U.S. patent number 3,777,562 [Application Number 05/243,595] was granted by the patent office on 1973-12-11 for methods of and means for determining the calorific value of combustible gases.
This patent grant is currently assigned to Precision Machine Products, Inc.. Invention is credited to William H. Clingman, Jr..
United States Patent |
3,777,562 |
Clingman, Jr. |
December 11, 1973 |
**Please see images for:
( Certificate of Correction ) ** |
METHODS OF AND MEANS FOR DETERMINING THE CALORIFIC VALUE OF
COMBUSTIBLE GASES
Abstract
Methods of and means for measuring the calorific value of
combustible gases wherein a mixture of a combustible gas and a
combustion-supporting gas is burned in one or more flames, the
temperature or temperatures of the burned gases being monitored and
the volume ratio of the combustion-supporting gas to the
combustible gas being adjusted so as to maintain said temperature
or the average of said temperatures at substantially maximum; the
volume ratio of said gases which produces said maximum temperature
varying substantially directly with the calorific value of said
combustible gas.
Inventors: |
Clingman, Jr.; William H.
(Dallas, TX) |
Assignee: |
Precision Machine Products,
Inc. (Dallas, TX)
|
Family
ID: |
27431485 |
Appl.
No.: |
05/243,595 |
Filed: |
April 13, 1972 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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21410 |
Mar 20, 1970 |
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Current U.S.
Class: |
374/37;
374/112 |
Current CPC
Class: |
G01N
25/32 (20130101) |
Current International
Class: |
G01N
25/20 (20060101); G01N 25/32 (20060101); G01n
025/30 () |
Field of
Search: |
;73/190 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Goldstein; Herbert
Parent Case Text
This application is a continuation-in-part of my copending
application Ser. No. 21,410, filed Mar. 20, 1970, now abandoned.
Claims
I claim:
1. A method of determining the calorific value of a combustible gas
including
mixing a combustible gas with a combustion supporting gas and
burning the resulting mixture,
measuring the temperature of the burned mixture,
adjusting the volume ratio of the gases until the temperature of
the burned mixture is at substantially maximum,
and ascertaining the volume ratio of said gases which produces said
maximum temperature and which is proportional to the calorific
value of the combustible gas.
2. A method as defined in claim 1 wherein
the gases prior to burning are at approximately ambient
temperature.
3. A method as defined in claim 1 wherein
said method is performed at ambient temperatures of from
approximately -40.degree. F. to 130.degree. F.
4. A method as defined in claim 1 wherein
the combustion supporting gas is dry air.
5. A method as defined in claim 1 wherein
the step of adjusting the volume ratio of the gases comprises
regulating the rate of supply of at least one of said gases to the
mixture until the temperature of the burned mixture is at
substantially maximum.
6. A method as defined in claim 5 wherein
the rate of supply of the combustion supporting gas is
regulated.
7. A method as defined in claim 5 wherein
the rate of supply of the combustible gas is regulated.
8. A method as defined in claim 1 wherein
the step of ascertaining the volume ratio of the gases comprises
separately metering the rate of supply of said gases to said
mixture.
9. A method as defined in claim 1 including
continually supplying to the mixture additional volumes of one of
the gases in small pulses to provide a continuing series of small
perturbations on the total flow rate of such gas,
measuring the pulses of the temperature of the burned mixture
related to the pulses of the flow rate,
adjusting the flow rate of one of said gases so as to provide a
predetermined temperature pulse amplitude.
10. A method as defined in claim 1 including
varying the volume of one of the gases mixed with the other gas to
provide different mixtures,
and recording the different temperatures of the burned
mixtures.
11. A method of determining the calorific value of a combustible
gas including
separating a volume of combustion supporting gas into two equal
divisions,
separately mixing the separated divisions with separate unequal
divisions of a volume of combustible gas whereby the division of
the combustible gas supplied to one of the separate mixtures is
slightly greater than the division of said gas supplied to the
other separate mixture,
separately burning said mixtures,
measuring the temperature difference between the burned
mixtures,
adjusting the volume ratio of the gases prior to division thereof
until the temperature difference of the burned mixtures is at a
predetermined value,
and ascertaining the volume ratio of said gases which produces said
temperature difference and which is proportional to the calorific
value of said combustible gas.
