U.S. patent number 3,743,011 [Application Number 05/195,680] was granted by the patent office on 1973-07-03 for heat exchanger.
This patent grant is currently assigned to Modine Manufacturing Company. Invention is credited to Donald J. Frost.
United States Patent |
3,743,011 |
Frost |
July 3, 1973 |
HEAT EXCHANGER
Abstract
A heat exchanger apparatus for exchange of heat between two
fluids which is especially adaptable for use as an oil cooler in an
internal combustion engine with the apparatus comprising a stack of
successive pairs of metal plates shaped and bonded together and
enclosed in a casing, the stack of plates being shaped to prvide
interconnected passages for a first fluid such as the oil to be
cooled, surrounding passages for a second fluid such as the liquid
coolant from an internal combustion engine, and means for flowing
the oil and the coolant through their respective passages to and
from the engine.
Inventors: |
Frost; Donald J. (Racine,
WI) |
Assignee: |
Modine Manufacturing Company
(Racine, WI)
|
Family
ID: |
22722328 |
Appl.
No.: |
05/195,680 |
Filed: |
November 4, 1971 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
|
23191 |
Mar 27, 1970 |
|
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Current U.S.
Class: |
165/283; 165/916;
165/167; 165/297 |
Current CPC
Class: |
F28F
9/24 (20130101); F01M 1/10 (20130101); F28D
9/0012 (20130101); F01M 5/002 (20130101); Y10S
165/916 (20130101); B01D 35/18 (20130101) |
Current International
Class: |
F28F
9/00 (20060101); F28D 9/00 (20060101); F28F
9/24 (20060101); F01M 1/10 (20060101); F01M
1/00 (20060101); F01M 5/00 (20060101); F28f
003/00 () |
Field of
Search: |
;165/164-166,167,35-38 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Myhre; Charles J.
Assistant Examiner: Streule, Jr.; Theophil W.
Parent Case Text
CROSS REFERENCE TO RELATED APPLICATION
This application is a continuation-in-part of my copending
application Ser. No. 23,191, filed Mar. 27, 1970 now abandoned.
Claims
I claim:
1. Heat exchanger apparatus for exchange of heat between two
fluids, comprising: a plurality of successive pairs of plates
arranged in a stack, each said plate having an outer edge and an
inner opening defining an inner edge; means joining each pair of
plates at first areas adjacent their inner edges and at second
areas inwardly of their outer edges, each said pair of plates being
spaced apart between their said first and second areas thereby
providing a first chamber in each pair; means joining adjacent
plates of each of said stacked pairs of plates at third areas
located outwardly of said second areas, said second areas of
successive pairs of plates being spaced apart thereby providing a
succession of peripherally located second chambers; fluid flow
opening means in said second areas joining said second chambers
thereby providing a flow manifold, said successive pairs of plates
being spaced apart inwardly of said third areas thereby providing a
succession of third chambers communicating at their outer ends with
said second chambers and open at their inner ends; means for
flowing a first said fluid radially outwardly through one group of
said third chambers from their said open inner ends and radially
inwardly through a second group of said third chambers to said open
inner ends of said second group, said flow being by way of said
manifold; and means for flowing a second said fluid through said
first chambers.
2. The apparatus of claim 1 wherein said second areas of said
plates are of small extent, with each plate having a plurality of
said second areas arcuately spaced around the plate thereby
providing a plurality of arcuately spaced sets of said second
chambers, the second chambers of each said set being joined by said
fluid flow opening means.
3. The apparatus of claim 2 wherein there are three of said sets
equally spaced around said stack of annular plates.
