U.S. patent number 3,860,222 [Application Number 05/412,481] was granted by the patent office on 1975-01-14 for cooling system for vacuum furnaces.
This patent grant is currently assigned to Wall Colmonoy Corporation. Invention is credited to Clifford C. Tennenhouse.
United States Patent |
3,860,222 |
Tennenhouse |
January 14, 1975 |
COOLING SYSTEM FOR VACUUM FURNACES
Abstract
A vacuum furnace construction of a type particularly suitable
for brazing, heat treating, sintering, annealing and other thermal
processing of metal components involving a heating thereof to
temperatures ranging up to about 2,300.degree.F. The furnace
incorporates a cooling system to effect a rapid cooling of the
workpieces at the conclusion of the thermal process without
exposing the components to oxidation attack at the high
temperatures prevalent in the vacuum furnace during the cooling
cycle. The invention further contemplates an improved heat
exchanger construction through which an inert cooling gas is
adapted to be circulated for reuse in the cooling system of the
vacuum furnace.
Inventors: |
Tennenhouse; Clifford C. (Troy,
MI) |
Assignee: |
Wall Colmonoy Corporation
(Detroit, MI)
|
Family
ID: |
23633169 |
Appl.
No.: |
05/412,481 |
Filed: |
November 2, 1973 |
Current U.S.
Class: |
266/250; 266/254;
373/110; 373/113; 373/137; 432/205 |
Current CPC
Class: |
F27D
11/02 (20130101); C21D 1/773 (20130101); H05B
3/00 (20130101); F27B 5/16 (20130101); F27B
2005/068 (20130101); F27B 2005/143 (20130101); F27B
2005/162 (20130101); F27B 2005/169 (20130101) |
Current International
Class: |
C21D
1/773 (20060101); C21D 1/74 (20060101); F27B
5/16 (20060101); F27B 5/00 (20060101); F27D
11/00 (20060101); F27D 11/02 (20060101); H05B
3/00 (20060101); F27B 5/06 (20060101); F27B
5/14 (20060101); C21d 001/06 () |
Field of
Search: |
;266/5C,5E,5R,24
;432/205 ;13/31 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Custer, Jr.; Granville Y.
Assistant Examiner: Feinberg; Craig R.
Attorney, Agent or Firm: Harness, Dickey & Pierce
Claims
What is claimed is:
1. A vacuum furnace comprising a structural enclosure defining a
three dimensional chamber, an insulating liner in said enclosure
and disposed in spaced relationship from the inner surfaces thereof
dividing said chamber into an outer zone and an inner work zone, a
support in said work zone for supporting work to be thermally
processed, heating means for heating said work zone, removable
closure means sealingly disposed on said enclosure for gaining
access to said chamber, an inlet port in said enclosure for
introducing a cooling fluid into said outer zone, an outlet port in
said enclosure for withdrawing the cooling fluid from said outer
zone, a baffle disposed between the interior surface of said
enclosure and the exterior surface of said insulating liner for
dividing said outer zone into an inlet zone disposed in
communication with said inlet port and an outlet zone disposed in
communication with said outlet port, said insulating liner
including a removable section for gaining access to said work zone,
nozzle means in said liner for directing cooling fluid from said
inlet zone into said work zone and in cooling relationship with
respect to any work on said support therein, discharge means in
said liner for discharging cooling fluid from said work zone into
said outlet zone, cooling means interposed between said inlet port
and said outlet port exteriorly of said enclosure for cooling said
cooling fluid withdrawn from said work zone, and including means
for circulating said cooling fluid through said inlet zone, through
said work zone, through said outlet zone and through said cooling
means.
2. The vacuum furnace as defined in claim 1 further including
cooling means disposed in heat transfer relationship with the
exterior surface of said enclosure.
3. The vacuum furnace as defined in claim 1 in which said nozzle
means in said liner is disposed in a position remote from said
discharge means therein.
4. The vacuum furnace as defined in claim 1 wherein said insulating
liner comprises sheet steel having a graphite heat insulating wool
over the inner surfaces thereof.
5. The vacuum furnace as defined in claim 1 in which said nozzle
means comprises a dish shaped member formed with an aperture in the
center thereof disposed in communication with said work zone and a
conically shaped member disposed in spaced relationship from said
dish shaped member and defining therebetween an annular nozzle
passageway disposed in communication with said outer zone and the
cooling fluid therein, said dish shaped member and said conical
member oriented so as to intercept any radiant heat waves reflected
through the aperture of said nozzle means.