12. A method as defined in claim 11 wherein
the gases prior to burning are at approximately ambient
temperature.
13. A method as defined in claim 11 wherein
said method is performed at ambient temperatures of from
-40.degree. F. to 130.degree. F.
14. A method as defined in claim 11 wherein
the combustion supporting gas is dry air.
15. A method as defined in claim 11 wherein
the step of adjusting the volume ratio of the gases comprises
regulating the rate of supply of at least one of said gases to the
mixture until the average temperature of the burned mixtures is at
substantially maximum.
16. A method as defined in claim 15 wherein
the rate of supply of the combustion supporting gas is
regulated.
17. A method as defined in claim 15 wherein
the rate of supply of the combustible gas is regulated.
18. A method as defined in claim 11 wherein
the step of ascertaining the volume ratio of the gases comprises
separately metering the rate of supply of said gases to said
mixture.
19. A method as defined in claim 11 including
varying the volume of one of the gases mixed with the other gas to
provide different mixtures,
and recording the different temperatures of the burned
mixtures.
20. A method as defined in claim 11 wherein
the step of adjusting the volume ratio of the gases comprises
regulating the rate of supply of at least one of said gases prior
to division thereof in accordance with the temperature difference
between the separately burned mixtures.
21. An apparatus for determining the calorific value of a
combustible gas including
means for mixing a combustible gas and a combustion supporting
gas,
means for burning the mixture,
means for supplying said mixture to the burning means,
means for sensing the temperature of the burned mixture and
adjusting the volume ratio of the gases until the temperature is at
substantially maximum,
and means for ascertaining the volume ratio of said gases which
produces said maximum temperature and which is proportional to the
calorific value of the combustible gas.
22. An apparatus as defined in claim 21 including
means for regulating the volume of at least one of the gases to
adjust the volume ratio of said gases.
23. An apparatus as defined in claim 22 wherein
the volume of the combustion supporting gas is regulated.
24. An apparatus as defined in claim 22 wherein
the volume of the combustible gas is regulated.
25. An apparatus as defined in claim 21 wherein
the means for ascertaining the volume ratio of the gases comprises
means for separately metering the rate of supply of said gases to
the mixing means.
26. An apparatus as defined in claim 21 including
means for continually supplying to the mixing means additional
volumes of one of the gases in small pulses to provide a continuing
series of small perturbations on the total flow rate of such
gas,
measuring means responsive to the polarity of the pulses for
measuring the pulses of the temperature of the burned mixture
related to the pulses of the flow rate and producing an output
related to said polarity,
and adjusting means responsive to the output of the measuring means
for adjusting the flow rate of one of said gases so as to provide a
predetermined temperature pulse amplitude.
27. An apparatus as defined in claim 21 including
means for varying the volume of one of the gases mixed with the
other gas to provide different mixtures,
and means for recording the different temperatures of the burned
mixtures.
28. An apparatus as defined in claim 21 wherein
the burning means is exposed to ambient temperatures of from
-40.degree. F. to 130.degree. F.
29. An apparatus as defined in claim 21 wherein
the combustion supporting gas is dry air.
30. An apparatus as defined in claim 21 wherein
the gases prior to burning are at approximately ambient
temperatures.
31. An apparatus as defined in claim 21 wherein
the mixing means comprises a pair of separate mixers,
the burning means comprises a pair of separate burners in separate
communication with the separate mixers,
the supplying means comprises means for equally dividing the
combustion supporting gas and separate means for unequally dividing
the combustible gas prior to separate mixing of the divisions of
the gases whereby one of the mixtures contains a slightly greater
quantity of said combustible gas than the other mixture,
the sensing means comprises a separate sensor for each burner,
the volume ratio of said gases being adjusted prior to division
thereof to produce the substantially maximum average temperature of
the burned mixtures.
32. An apparatus for determining the calorific value of a
combustible gas including
a pair of separate mixer means,
means for supplying equal divisions of a combustion supporting gas
to each mixer means,
means for supplying unequal divisions of a combustible gas to the
separate mixer means whereby one of the resulting mixtures contains
a slightly greater quantity of the combustible gas than the other
mixture,
separate means separately communicating with said separate mixer
means for separately burning said mixtures,
means for measuring the temperature difference of the burned
mixtures and then adjusting the volume ratio of the gases prior to
division thereof until the temperature difference is at a
predetermined value,
and means for ascertaining the volume ratio of said gases which
produces said temperature difference and which is proportional to
the calorific value of said combustible gas.