4. Heat exchanger apparatus for exchange of heat between two
fluids, comprising: a plurality of successive pairs of annular
plates arranged in a stack; means joining each pair of plates at
first areas adjacent their inner edges and at second areas inwardly
of their outer edges, each said pair of plates being spaced apart
between their said first and second areas thereby providing a first
chamber in each pair; means joining adjacent plates of each of said
stacked pairs of plates at third areas located outwardly of said
second areas, said second areas of successive pairs of plates being
spaced apart thereby providing a succession of peripherally located
second chambers; fluid flow opening means in said second areas
joining said second chambers thereby providing a flow manifold,
said successive pairs of plates being spaced apart inwardly of said
third areas thereby providing a succession of third chambers
communicating at their outer ends with said second chambers and
open at their inner ends, and said second areas of said plates are
of small extent, with each plate having a plurality of said second
areas arcuately spaced around the plate thereby providing a
plurality of arcuately spaced sets of said second chambers, the
second chambers of each said set being joined by said fluid flow
opening means; means for flowing a first said fluid radially
outwardly through one group of said third chambers from their said
open inner ends and radially inwardly through a second group of
said third chambers to said open inner ends of said second group,
said flow being by way of said manifold; means for flowing a second
said fluid through said first chambers; means joining adjacent
plates of each of said stacked pairs of plates at an enclosing
fourth area of each plate, each said joined pair of fourth areas
being spaced from the adjacent joined pair of fourth areas thereby
providing a succession of peripherally located fourth chambers;
fluid flow opening means in each said joined pair of fourth areas
thereby providing a second manifold; and means for flowing said
first said fluid through said second manifold prior to flow through
said third chambers.
5. The apparatus of claim 4 wherein said fourth areas of said
plates are of small extent, with each plate having a plurality of
said fourth areas arcuately spaced around the plate thereby
providing a plurality of arcuately spaced sets of said fourth
chambers, the fourth chambers of each said set being joined by said
fluid flow opening means.
6. The apparatus of claim 5 wherein there are three of said sets of
fourth chambers symmetrically arranged with respect to each other
and to said second chambers.
7. The apparatus of claim 4 wherein each said third chamber is
provided with an annular agitator fin therein.
8. The apparatus of claim 7 wherein each agitator fin comprises a
plate with one set of spaced projections extending from one side
thereof and a second set of spaced projections extending from the
other side thereof.
9. The apparatus of claim 8 wherein each said projection is
essentially frustoconical with the peak of each projection being
located against a said plate.
10. The apparatus of claim 4 wherein a first of said two fluids
comprises lubricating oil for an engine and a second of said fluids
comprises engine coolant liquid, and there are provided an
enclosing casing having a first inlet for said first fluid to said
second manifold and an outlet from said second manifold to said
conduit, means joining said first inlet to said engine for oil flow
therethrough, and means joining said outlet to said engine for flow
of oil therethrough.
11. The apparatus of claim 10 wherein there are provided means
dividing said inner flow passage means into two adjacent parts, one
part communicating with said one group of third chambers and the
second part communicating with the second group of said third
chambers, and a flow conduit for said first fluid located in said
inner flow passage means, said conduit having a first side opening
leading to said first group, an axially spaced second side opening
leading from said second group, and means on said conduit
separating said groups.
12. The apparatus of claim 11 wherein there are provided a check
bypass valve in said conduit between said first group and said
second group openable at a preselected pressure equivalent to the
viscosity of cold congealed lubricating oil to bypass said first
and second groups of said third chambers.
13. The apparatus of claim 1 wherein there are provided separating
means in the plates of said stack for separating said succession of
third chambers from a series of fourth chambers, means connecting
said fourth chambers in series to provide a bypass path exteriorly
of said path comprising said second and third chambers, and bypass
valve means in said bypass path for opening said path to said first
fluid when said first fluid is less than a preselected
temperature.
14. The apparatus of claim 13 wherein said stack of plates are
arranged in sets to provide said groups of third chambers and
corresponding second chambers, each said set being separated from
the next by a transverse partition having openings therein
interconnecting said second chambers flow manifold and
interconnecting said fourth chambers of said bypass paths.
15. The apparatus of claim 13 wherein there are provided
turbulizers in said second and third chambers.
16. The apparatus of claim 13 wherein said first fluid comprises an
engine lubricating oil and said second fluid comprises a coolant
liquid.
17. The apparatus of claim 16 wherein there is provided an oil
filter communicating with the exits of said path and said bypass
path to receive oil therefrom, and a tube extending through said
stack of plates on which said filter is mounted, said tube being
connected to the exit from said filter for flow of oil therefrom
and return to said engine.
18. The apparatus of claim 1 wherein said first chambers are
provided by cooperating spacers in each said pair of plates.
19. The apparatus of claim 18 wherein each said spacer comprises a
raised element in its said plate.