6. The vacuum furnace as defined in claim 1 in which said nozzle
means are oriented so as to introduce the cooling fluid into said
work zone in the form of a high velocity stream directed toward any
work on said support therein and to cause a toroidal flow pattern
of cooling fluid within said work zone.
7. The vacuum furnace as defined in claim 1 in which said work zone
is of a generally cylindrical configuration formed with said nozzle
means in one end thereof and said discharge means in the opposite
end thereof and wherein said heating means extend longitudinally
around the inner side of said work zone encircling said support and
any work thereon.
8. The vacuum furnace as defined in claim 1 in which said removable
section of said liner incorporates said nozzle means therein and is
disposed adjacent to said removable closure means in said
enclosure.
Description
BACKGROUND OF THE INVENTION
The use of vacuum-type furnaces for the thermal processing of
workpieces is receiving widespread acceptance because of the
protection from oxidation attack afforded to such workpieces at the
elevated temperatures employed. While the vacuum furnace of the
present invention is particularly applicable for use in brazing,
significant advantages can also be obtained in the utilization of
such furnaces in various types of heat treating, sintering,
annealing and similar thermal processes frequently requiring
temperatures that are as high as about 2,300.degree.F at which
metal components are extremely susceptible to chemical reaction and
oxidation attack.
A continuing problem associated with high temperature vacuum
furnaces has been the long length of time required to cool the
workpieces at the completion of a thermal processing cycle in order
to enable the furnace to be opened and the workpieces to be removed
therefrom. The elaborate radiant heat insulation required in
furnaces of this type in addition to the construction necessary to
enable the attainment of high vacuums has at least in part been
responsible for rendering cooling systems as heretofore proposed
either unsuccessful from an operational standpoint or impractical
from a commercial standpoint. A further complication is the
necessity of protecting the metal work components from oxidation
attack during the cooling cycle at least until reasonably moderate
temperature levels are attained at which they are less prone to
oxidation attack. Among the various solutions heretofore proposed
are the circulation of an inert gas through the furnace which has
been found inadequate to provide the requisite cooling capacity as
well as the direct introduction of liquid nitrogen into the work
zone. The latter technique, although effective insofar as cooling
is concerned, is very expensive and can only be employed on parts
that are to be quenched at an oil quench rate or faster.
The cooling system in accordance with the vacuum furnace
construction of the present invention provides for a simple and
economical solution to the cooling problem of thermally processed
parts whereby a significant reduction in the process cycle is
achieved thereby substantially increasing the efficient use of the
furnace and the productive output thereof.
SUMMARY OF THE INVENTION
The benefits and advantages of the present invention are achieved
by a vacuum furnace which consists of a structural enclosure
defining an internal three-dimensional chamber within which a
thermal insulating liner is placed and is spaced inwardly of the
inner surfaces of the enclosure defining an outer zone and an inner
work zone in which the workpieces are adapted to be disposed during
a thermal processing cycle. The work zone further incorporates a
support on which the workpieces are adapted to be placed and the
inner surface of the insulating liner is provided with a plurality
of heating elements for heating the work zone as well as the
workpieces therein. The outer zone is divided by means of a baffle
into an inlet zone connected to an inlet port through which a
cooling gas such as argon, for example, is adapted to enter and an
outlet zone formed with an outlet port for discharging the cooling
gas from the furnace.
The insulating liner is formed with an annular nozzle arrangement
disposed in communication with the inlet zone for receiving and
discharging the cooling gas in the form of a high velocity stream
and in impinging and cooling relationship with respect to the
workpieces in the work zone to effect a relatively rapid cooling
thereof at the completion of a thermal processing cycle. The
cooling gas preferably travels in a toroidal flow pattern within
the work zone and is withdrawn through a discharge opening in the
insulating lining positioned at a point remote from the nozzle. The
discharge opening is positioned in communication with the outlet
zone from which the cool gas is withdrawn and is passed through a
heat exchanger for a cooling thereof.
The vacuum furnace further includes a removable closure in a wall
of the furnace for gaining access to the interior of the furnace
and a removable section in the heat insulating liner for gaining
access to the work zone and work positioned on the work support
therein. Preferably, the nozzle arrangement is embodied in the
removable section of the insulating lining and is disposed adjacent
to the removable closure in the furnace to facilitate a loading and
unloading of workpieces from the work zone. The vacuum furnace also
includes a system including control means incorporating sensing
means therein for sensing the temperature and pressure existing
within the vacuum furnace and for controlling the quantity and rate
of circulation of the inner cooling fluid through the furnace.
