U.S. patent number 3,814,172 [Application Number 05/238,920] was granted by the patent office on 1974-06-04 for heat exchangers.
This patent grant is currently assigned to The A.P.V. Company Limited. Invention is credited to David Teignmouth Shore.
United States Patent |
3,814,172 |
Shore |
June 4, 1974 |
HEAT EXCHANGERS
Abstract
A heat exchange apparatus and method of using it comprising
periodically flexing flexible flat heat transfer plates so as to
vary the cross section of the flow space, thereby achieving
turbulence which promotes improved heat transfer. The variation in
cross section may be obtained mechanically or through varying the
pressure of the medium on one side of the plate.
Inventors: |
Shore; David Teignmouth
(Banstead, EN) |
Assignee: |
The A.P.V. Company Limited
(Sussex, EN)
|
Family
ID: |
22899878 |
Appl.
No.: |
05/238,920 |
Filed: |
March 28, 1972 |
Current U.S.
Class: |
165/303; 165/84;
165/166; 165/46; 165/167 |
Current CPC
Class: |
F28F
13/10 (20130101); F28D 9/0087 (20130101); F28F
21/065 (20130101); F28F 13/08 (20130101); F28F
13/12 (20130101) |
Current International
Class: |
F28F
21/06 (20060101); F28D 9/00 (20060101); F28F
13/08 (20060101); F28F 21/00 (20060101); F28F
13/00 (20060101); F28d 011/06 () |
Field of
Search: |
;165/1,83,92,12,166,84 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Sukalo; Charles
Attorney, Agent or Firm: Christel & Bean
Claims
I claim:
1. A heat exchanger of the type comprising at least flow space for
passage of a first liquid heat transfer medium in the form of a
comparatively thin flat film, each flow space being bounded on at
least one side by a substantially flat heat transfer plate which
serves partially to define a flow space for a second or another
heat transfer medium, means for periodically flexing said plate to
give periodic variation in the cross section of one or more flow
spaces, and a support system in the second medium flow space.
2. A heat exchanger as claimed in claim 1, in which the flow spaces
are sealed by gaskets.
3. A heat exchanger as claimed in claim 1, in which the flexing of
the heat transfer plate is achieved by mechanical means operatively
connected to said plate.
4. A heat exchanger as claimed in claim 1, in which said means for
flexing said plate includes means for varying the hydraulic
pressure of the medium on one side of said plate.
5. A heat exchanger as claimed in claim 4, in which the hydraulic
pressure is the differential pressure between the flow spaces for
the first and second heat transfer media and means is provided for
cyclically varying this differential pressure.
6. A heat exchanger as claimed in claim 5, in which the cyclically
varying means comprises a throttling system in at least one of said
flow streams.
7. A heat exchanger as claimed in claim 6, in which the throttling
system comprises two arms in parallel, one arm containing an
adjustable valve, and the other arm containing an adjustable valve
in series with an on-off valve.
8. A heat exchanger as claimed in claim 3, in which the heat
transfer plates to be flexed are weakened at the edges.
9. A heat exchanger as claimed in claim 1, of a multi-pass type,
comprising a non-return valve between each two passes.
Description
This invention relates to heat exchangers of the type comprising at
least one flow space in which a liquid heat transfer medium to be
treated flows as a thin substantially flat film, the flow space
being bounded on at least one side of the film by a heat transfer
plate also partially defining a flow space for a second heat
transfer medium.
Such a heat exchanger may be of the gasketed plate type in which
successive flow spaces are defined between plates in spaced
face-to-face relationship and bounded by gaskets which also serve
to control flow of the media from and to supply and return ducts
for the media, which ducts are generally formed by aligned
apertures in the plates.
Alternatively, the heat exchanger may be of the type in which the
plates are welded together into cells each comprising a group of
flow spaces and headers for the supply and discharge of the heat
transfer media.
In the gasketed plate type of heat exchanger, which is currently in
widespread use, there is a tendency towards larger plates. When, as
is usual, the plates are of stainless steel or other metal or
alloy, and are formed with patterns of turbulence promoting
corrugations or other formations, the cost of press tools an
presses for the formation of the plates becomes very high. It will
be appreciated that the turbulence promoting formations also have a
function in stiffening the plates to inhibit deformation under
operating pressure, and crossing of the corrugations, or the
cooperation of other formations is also used to provide interplate
support to prevent deformation of the plates, and that such
function becomes more necessary in the conventional heat exchangers
as the size of the plates increases.
The present invention represents a break with these conventional
types of heat exchanger in that controlled flexing of the plates is
introduced to provide turbulence and promote heat transfer.
It has previously been proposed to provide flexible plates with
spacer elements which extend only part way across a flow space when
the plates are undeflected and to deflect the plates one way or the
other. The purpose was to enable deposits of impurities, such as
fibrous material, building up on the spacer elements to be removed
by switching channels as and when required. In other respects, the
operation was conventional.