Description
SUMMARY OF THE INVENTION
One of the features of this invention is to provide a heat
exchanger apparatus having the structure set out above.
In one embodiment the heat exchanger apparatus when used to cool
engine lubricating oil has means thereon for mounting an oil filter
with flow connections for passage of the oil through the filter and
preferably prior to passage of the oil through the oil cooling
portions of the heat exchanger.
In a more specific embodiment of the invention a central conduit of
the heat exchanger is used to mount the exchanger on the engine
block, to mount the filter on the heat exchanger when a filter is
used, to mount a cover plate in place of the filter when one is not
used and to contain a bypass valve that permits passage of cold oil
directly back to the engine without substantial flow through the
oil cooling portion of the apparatus.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side elevational view partially broken away of an
engine block having mounted thereon a heat exchanger oil cooler
apparatus embodying the invention with an oil filter of the
customary type in position.
FIG. 2 is a view similar to FIG. 1 but with an enclosing cap
replacing the oil filter of FIG. 1.
FIG. 3 is a plan view of the heat exchanger partially broken away
and omitting both the filter of FIG. 1 and the cap of FIG. 2.
FIG. 4 is an enlarged longitudinal sectional view through the heat
exchanger apparatus embodying the invention.
FIG. 5 is a plan view of one of a plurality of co-operating fluid
flow plates used in the heat exchanger.
FIG. 6 is an edge elevational view of the plate of FIG. 5.
FIG. 7 is an enlarged transverse sectional view taken substantially
along line 7--7 of FIG. 5.
FIG. 8 is a plan view of an agitator or turbulizer fin used between
each adjacent pair of plates.
FIG. 9 is an enlarged plan view of a detail portion of FIG. 8.
FIG. 10 is a sectional view taken substantially along line 10--10
of FIG. 9.
FIG. 11 is a view similar to FIG. 4 but illustrating a second
embodiment of the invention.
FIG. 12 is a view similar to FIG. 5 but illustrating a plate of
this second embodiment.
FIG. 13 is a sectional view taken along line 13--13 of FIG. 12.
FIG. 14 is a sectional view taken along line 14--14 of FIG. 12.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
As illustrated in the drawings the heat exchanger apparatus 10 of
this invention is shown as mounted on an engine block 11 in
communication with a lubricating oil passage 12 therefrom and a
second oil passage 13 leading back into the block. In addition, as
illustrated in FIGS. 1 and 2, the engine block contains outlet and
inlet passages for flow of liquid coolant from the coolant
containing portions of the block directly to and from the heat
exchanger 10 as illustrated by the broken line connections 14 and
15 of FIGS. 1 and 2 as well as the liquid conduits of FIG. 3.
The apparatus although illustrated as being used to cool
lubricating oil in an engine by using liquid coolant directly from
the engine can also be used for exchange of heat between any two
fluids. The heat exchanger of the first embodiment of FIGS. 1-10
comprises a plurality of successive pairs of metal plates 16 that
are arranged in a stack having a generally cylindrical outer
configuration. Each plate 16 has an outer edge 17 and an inner
opening defined by an inner edge 18. Each successive pair of plates
is joined at first areas 19 adjacent their inner edges 18 and at
second areas 20 inwardly of the plate outer edges 17.
Each of the stacked pairs of plates is spaced apart between the
first 19 and second 20 joined areas to provide a first chamber 21
in each pair of plates. Because there are successive pairs of
plates arranged in the stack as shown in FIG. 4 there are of course
a plurality of successive chambers 21.
Also provided are means joining adjacent plates in each of the
stacked pairs of plates at third areas 22 with these third areas
being located outwardly of the second areas and in the embodiment
illustrated around the periphery of the assembly of plates.
The second joined areas 20 of the plates are spaced apart as
illustrated at the bottom of FIG. 4 and thereby provide a
succession of peripherally located second chambers 23. Fluid flow
opening means 24 are located in these second areas 20 joining the
series of second chambers 23 to provide a flow manifold 25.
Each successive pair of plates 16 is spaced apart inwardly of the
joined third areas 22 to provide a succession of third chambers 26
that communicate at their outer ends with the second chambers 23
and that are open at their inner ends as illustrated at 27.
