Plate heat exchanger

A plate heat exchanger is provided which includes a plurality of plates mounted in abutting face-to-face relation. Interposed adjacent plates is a sealing gasket. The plates are held in assembled relation by an adjustable press. Each plate is provided with an extruded first section having second sections secured to opposite peripheral segments thereof. Each section is provided with broad opposed exterior surfaces. The first section has a plurality of internal passages formed therein defining first flow-paths for a first heat exchange medium. The opposed broad exterior surfaces of adjacent plates coact with the sealing gasket to define second flow-paths for a second heat exchange medium. The pressure exerted on the plates by the press to maintain same in abutting relation is determined by the maximum pressure generated by the second heat exchange medium within the second flow-paths during operation of the plate heat exchanger.

BACKGROUND OF THE INVENTION 
The utilization of plate heat exchangers in many commercial or 
manufacturing operations has markedly increased over the years because of 
the numerous inherent advantages possessed by plate heat exchangers as 
compared to other types of heat exchange equipment (e.g., shell and tube). 
Some of the inherent advantages include (a) versatility and flexibility to 
effectively meet various heat exchange demands; (b) improved control of 
end or terminal temperature differences; (c) varying the number of plates 
to increase or decrease capacity; (d) restreaming or rearranging the 
flow-paths so as to better control pressure drops; and (e) reduce 
maintenance costs. 
While the inherent advantages are numerous, prior plate exchangers are 
nevertheless beset with one or more of the following shortcomings: (1) 
plate warpage; (2) the plates are costly to manufacture because of the 
need for corrugations, dimples, buttons, or the like to be formed therein 
in order to maintain the desired spacing between adjacent plates; (3) an 
inordinate amount of entrapment or incrusting of particulates occurs 
within the flow-paths because of the size, shape, and number of the 
spacers disposed within the flow-paths; thereby, seriously impeding flow 
therethrough; (4) special gasket and bonding materials are required to 
assure proper sealing between the plates during operation of the 
exchanger; (5) the plates can only be mounted in one relative position, 
thereby restricting placement of the heat exchanger at only one location 
on the job site; and (6) because of problems regarding structural 
integrity, the length of each plate was restricted (e.g., not more than 
eight feet) thereby reducing the percentage regeneration capability of the 
plate. 
SUMMARY OF THE INVENTION 
Thus, it is an object of the invention to provide an improved plate heat 
exchanger which is not beset with the aforenoted shortcomings. 
It is a further object to provide an improved plate heat exchanger wherein 
the plates thereof may be readily formed to any length desired and mounted 
in a variety of relative positions (e.g., flat horizontal; on 
edge-horizontal; on edge-vertically; tilted to effect optimum condensate 
drainage end-to-end). 
It is a further object to provide an improved plate heat exchanger wherein 
substantially the whole, or significant portions, of the plates are 
extruded thereby providing internal passages having highly desirable 
structural strength and an integrity of shape, even under temperatures and 
pressure which vary over a wide range. 
It is a still further object to provide an improved plate heat exchanger 
wherein the pressure required to maintain the plates in proper abutting 
face-to-face relation is substantially less than normally required. 
It is a still further object to provide an improved plate heat exchanger 
wherein the plates thereof are substantially non-flexible thereby greatly 
facilitating the installation, maintenance, and servicing of the 
exchanger. 
Further and additional objects will appear from the description, 
accompanying drawings, and appended claims. 
In accordance with one embodiment of the invention an improved plate heat 
exchanger is provided which includes a plurality of plates mounted in 
abutting face-to-face relation. Each plate is provided with internal 
passages defining first flow-paths for a first heat exchange medium. 
Adjacent plates coact to form passages defining second flow-paths for a 
second heat exchange medium. The first and second flow-paths are 
independent of one another with separate inlet and outlet means therefor 
so as to allow counter-flow of the media throughout the exchanger. Sealing 
gasket means are interposed adjacent plates. Each plate includes an 
extruded first section having the internal passages formed therein and 
arranged in side-by-side relation. Second sections are disposed at 
opposite peripheral segments of the plate first section and are provided 
with the inlet and outlet means. The first and second sections have broad, 
opposed, exterior surfaces which coact with the sealing gasket means to 
define the second flow-paths.