The invention consists in a method of heat treating a first liquid
heat transfer medium comprising passing it in a comparatively thin
flat film into a flow space, bounded on at least one side by a
flexible flat heat transfer plate, and cyclically flexing the plate
to vary the cross section of the flow space, while passing a second
medium in heat transfer relationship with the first medium through
the said heat transfer plate.
The present invention further consists in a heat exchanger of the
type comprising at least one flow space for passage of a first
liquid heat transfer medium in the form of a comparatively thin
flat film, the or each flow space being bounded on at least one
side by a substantially flat heat transfer plate which serves
partially to define a flow space for a second heat transfer medium,
and means for cyclically flexing the flat heat transfer plate to
five cyclic variation in the cross section of the or each flow
space for the first heat transfer medium.
Thus, the expensive press tools for complex shapes of turbulence
promoting corrugations are avoided.
Also, the flexing of the plate itself enables satisfactory heat
transfer to be obtained with very viscous materials which cannot be
made turbulent by the conventional turbulence-promoting ridges.
Such viscous materials are normally treated in a so-called swept
surface heat exchanger, and a heat exchanger according to the
invention, with a comparatively small number, even down to one, of
flow passages of the viscous material can provide a satisfactory
heat transfer.
The cyclic flexing of the plates may be such as to give almost
total displacement of the liquid medium in the flow space so that
only very thin films are left at certain instants of the cycle,
followed by an increase in section and a increase of the flow. The
displacement action of the flow channel, by providing velocities
other than in the normal direction of flow, improves the
distribution.
The objections to previous forms of flat plate heat exchanger has
been that heat transfer is inferior to that of plates having
turbulence promoting corrugations unless the plates are very close
together, and this leads to poor distribution across the flow space
and possible blockage by fouling or suspended solids. Cyclic
flexing overcomes these problems.
In the second medium flow spaces a support system may be provided,
for example an expanded metal or plastic mesh. The heat exchanger
would thus consist of thin flat plates which may be regarded as
flexible membranes. The product flow channels being free of
internal encumberance, while the second medium flow spaces contain
a support grid or mesh. The product flow plates may be welded or
all the plates may be sealed by rubber or asbestos gaskets. In the
case of a gasketed design, external and internal support of the
gasket may be provided. Gasket grooves may be accommodated in the
plate, and this will require only a limited press action at the
periphery of the plate surface, or it may be provided by support
frames placed between each of the thin flat plate membranes.
If required a mesh or other compressible support system may also be
incorporated in the flow spaces for the product median, although
this would reduce the amount of flexure available. On the other
hand, it would increase the inherent turbulence in the flow
system.
It will be seen that by flexing the plates to vary the flow
section, the frequency and amplitude of the variations can be
chosen so as to cause variations in the flow and affect the
velocity distribution, the holding efficieny, and also the heat
transfer.
Under certain circumstances, the flexing of the plate can be made
to provide a pumping action, particularly in a multi-pass heat
exchanger having connector grids between the passes. The flexing of
the plate may be by external hydraulic pressure or by mechanical
means. For the case of external hydraulic pressure, this may be
applied from the flow spaces for the second medium. The pumping
action provided may replace or supplement the pump for the medium
in question.
The flexible heat transfer surface may be much thinner than that
used in conventional pressed plate heat exchanger design. The
flexible material may be a metal or a single or laminated plastic
film, using materials such as polyvinylchloride, polypropylene or
polytetrafluorethylene. Although the thermal conductivity of such
plastics materials is low, the membrane type plates may be
sufficiently thin as to offer an economic solution compared with
conventional metallic pressed plates.
Where plastics material plates are employed, either the thickness
or the modulus of elasticity employed adjacent to the plates edges
may be so as to ensure that the displacement action is uniform
across the width of the flow channel.
Changes in the modulus of elasticity may be effected by irradiation
of the polymer material in local areas.
For the specific problem of dealing with very viscous fluids, the
invention may be employed with advantage in a single flow channel.
In this case the service fluid i.e., the other medium, will be
passed through chambers on one or both sides of the heat transfer
channel. By varying the pressure in the chambers a pumping action
will be provided, while at the same time providing conditions for
good heat transfer.
The invention will be further described with reference to the
accompanying drawings, in which:
FIG. 1 and 2 are diagrams illustrating the construction and
operation of one form of heat exchanger according to the
invention;
FIG. 3 is a view similar to FIG. 2 of a modified form of heat
exchanger;
FIG. 4 is a section on the line X--X of FIG. 3;
FIGS. 5, 6 and 7 illustrate three forms of pressure control for use
in heat exchangers;
FIGS. 8 and 9 are diagrams to illustrate a pumping effect in a
multi-pass heat exchanger; and
FIG. 10 is a diagram showing a pressure control system in a
multi-pass heat exchanger.
Referring first to FIGS. 1 and 2, there is shown a group of plates
1 defining flow spaces PA and PB for two heat media, namely the
product and a service fluid respectively. The service fluid flow
spaces PB are packed with a support grid or mesh 2. In the
condition shown in FIG. 1, the pressure of the product is somewhat
greater than that of the service fluid, so that the plates are
flattened against the support grid 2, so that the nominal flow
section in the product flow spaces is maintained.