As will be described in more detail herein, means are provided for
flowing a first fluid, in the illustrated embodiment engine
lubricating oil, radially outwardly through one group of third
chambers 26 by way of their open inner ends 27 and radially
inwardly through a second group of these third chambers 26 to their
open inner ends 27 with the flow being by way of the first manifold
25 and also means for flowing a second fluid, in this embodiment
liquid coolant from the engine, through the first chambers 21.
In the preferred apparatus the means joining the pairs of plates at
their first areas 19 extend completely around the inner edges of
the stack of plates thereby providing an inner flow passage means
28. Means are provided for dividing this inner flow passage means
into two adjacent parts with one part 29 communicating with the one
group of third chambers 26 and a second part 30 communicating with
a second group of these chambers 26. In the embodiment disclosed
this dividing means is embodied in a fluid flow conduit or pipe 31
extending through the inner flow passage 28 with this pipe having a
first series of three circularly arranged openings 32 leading
directly to the one flow passage part 29 and a second series of
three circularly arranged openings 33 adjacent the second flow
passage part 30. The openings 32 and 33 are axially spaced from
each other along the pipe 31 and are located on opposite sides of
an annular boss 34 on the outside of the pipe 31 and positioned at
the midpoint of the flow passage 28 to divide it into the first
part 29 and the second part 30.
In the illustrated first embodiment of the heat exchanger the
joined second areas 20 are of small extent and arcuately extended
as shown in FIG. 5 with the resulting fluid flow openings 24 being
of similar shape. As is shown in FIG. 5 there are a plurality of
these second areas 20, here shown as three, arcuately spaced around
each plate 16 adjacent the periphery thereof. As illustrated, the
areas 20 and their contained openings are spaced about 120.degree.
apart.
There are also provided means joining adjacent plates 16 of each of
the stacked pairs of plates as illustrated in FIG. 4 at an
enclosing fourth area 35 and with each of the joined pairs of
fourth areas being spaced from the adjacent joined pair of fourth
areas to provide a succession of peripherally located fourth
chambers 36 that are connected by openings 37 thereby providing a
second manifold 38. The areas 66 of plates 16 surrounding openings
37 are also joined together to provide a fluid tight structure.
The assembly of joined pairs of plates 16 are capped at their
opposite ends by an end plate 39 adjacent the engine block 11 and
an opposite end plate 40 at the opposite end. In the illustrated
embodiment there are three sets of second manifolds 38 also
arranged 120.degree. apart and symmetrically arranged with respect
to each other to the three first manifolds 25 previously described.
In order to provide for flow of a first fluid such as the
illustrated engine lubricating oil through the three second
manifolds 38 there are provided in the end plate 39 three openings
41 each leading directly into a manifold 38 as illustrated in FIG.
4 while the opposite end plate 40 is provided with three similar
openings 42 for flow of fluid from the three second manifolds 38.
Thus with this arrangement in the illustrated embodiment the flow
of fluid or oil from the engine block 11 is in three parallel paths
comprising the three manifolds 38.
The assembly of stacked plates 16 is enclosed in a generally
cylindrical casing 43 that has an edge 44 joined to the outer edge
of the first end plate 39. The opposite end 45 of the casing 43 is
spaced from the end plate 40 so as to provide an annular chamber
46. The three manifolds 38 empty into this annular chamber by way
of the aligned openings 42.
The liquid coolant is conducted from the coolant containing
portions of the engine block 11 by way of the previously described
coolant connecting lines 14 and 15. In its flow through the heat
exchanger the coolant flows through the first chamber 21 and around
the three first manifolds 25 as well as around the three second
manifolds 38 before returning to the coolant section of the engine
block 11. This flow through the spaced chambers 21 and around the
total of six manifolds provides very efficient cooling of the oil
that is at the same time flowing through the assembly of third
chambers 26. As is obvious, each third chamber 26 that forms a
portion of the oil flow passage is surrounded by the first chamber
21 which contains the liquid coolant.
In order to further increase the coolant efficiency each third
chamber 26 contains an annular agitator or turbulizer fin 47 that
is illustrated in detail in FIGS. 8, 9 and 10. As is shown in FIG.