The present invention further contemplates an improved heat
exchanger construction including a pair of spaced headers formed
with an inlet port and an outlet port, respectively, for receiving
the inert cooling gas to be cooled. The headers are interconnected
by a plurality of conduits and a corresponding plurality of heat
exchanger tubes extend through the conduits and through the headers
at the ends thereof and project outwardly of the headers such that
the ends of the tubes can be connected to a supply of a heat
exchange fluid. In this manner, no connections are present along
the lengths of the heat exchange tubes which are disposed within
the evacuated interior of the heat exchanger so that any leaks that
may occur therein can be located and repaired without removing the
heat exchange fluid and without contaminating the atmosphere within
the vacuum furnace by heat exchange fluid.
Additional benefits and advantages of the present invention will
become apparent upon a reading of the description of the preferred
embodiments taken in conjunction with the accompanying
drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side elevational view, partly schematic, illustrating a
vacuum furnace system and ancillary equipment and controls arranged
in accordance with a preferred practice of the present
invention;
FIG. 2 is a magnified side elevational view, partly in section, of
a vacuum furnace and the cooling system incorporated therein;
FIG. 3 is a magnified fragmentary sectional view of the furnace
closure seated against the upper wall of the vacuum furnace as
encompassed by the dotted circle indicated at 3 in FIG. 2;
FIG. 4 is a schematic side elevational view of the relative
disposition of the controls, heat exchanger and vacuum pump of a
vacuum furnace system as shown in FIG. 1;
FIG. 5 is a plan view of a heat exchanger;
FIG. 6 is an end elevational view of the heat exchanger shown in
FIG. 5; and
FIG. 7 is a magnified fragmentary sectional view of the header
portion and heat transfer tubes disposed in the transverse conduits
of the heat exchanger shown in FIG. 6 as viewed substantially along
the line 7--7 thereof.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now in detail to the drawings and as may be best seen in
FIG. 1 a vacuum furnace system of a general type to which the
present invention is applicable includes a vacuum furnace 10
connected by means of conduits 12 and 14 to a pumping and cooling
system 16 which is controlled by a control system housed in a
control panel 18. The control system incorporates appropriate
temperature and pressure sensing devices (not shown) for monitoring
the conditions prevalent in the interior of the vacuum furnace. The
vacuum furnace 10 as best seen in FIGS. 2 and 3 consists of a
generally circular cylindrical receptacle or tank 20 having a dish
shaped bottom 22 to which a series of upright legs 24 are securely
affixed. The upper portion of the tank 20 is provided with a
generally flat top panel 26 which is securely fastened by means of
screws to an annular flange 28 encircling the periphery of the
upper edge of the tank. The top panel 26 is formed with a circular
opening 30 in the center thereof over which a dome shaped closure
member 32 is removably positioned in sealing engagement
thereagainst.
As best seen in FIG. 3, the lower edge of the closure member 32 is
provided with an annular flange 34 which is provided with a groove
36 in the lower face thereof in which a resilient O-ring type seal
38 of a heat-resistant elastomeric material, such as a silicone
rubber, is removably disposed. The face of the O-ring seal 38 is
adapted to be seated in sealing engagement against the upper
surface of the top panel 26 adjacent to the opening 30.
In a manner similar to that shown in FIG. 3, an O-ring seal 40 is
adapted to be received in the face of the groove of the annular
flange 28 for sealing the peripheral portion of the top panel 26 to
the tank 20.
A radiant heat insulating liner 42, including a generally circular
cylindrical sheet metal side wall 44 connected at the upper and
lower edges thereof to annular radially inwardly extending end
walls 46, is mounted in spaced substantially concentric
relationship with respect to the inner surface of the wall of the
tank and is supported in spaced relationship from a bottom thereof
by means of supporting legs 48. The lower wall of the insulating
liner is formed with an outlet assembly comprising a generally
dish-shaped member 50 formed with an axially downwardly extending
discharge tube 52 and an inverted conically-shaped deflection plate
54 supported on spacers 56 which is positioned in spaced central
alignment above the discharge tube 52.
The upper end wall of the insulating liner is provided with a
nozzle assembly including a lower dish-shaped member 58 of a
generally circular conical configuration which is formed with a
discharge opening 60 in the center thereof. A conical deflector
plate 62 is supported by spacers 64 in spaced substantially
parallel relationship above the upper surface of the dish-shaped
member 58 and defines an annular downwardly convergent nozzle
opening 66 which communicates with the discharge opening 60.