Referring now to the drawings and more particularly to FIG. 1, one form of 
the improved heat exchanger 10 is shown which is adapted for use in a 
dairy plant or the like. The exchanger 10 is provided with suitable inlet 
and outlet connections 11a-b and 12a-b. Connections 11a-b are provided for 
a first heat exchange medium (e.g., steam or ammonia) and connections 
12a-b are provided for a second heat exchange medium (e.g., milk, water, 
etc.). By way of example, the first medium may have a working pressure of 
approximately 275 p.s.i.g. and the second medium may have a working 
pressure of 100 p.s.i.g. The types of heat exchange medium and the working 
pressures thereof may vary over a wide range. Normally, however, the 
designed working pressure for the first heat exchange medium would be 
about 300 p.s.i.g. and that of the second heat exchange medium would be 
about 125 p.s.i.g. 
Heat exchanger 10 also includes a plurality of individual elongated plates 
13, see FIG. 2, which, in the illustrated embodiment, are horizontally 
disposed and stacked in abutting face-to-face relation. The number of 
plates comprising the stack S and the size and length of each plate will 
depend upon the operation requirements of the system in which the plate 
heat exchanger is installed. The stack of plates are subtended by the 
lower portion L of a supporting frame F and the top of the stack is 
engaged by the top portion T of the frame. The periphery of the frame top 
portion T is adjustably secured to the periphery of frame lower portion L 
by a plurality of symmetrically arranged hold-down nut and bolt units H. 
The pressure exerted on the stack by the frame top portion can be 
carefully determined by the use of a conventional torque wrench or the 
like. 
As seen in FIG. 5, a sealing gasket G is interposed each pair of plates 
comprising the stack S. The gasket may be formed of various types of 
materials commonly utilized for this purpose and must be capable of 
withstanding the temperatures and pressures to be encountered when the 
medium flows within the passages formed between adjacent plates. 
Furthermore, the gasket material must be inert to such heat exchange 
medium. 
Each plate 13 in exchanger 10 is preferably of like construction, and as 
seen in FIG. 2, includes a first, or center section 14 which is extruded 
from a suitable material (e.g., aluminum) having high thermal 
conductivity; high structural strength; and is not deleteriously affected 
by the heat exchange media. 
Secured by welding or the like to opposite ends of the center section 14 
are header, or second, sections 15 which preferably are precision castings 
and of like configuration. 
Center section 14, as seen in FIGS. 4 and 5, has formed therein a plurality 
of elongated passages 16 arranged in spaced, substantially parallel 
relation. Adjacent passages are separated from one another by a web 17 
which extends from a broad top surface 18 to a broad bottom surface 20 of 
the section 14. The passages 16 are preferably of like configuration and 
are coextensive with one another. Each passage is relatively straight and 
has substantially smooth wall surfaces which do not impeded or encumber 
flow of the heat exchange medium through the passage. By reason of this 
construction, there is a minimal pressure drop as the heat exchange medium 
flow through the passage and a closer terminal-to-terminal temperature 
control can be achieved. In view of the self-contained strength of the 
extruded section 14, the top and bottom surfaces 18, 20 thereof remain 
stable thereby avoiding a serious warpage problem, which is common in many 
prior plate heat exchangers. As previously noted, such prior plate heat 
exchangers have attempted to minimize warpage by forming corrugations, 
dimples, buttons, or the like in either, or both, the top and bottom 
surfaces and thereby maintain space uniformity between portions of 
adjacent plates. 
As noted in FIG. 5a, each web 17 of the center section 14 has the length 
thereof foreshortened, thereby enabling adjacent passages 16 to be 
interconnected at their ends for reasons to be explained more fully 
hereinafter. 
Formed along the elongated margin of the top surface 18 of center section 
14 are a pair of upwardly protruding elongated ribs 21, 22. The ribs coact 
to form a substantially channel-shaped retainer-guide pocket for the 
sealing gasket G. Rib 21 normally projects upwardly a slightly greater 
distance than rib 22 and thereby more effectively prevents blow-out of the 
accommodated gasket, when the heat exchanger is in operation. Ribs 21 and 
22 provide added stiffness to the plate top surface and also may serve to 
determine the minimum height of the passage 23 formed between adjacent 
plates when the stack S is compressed between the frame portions L and T, 
see FIG. 5. While the ribs 21, 22 are shown formed on the top surface of 
section 14, they may be formed instead on the bottom surface 20, if 
desired. 
The header sections 15, as illustrated in FIGS. 2 and 3, are of like 
configuration and may be precision castings. Each header section includes 
broad top and bottom surfaces 24 and 25, respectively, which are coplanar 
with corresponding surfaces of the center section. In addition, each 
header section 15 includes narrow side surfaces 26 which are normally 
coplanar with corresponding narrow side surfaces 27 of the center section. 