An example of this design concept uses stainless steel plates
having a heat transfer surface measuring 36 inches .times. 60
inches. The plates are spaced one-eighth inch apart and sealed at
their periphery by conventional rubber gaskets. One or more
non-return valves are provided to ensure that the product only
flows out of the discharge side of the product flow channel. To
reach the condition of FIG. 2, a super-pressure in excess of 2
p.s.i. is applied to the service fluid chambers, causing a
displacement in the product channel equivalent to a reduction in
spacing of the plates by one-tenth inch. To ensure the maintenance
of an adequate flow channel of the product side during the filling
part of the cycle, it is preferred to maintain a super-pressure of
at least 2 p.s.i. between the product channel and the service fluid
channels. Thus, the pressure variation between the two channels
swings from -2 p.s.i. to +2 p.s.i. The frequency of pressure change
depends upon the product, its viscosity, and whether or not it is
saturated with gas. Depending upon the materials of construction
and the heat transfer problem, the frequency of pressure change
would be between 0.1 and 2 cycles/second.
Air or gas should be excluded from the system as the
compressibility will absorb the pressure pulses and limit the
effect on the plates themselves.
When using plates of uniform stiffness, the plates 1 tend to bow
out from their flat condition (shown in dashed lines in FIG. 2) so
that their maximum deflection is only achieved at the centre region
of the plates. In order to get a greater deflection over a major
area of the plate, the plates may be provided with a weakened area
3 at the edges, as shown in FIGS. 3 and 4. In this form, the plates
act as diaphragms, and the whole region away from the edges moves
as a substantially flat zone bodily towards the adjacent plate,
away from the rest position shown in dashed lines, so that there is
a greater volume reduction in the flow space.
FIG. 5 illustrates one mode of achieving cyclic variation of the
hydraulic conditions by cyclic throttling on the output side of the
service fluid flow space PB. This is achieved by the use of a
throttling system consisting of parallel arms comprising
respectively an adjustable valve 4 and an adjustable valve 5 in
series with an on-off valve 6. This three valve system has the
advantages of allowing control of the pressure level by means of
the adjustable valves, avoiding complete shut-off when the valve 6
is closed, and allowing control of the pressure differential.
FIG. 6 shows an arrangement in which a system of valves 4, 5 and 6
is arranged in the output sides of both the product and service
fluid flow spaces PA and PB.
As shown in FIG. 7, it is also possible to have the throttling
system of valves 4, 5 and 6 in the inlet side of either or both
flow systems. It is also possible to throttle the output side of
the product flow stream.
FIGS. 8 and 9 illustrate how cyclic variation of pressure on one
side of the heat exchanger can exert a pumping action on the other
side. The plates 1 are shown as constituting a downward pass 1a
flanked by two upward passes 1b. Only one product flow passage of
each pass is shown, although it will be appreciated that each pass
could consist of a number of flow passages in parallel. Non-return
valves 7, 8 and 9 are provided.
When the pressure is high in the service fluid side of the upward
passes 1b and low in that of the downward pass 1a, product flows
through the non-return valves 7 and 9, while the non-return valve 8
is closed. Upon reversal of the pressure condition, so that the
system moves from the FIG. 8 condition to that of FIG. 9,
non-return valve 8 opens and non-return valves 7 and 9 close, so
that product flows into the upward passes and out of the downward
pass in a forward direction. The product is thus pumped
successively through the non-return valves 7, 8 and 9 by the cyclic
pressure variation in the service fluid sides taking plate
180.degree. out of phase.
FIG. 10 illustrates a simple form of control system for operating a
multi-pass heat exchanger as described with reference to FIGS. 8
and 9. A pump 11 for the service fluid feeds two service fluid
inlet lines 12 and 13 for the upward and downward passes 1b and 1a
respectively, and the outlet lines for the service fluids are
provided with variable throttling systems comprising three valves
4, 5 and 6 as described with reference to FIG. 5. A product pump 14
is provided to ensure that the first upward pass 1b is filled. The
on-off valves 6 operate out of phase to achieve the pumping action
previously described. The pulse levels set by the adjustable valves
4 and 5 in the throttling systems may be automatically adjusted in
accordance with the pressure levels prevailing in the opposed
product flow channels by suitable control equipment is desired.
With multi-pass operation, there could be sufficient stages, and
also sufficient pressure differential, to cause total blockage of
the flow passage in successive stages of the equipment, thus
providing a pumping action which is comparable with a peristaltic
pump.
In the case of the single heat transfer passage, or a pair of
passages arranged back to back there is also the possibility of
providing the compression of the flow channel by mechanical means
such as the roller in a peristaltic pump design, although it will
be appreciated that this would limit the heat transfer to one wall
of the flow chamber.
Even such a simple design would provide in comparison with the
swept surface heat exchanger, a much bigger heat transfer area at a
lower cost per square foot.
Various modifications may be made within the scope of the
invention.
* * * * *