8, each fin 47 is a metal plate that is generally circular with an
inner circular opening 48 that substantially coincides with the
inner end 27 of the third chamber 26 in which the fin 47 is
located. The outer periphery of each fin 47 is provided with three
symmetrically arranged recesses 49 each of which is arranged on the
outside of one of the three second manifolds 38.
As is illustrated in the enlarged details of FIGS. 9 and 10 each
fin 47 comprises a plate having one set of spaced projections 63
extending out of the plane 50 of the plate on one side thereof and
another set of projections 51 extending from the other side of the
plane 50 of the plate and with certain of the projection 63 and 51
as illustrated in FIG. 10 being joined directly as indicated at 52.
In the illustrated embodiment each projection 63 and 51 of each fin
47 is of essentially frustoconical shape with the peak of each
projection being positioned against an enclosing plate 16 as
illustrated in FIG. 4.
As illustrated the heat exchanger of this invention for exchanging
heat between two fluids is ideally designed for cooling lubricating
oil from an engine by use of the liquid coolant directly from the
engine. The heat exchanger is easily mounted on the engine block 11
by having one end 52 of the pipe or conduit 31 threaded directly to
the block in alignment with the other passage 13 in the block. The
edge 44 of the cooler will then enclose the other oil passage 12 as
illustrated in FIG. 4 and at the same time retain in position a
surrounding O-ring gasket 53 to prevent oil leakage between the
heat exchanger and the engine block.
The opposite end 54 of the pipe 31 can also extend beyond the heat
exchanger and contains attaching means, here shown as threads 54,
for attaching either an oil filter 55 as shown in FIG. 1 or an
enclosing dished cap 56 as illustrated in FIG. 2. This end also
holds a nut 64 retainer for the heat exchanger plates 16. In either
case the oil filter 55 or cap 56 holds in position a second O-ring
gasket 57 as shown in each of FIGS. 1 and 2 that surrounds the exit
passages 58 leading from the annular chamber 46. Whether the oil
filter 55 is used or merely the enclosing cap 56 the oil will flow
outwardly of the block 11 through the passage 12 and through the
three sets of second manifolds 38 in parallel flow through the
exchanger. From the manifolds 38 the oil flows through the openings
42 into the chamber 46 and from there through the openings 58
either through the oil filter 55 or into the cap 56.
The oil is then directed from either the filter 55 or the cap 56
into the interior of the pipe 31 for return to the engine by way of
the passage 13. If the oil is cold and therefore with a relatively
high viscosity it displaces a bypass valve 60 for flow directly
through the pipe 31 into the return passage 13, bypassing the heat
exchanger chambers 26. This bypass valve will now be described.
The interior of the pipe 31 at about the region of the annular boss
34 is provided with an annular valve seat 59 for a spring pressed
circular valve 60. This valve 60 is held in position on the seat 59
by a helical compression spring 61 one end of which bears against
the valve 60 and the other end of which bears against a cross pin
62 that extends across the interior of the pipe 31. Thus with this
arrangement the valve 60 is located between the two sets of
openings 32 and 33.
When the oil flowing inwardly (arrow 65) through the pipe 31 is
cold and viscous it exerts sufficient pressure on the valve 60 to
displace it against the thrust of the spring 61 and permit the oil
to flow around the valve 60 and directly into the return passage 13
without flowing through the oil cooling passages. When, however,
the oil has become sufficiently heated to have a reduced viscosity
it cannot then overcome the pressure of the spring 61 so that the
valve 60 closes. In one typical embodiment of this invention the
spring 61 was designed to close at about 10 pounds per square inch
pressure.
With the valve 60 closed by the spring 61 the oil thereupon flows
radially outwardly through the set of three openings 32 and through
the first set of oil flow chambers 26 and into the corresponding
chambers 23 of the first manifold 25. These are of course the
chambers 26 on the upstream side of the boss 34. Then the oil flows
through the three first manifolds 26 into the remaining oil cooling
chambers 26 which are on the downstream side of the boss 34. Here
the oil flows radially inwardly toward the pipe 31, through the
three circularly arranged openings 33 and then axially into the
engine by way of the passage 13.