As best seen in FIG. 2, the insulating liner, including the nozzle
assembly and the discharge assembly, divide the interior of the
vacuum furnace into an outer zone and an inner work zone. The inner
work zone is provided with a table or support 68 projecting
upwardly through the discharge assembly on which workpieces which
are to be thermally processed are adapted to be stacked. A
plurality of electrical resistance heating elements 70, which
preferably comprise graphite tape elements, are supported between
upper and lower terminals 72, 74 which extend through insulators 76
mounted in correspondingly-shaped apertures formed in the side wall
44 of the insulating liner. The heating elements 70 are arranged in
vertically spaced relationship around the inner surface of the
insulating liner and around the workpieces adapted to be placed on
the upper surface of the work support 68. The ends of the terminals
72 are connected to a common annular bus bar 78, while the ends of
the terminals 74 are connected in common to an annular bus bar 80.
Each bus bar is in turn connected to a feed-through terminal
extending in sealed relationship through the wall of the tank such
as the feed-through device indicated at 82 in FIG. 2, which is
connected to the bus bar 80.
The interior of the insulating liner is covered with a suitable
heat-resistant insulating layer 84 which may be comprised of any
one of a variety of suitable commercially available materials
including carbon felt and ceramic fiber blankets. The inner
surfaces of the nozzle assembly and a discharge assembly of the
insulating liner are similarly covered with the insulating
layer.
In accordance with the arrangement shown in FIG. 2, the angularity
of the openings defined by the nozzle opening 66 and the discharge
opening in the discharge assembly are oriented in relationship to
the disposition of the insulating liner and insulating layer
thereon so as to intercept any heat rays radiating or reflecting
from the surfaces within the interior of the work zone including
the radiant heating elements 70. Accordingly, the outer zone is
maintained at a substantially lower temperature than the work zone
and this is further controlled by means of cooling channels 86
which are brazed or welded to the exterior surfaces of the vacuum
furnace including the side walls of the tank 20, the dome-shaped
closure 32, the top panel 26 and the dish-shaped bottom 22. A
suitable cooling fluid, such as water for example, is circulated
through the channels via a suitable header and flow control valves
(not shown) connected thereto to facilitate a cooling of the vacuum
furnace at the completion of a thermal processing cycle and to
maintain the shell of the tank within an acceptable temperature
range throughout the cycle.
The outer zone between the insulating liner and the inner wall of
the tank is divided by an annular baffle 88, as best seen in FIG.
2, into an upper or inlet zone and a lower or outlet zone. The
upper zone is provided with a flanged inlet port 90, to which the
conduit 12 is connected for supplying a cooling fluid such as
substantially dry argon to the upper portion of the furnace for
discharge in cooling relationship through the nozzle opening 66.
The lower zone is connected to a flanged outlet port 92, to which
the conduit 14 is connected for removing the inert heat-exchanged
gas from the lower zone as it is discharged from the work zone
through the discharge assembly. The conduit 14 is also effective
for removing air and other gaseous products from the furnace
interior in order to attain the desired vacuum during the thermal
processing cycle.
Referring now to FIG. 4, the conduit 14, as schematically shown, is
connected to the inlet side of a blower, such as a Rootes blower
94, which functions both to evacuate the interior of the vacuum
furnace 10, as well as to circulate the inert cooling gas through
the furnace and heat exchange equipment. During a vacuum thermal
processing cycle, the blower 94 is supplemented by a vacuum pump 96
which is connected to the outlet side of the blower 94 through
remotely-actuated valve 98 which is controlled by the control
system within the control panel 18.
At the conclusion of a thermal processing cycle, and at the
initiation of a cooling cycle, the valve 98 is closed and inert gas
is admitted into the interior of the furnace from a supply tank
indicated at 100 through a remotely-actuated valve 102, which is
connected by means of a supply line 104 to the lower outer zone of
the furnace. The inert gas is withdrawn from the interior of the
furnace through the conduit 14 by the blower 94 and is circulated
through a heat exchanger 106 to effect a cooling thereof,
whereafter it passes through a remotely-actuatable control valve
108 back into the upper outer zone of the furnace for discharge
through the nozzle assembly against the workpieces disposed within
the work zone.