One end of the header section is closed by a narrow end wall 28. The upper 
edge of wall 28 forms an upwardly-projecting lip 28a. The height of lip 
28a is substantially the same as that of the ribs 30, 31, 32, 33 also 
formed on the top surface 24 of the header section. Rib 30 has a 
serpentine-like configuration with the ends 30a thereof substantially 
aligned with the corresponding end 21a of rib 21 formed on the top surface 
18 of center section 14. 
Rib 31 is interrupted and has one segment 31a thereof partially 
encompassing an enlarged transverse port 34 found in the header section 
which extends from the top surface 24 to the bottom surface 25. Port 34 
communicates with the passages 23 formed between adjacent plates of the 
assembled stack. Rib 31 also includes a second segment 31b which may be 
substantially crescent shaped. Segment 31b has a curved surface 
substantially aligned with the surface of rib 22 which is adjacent the 
accommodated gasket. Rib 30 and rib segments 31a, 31b coact with one 
another to form a retainer-guide pocket for part of the sealing gasket 
carried by the center section 14. 
Header section 15 is also provided with a second port 35 similar in shape 
to port 34 but spaced therefrom. Communicating with port 35 and formed 
intermediate the top and bottom surfaces 24, 25 is an internal secondary 
port 36 which extends radially from the periphery of port 35 to the 
adjacent end 14a of the center section 14 to which the header is 
connected. Because the ends 17a of the interior webs 17 of the center 
section are recessed from the center section end 14a, port 36 is in 
communication with all of the internal passages 16 formed in the center 
section. 
Rib 33, which is formed in the top surface 24 of the header section, 
surrounds an end of port 35. Rib 32 also formed on the top surface 24 is 
in spaced concentric relation with rib 33 and coacts therewith to form a 
pocket for an annular second sealing gasket, not shown. The second gasket 
may be formed of the same material as gasket G. 
A modified form of the improved plate heat exchanger 110 is shown in FIG. 6 
which is similar to exchanger 10, except that instead of the first heat 
exchange medium flowing through inlet connection 11a, header section 15, 
center section 14, header section 15 and out through connection 11b, the 
medium enters the passages 16 of the center section 14 through a plurality 
of individual tubes T.sub.1 and is discharged from the center section 
through a like number of tubes T.sub.2. There is a pair of tubes for each 
plate. Each tube is connected at one end to an external header section 115 
which is spaced endwise from a corresponding end plate P', the latter 
being secured to and overlying the entire end face of the center section 
114. The other end of each tube is connected to a connector C which, in 
turn, is affixed to an exposed portion of the end plate. The connector C 
is provided with a central opening which is aligned with a suitable 
opening formed in plate P'. Thus, the first heat exchanger medium will 
flow to each of the passages 16 because the interior webs 17 have recessed 
ends 17a, as seen in FIG. 5a. 
Exchanger 110 might be a preferred embodiment where the heat exchange 
medium flowing through tubes T.sub.1, T.sub.2 is a toxic product and the 
latter is contained under high pressure within the header sections 115. If 
for any reason a leakage of the product should occur at either of the 
connectors C, such leakage would be to the atmosphere rather than to the 
other heat exchange medium flowing through passages 23. To facilitate 
understanding of exchanger 110, the parts thereof which correspond to 
parts of exchanger 10 have been given the same number, but in a 100 
series. 
Because of the structural integrity and non-flexing characteristics of the 
plates 13 and 113, assembly and disassembly of the plates within an 
exchanger is greatly facilitated. Furthermore, installing, maintaining, or 
change-out of the various gaskets present no problem because no bonding or 
glueing of the gaskets is required. In the improved plate heat exchanger, 
the compressive force required to properly retain the plates in assembled 
relation need only be greater than the pressure of the heat exchange 
medium flowing through passages 23. This latter pressure is normally 
substantially less than the pressure of the medium flowing through 
passages 16. Thus, by reason of the reduced compressive force required, a 
broad range of gasket materials may be utilized and the useful life of the 
gaskets significantly extended. 
While the plates 13, 113 in the illustrated embodiments are shown in a 
flat, horizontal position, they can be disposed on edge (side or end) or 
they can be tilted so that condensate, if any, will accumulate at the 
lower end of the plate and be readily drained. Because of this versatility 
regarding the disposition of the plates, the improved heat exchanger can 
be placed in the most practical location within a given area. In the 
improved heat exchanger, an ideal heat transfer condition exists, namely, 
the heat exchange media are in one pass counter flow relation. 
The size, shape, and number of internal passages formed in the plates may 
vary from that shown without departing from the scope of the invention.