During the flow of the oil in the chambers 26 which is first
radially outwardly and then radially inwardly the oil is cooled by
the surrounding coolant in the series of first chambers 21 and this
cooling is more efficiently accomplished by reason of the agitator
fin 47 in each chamber 26 which causes a turbulent flow.
The heat exchanger of this invention is very efficient in
exchanging heat between two flowing fluids and occupies very small
space. These general characteristics make it extremely useful as an
oil cooler for cooling the oil of an engine and it can be mounted
directly on the block so as to permit oil and coolant directly from
the engine to flow through the heat exchanger and back to the
engine. Furthermore, in one embodiment as illustrated in FIG. 1 the
cooler serves as a mounting for an oil filter so that a separate
mounting is not required and when the filter is used it permits
preferably flowing the oil through the filter to remove any solid
foreign particles before the oil is conveyed through the cooling
portion of the apparatus.
Because the heat exchanger receives coolant directly from the
engine and not from a radiator its performance is not controlled by
the usual engine thermostat which controls flow through a radiator.
This flow of coolant directly from the engine provides warm coolant
at the very beginning of operation of the engine so that the
viscosity of the oil is immediately lowered for flow of this
decongealed oil through the cooler passages rapidly and
efficiently.
As can be seen from the detailed description given above of the
construction of the exchanger, the device is made up entirely of
assembled sheet metal parts some of which are plates held in
position within an enclosing casing. The exchanger includes a
conduit 31 that also serves as a means for mounting the exchanger
on the engine block and for mounting an oil filter where one is
used or a flow directing cap in place of the filter.
FIGS. 11-14 illustrate a second embodiment of the invention in
which oil flows through the cooler apparatus 110 and then passes on
to the filter as shown at 55 in the first embodiment or the return
cap 56 also shown in this first embodiment and with the second
embodiment in addition providing a bypass through which the oil may
flow without being cooled where cooling is not required. In this
second embodiment there are the same coolant connections as in the
first embodiment and with these being indicated generally at 115 in
FIG. 11. As indicated, the liquid coolant flows into the apparatus
as indicated at 70 and from the apparatus as shown at 71.
The heat exchanger itself comprises a series of plates 116 arranged
in successive pairs with each pair having outer edges 117 joined
together as illustrated in FIG. 11 and inner edges 118 that are
interconnected so as to comprise joined first areas 119. Each
adjacent pair of plates 116 are also joined at second areas 120
inwardly of the outer edges and each of the pairs of plates are
spaced apart between their first 119 and second 120 areas to
provides a series of first chambers 121 as illustrated on the right
side of FIG. 11. In the illustrated embodiment these first chambers
121 receive coolant that flows through the enclosing casing 143 to
cool the oil flowing through the heat exchanger in the manner to be
described in greater detail hereinafter.
The stacked pairs of plates are joined at third areas 117 located
outwardly of the second areas 120. These second areas 120 are
spaced apart in the successive pairs of plates to provide a
succession of peripherally located second chambers 123. Fluid flow
opening means 124 are provided in these second areas to provide a
flow manifold 125 joining the second chambers 123 in series as
shown at the left side of FIG. 11.
The successive pairs of plates 116 are spaced apart inwardly of the
third areas 117 to provide a series of third chambers 126 each of
which communicates with a corresponding second chamber 123 and
these third chambers 126 are open at their inner ends or edges to
fourth chambers 136 provided between the adjacent plates of
adjacent pairs as shown at the right side of FIG. 11.
These fourth chambers 136 comprise means for flowing a first fluid,
such as oil in the illustrated embodiment, radially outwardly
through one group of third chambers 126 by way of openings 137 in
the adjacent pairs of plates. At the outer extremities of these
third chambers 126 which receive oil directly from the fourth
chambers 136 the interconnection to the second chambers 123 of the
manifold 125 provides for flowing the oil then radially inwardly
through the second set or group of oil flow third chambers 126
which in FIG. 11 are above the dividing partition 73.