In order to provide a uniform rate of cooling of the workpieces and
to avoid an overload of the heat exchanger, the control system
through the flow control valve 102 effects a controlled addition of
inert gas to the vacuum furnace in response to the temperature of
the inert gas discharged from the outlet side of the blower 94 as
sensed by a temperature sensing device 110 connected to the control
panel 118. For example, at the conclusion of a vacuum brazing
operation of workpieces at a temperature of about 1,400.degree.F,
electric power to the heating elements is discontinued and the
interior of the furnace immediately commences to cool through
normal radiation and convection approaching a level of about
1,000.degree.F, at which time the inert cooling gas cooling cycle
is initiated. The inert or other nonoxidizing gas is introduced
through the supply line 104 into the furnace until a pressure of
about 0.2 atmospheres absolute is attained. As the workpieces
within the furnace progressively cool, the quantity of heat removed
therefrom by the cooling gas decreases, which is reflected in a
reduction in the temperature of the gas as sensed by the sensing
device 110. As the temperature of the gas decreases, the control
system causes an actuation of the flow control valve 102, causing
additional gas to be admitted into the interior of the furnace,
causing an increase in the pressure thereof so as to increase the
density of the cooling gas and the quantity of heat extracted
thereby. Accordingly, by monitoring the temperature and pressure of
the cooling gas being circulated through the vacuum furnace, a
substantially uniform rate of heat removal is provided, which in
turn imposes a substantially uniform load on the heat exchanger
106.
It will be understood that alternative satisfactory arrangements
and controls for the ancillary equipment can be employed in
combination with the vacuum furnace construction as shown in FIG. 2
in order to obtain the increased cooling rate of the workpieces at
the completion of a thermal processing cycle. It will also be
understood that the chemical reactivity of the cooling gas as
established by its composition and nonoxidizing properties can be
varied consistent with the nature of the parts being processed and
their susceptibility to chemical attack and deterioration at the
elevated temperatures encountered during the course of the cooling
cycle.
Referring now to FIGS. 5-7, a gas-to-liquid heat exchanger is shown
which is constructed in accordance with another embodiment of the
present invention to provide for a rapid cooling of the cooling
gas, while at the same time minimizing the likelihood of a
contamination of the vacuum furnace atmosphere as a result of
leakage of the heat exchange liquid utilized for cooling the gas.
As shown, the heat exchanger comprises a first header 112 having an
inlet port 114 at one end thereof and being closed by a cap 116 at
the opposite end thereof. A second header 118 is disposed in spaced
substantially parallel relationship with respect to the first
header and is formed with an outlet port 120 at an end opposite to
the inlet port in the first header and is closed at its opposite
end by means of a cap 122. A plurality of conduits 124 extend in
spaced transverse relationship relative to the first and second
headers and the end portions thereof extend through the header
walls and project into the interior of the headers. The end
portions of the conduits are secured in gas-tight sealed
relationship in the headers such as by means of brazing or
welding.
A heat transfer tube 126 extends axially through each conduit 122
and the end portions thereof project through the outer walls of the
headers and are sealingly fastened therein such as by means of
welding. The central portion of the heat transfer tubes 126 is
formed with a plurality of radially extending elements or bristles
128 secured in heat exchange contact at their inner ends to the
outer surface of the tube. The bristles 128 serve to substantially
increase the effective heat transfer area of the heat transfer
tubes and are adapted to be disposed in heat transfer relationship
with the gas passing through the transverse conduits from the first
header to the second header. An extraction of heat from the
bristles through the wall of the transfer tubes is accomplished by
a cooling liquid such as water which enters an inlet elbow 130 at
the closed end of the first header 112 as shown in FIG. 5 and is
discharged at the opposite end of the second header 118 through a
discharge elbow 132. The cooling liquid travels in a serpentine
manner from the inlet elbow to the discharge elbow by means of the
U-shaped connectors 134 secured to the projecting end portions of
the heat transfer tubes connecting adjacent pairs to each other. In
accordance with this arrangement the integral nature of the heat
transfer tubes disposed within the headers and transverse conduits
minimizes any possibility of a leakage of liquid into the evacuated
interior of the heat exchanger and a contamination of the
atmosphere of the vacuum furnace. Any leakage that may occur most
likely will occur at the connections between the ends of the tubes
and the U-shaped connectors 134 which is exterior of the heat
exchanger and can be readily observed and repaired as may be
required from time to time.
It will also be appreciated that alternative satisfactory heat
transfer tubes can be employed in lieu of the bristle-type tube 126
shown in FIG. 7. In the embodiment illustrated, the bristles or
heat transfer elements are integrally formed on the surface of the
tubing by means of a mechanical cutting action leaving the cut
chips attached at their inner ends to the tube surface, assuring
excellent heat transfer between the bristles and tube walls.
Alternative satisfactory heat transfer tubes are commercially
available which can be satisfactorily employed to achieve benefits
similar to those obtained by the tube 126.
While it will be apparent that the invention herein disclosed is
well calculated to achieve the benefits and advantages as
hereinabove set forth, it will be appreciated that the invention is
susceptible to modification, variation and change without departing
from the spirit thereof.
* * * * *