane and said first portion wherein the relationship between the width of said one passage in inches CW, the width of said port face in inches PW, and the distance between said port face and said plane in inches DL is as follows: where D1 the effective hydraulic diameter in feet for the fin material of said first position; D2 the effective hydraulic diameter in feet for the fin material of said second portion; Ac1 is the effective free area factor for the fin material of the first portion; Ac2 is the effective free area factor for the fin material of the second portion; phi f1/f2 where f1 and f2 respectively are the effective drag friction coefficients for the fin materials of said first and second portions at a common Reynolds number in the turbulent flow range.

Claim 6

The apparatus as defined by claim 3 wherein the length of said one passage exceeds its width by a factor in excess of 6.