The heat exchanger also provides means for flowing a second fluid
through the first chambers 121 which in this embodiment is liquid
coolant within the enclosing casing 143. In order to provide for
flow of coolant for the second fluid through the first chambers 121
each plate 116 is provided with the series of raised areas 86 as
shown in FIG. 12. These raised areas which are of small extent have
flat tops which are interconnected in adjacent plates of successive
pairs of plates as shown in FIG. 11 so as to hold these successive
plates apart in peripheral areas. Thus as shown in FIG. 14 one side
of each plate 116 which here is the left side forms a boundary for
the coolant containing first chambers 121 while the opposite sides
form the boundary of the oil containing third chambers 126. In
order to indicate these respective sides of the plate the sides are
identified with the numerals 121 and 126 in FIG. 14.
The assembly of plates are arranged in a stack as shown in FIG. 11
and the stack is assembled in a plurality of sets, here shown as
two, with each set being separated from the other by the transverse
partition 73. This partition is provided with one opening 74
forming a part of the flow manifold 125 and with a second opening
75 which will be described in more detail hereinafter.
In the second chambers 123 and third chambers 126 there are
provided agitator fins 147 similar to the fins 47 shown in detail
in the first embodiment.
In order to separate the cooling flow path and the by-pass
non-cooling flow path each plate 116 is provided with a continuous
ridge 76 enclosing the bypass path 77 portion of the plates and the
openings 85 in which is located the pipe 131. In the assembled
plates the peaks of these ridges are joined as indicated at FIG. 11
and thereby enclose the bypass path 77 and separate it from the
cooling oil path 72 which includes the third chambers 126 and the
interconnected second chambers 123. Oil flow in this bypass path is
indicated by the dotted line arrows 79 in FIG. 11.
The enclosing casing 143 through which the coolant 70 is directed
has an end plate 145 on the end opposite the plate 139 and
containing a plenum chamber 158 having flow openings 80 for both
the oil path flow and also the bypass path flow.
Aligned with the openings 75 in the partition 73 are a series of
openings 81 in the plates. Located in the space provided by these
openings and in the bottom half of the heat exchanger is a bypass
valve structure 82 similar to the valve 60, spring 61 and cross pin
62 of the first embodiment as illustrated in FIG. 4. This bypass
valve operates in the same manner as in the first embodiment and
therefore opens when the oil is cold enough not to require cooling
so that the oil can flow directly through the bypass path 77 into
the filter or into the return cap as illustrated in FIGS. 1 and
2.
The heat exchanger or oil cooler of the second embodiment operates
as follows. Coolant such as the coolant liquid of the engine is
circulated through the casing 143 and the coolant first chambers
121 as in the first embodiment. Lubricating oil when cooling is
required flows through the third chambers 126 and manifold second
chambers 123 as indicated by the arrows 72 of FIG. 11. While
flowing through these chambers the oil passes through and around
the assembled turbulizer fins 147 for agitation and better heat
transfer. In the disclosed embodiment the oil flows in parallel
through the cooling chambers beneath the partition 73 and then
passes from the flow manifold 124 through the openings 74 in the
partition to the second set of cooling chambers that are above the
partition of FIG. 11. From here the oil then flows through an end
opening 84 in an end plate 140 and into either the oil filter of
the type illustrated in FIG. 1 or into the return cap shown at 56
in FIG. 2 if an oil filter is not used. The oil then flows back
through the fitting or pipe 131 to the engine as indicated by the
arrows 165.
In the event the oil is so cold that no cooling is required the
high viscosity of the oil will open the valve 82 so that the oil is
directed in the bypass path and without flowing through the cooler
itself, all in the same manner as described in the first
embodiment.
In spite of the compact size of the heat exchanger it provides flow
of oil in parallel passages radially outwardly and then radially
inwardly with these passages each being surrounded by coolant and
with each passage preferably containing an agitator or turbulizer
fin. This type of oil flow separated into the two paths arrangement
permits attaining high heat transfer between the oil and the
coolant with a low pressure drop through the exchanger because the
total length of the parallel flow is quite short.
The heat exchanger of this invention is also adaptable to existing
oil filter locations and is readily accessible for rapid
replacement or repair and can be easily removed for cleaning. It
has an attractive appearance and can be used as a supplement to an
existing oil cooler where greater cooling capacity is required or
desired.
Having described my invention as related to the embodiment shown in
the accompanying drawings, it is my intention that the invention be
not limited by any of the details of description, unless otherwise
specified, but rather be construed broadly within its spirit and
scope as set out in the appended claims.
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