33. An apparatus as defined in claim 32 including
means for regulating the volume of at least one of the gases to
adjust the volume ratio of said gases.
34. An apparatus as defined in claim 33 wherein
the volume of the combustion supporting gas is regulated.
35. An apparatus as defined in claim 33 wherein
the volume of the combustible gas is regulated.
36. An apparatus as defined in claim 32 wherein
the means for ascertaining the volume ratio of the gases comprises
means for separately metering the rate of supply of said gases to
the mixing means.
37. An apparatus as defined in claim 32 including
means for varying the volume of one of the gases mixed with the
other gas to provide different mixtures,
and means for recording the different temperatures of the burned
mixtures.
38. An apparatus as defined in claim 32 wherein
the burner is exposed to ambient temperatures of from -40.degree.
F. to 130.degree. F.
39. An apparatus as defined in claim 32 wherein
the combustion supporting gas is dry air.
40. An apparatus as defined in claim 32 wherein
the gases prior to burning are at approximately ambient
temperatures.
41. An apparatus as defined in claim 32 including
means for regulating the rate of supply of at least one of the
gases prior to division thereof until the temperature difference
between the separately burned mixtures is at a predetermined
value.
42. A method of determining the calorific value of combustible
gases including
equally dividing a combustion supporting gas and separately mixing
the separated equal divisions of the gas with separate unequal
divisions of a combustible gas whereby the division of the
combustible gas supplied to one of the mixtures is slightly greater
than the division of said gas supplied to the other mixture,
burning said mixtures separately,
measuring the temperatures of the burned mixtures,
adjusting the volume ratios of the gases prior to division thereof
to produce the substantially maximum average temperatures of the
burned mixtures,
and ascertaining the volume ratios of said gases which produce said
maximum average temperature and which is proportional to the
calorific value of the combustible gas.
Description
BACKGROUND OF THE INVENTION
The calorific value of a combustible gas has been defined as the
quantity of heat in British Thermal Units (BTU) which is released
when one standard cubic foot of gas is completely oxidized at a
temperature of 60.degree. F. and any water produced by oxidation is
in the liquid state. When the gas is a hydrocarbon or a mixture of
hydrocarbons, the oxidation products for complete oxidation are
carbon dioxide and water; and when one standard cubic foot of said
gas is mixed with a sufficient quantity of oxygen at 60.degree. F.
to completely oxidize said gas, oxidation is carried out and the
products thereof, carbon dioxide and water, are cooled to
60.degree. F. and all water is condensed to liquid state, the total
heat given off, including the heat transferred in cooling the said
products and in condensing all of the water, is the calorific value
of said gas. As defined in this manner, the calorific value is a
function only of the chemical composition of the combustible gas,
whereby it is possible to determine the calorific value when only
the chemical composition of said gas is known.
Calorific value so defined is used extensively in industry as a
measure of the quality of a gas or other fuel. IF a If is to be fed
to a burner, the proper operation of the latter is often highly
dependent upon calorific value whereby it is essential to control
such value within narrow limits. Accordingly, it is common practice
for suppliers and users of combustible gas to monitor the calorific
value thereof.
Since the calorific value of a combustible gas depends only on its
chemical composition, said value can be determined by a complete
chemical analysis of the gas if the calorific value of each of its
constituents is known; however, this method is time-consuming and
impractical for continuously monitoring the calorific value. All
standard methods for measuring calorific value involve mixing and
burning a known volume of a combustible gas with an excess of
oxygen-containing or combustion-supporting gas, transferring the
resultant heat to a heat absorbing fluid and measuring the quantity
of heat transferred. The conditions for these operations would
ideally be the same as in the above definitions of calorific value.
Any deviation from these conditions will cause the resultant heat
transferred per standard cubic foot of combustible gas in the
measurement to be different from the calorific value.
In practice, it is difficult to maintain the rigid conditions
required for correct measurement, since the initial temperatures of
the combustible and oxygen-containing gases are seldom, if ever,
60.degree. F. Also, the temperature of the combustion products
after heat transfer is not 60.degree. F. and, usually, is higher
than the initial temperature of the gases. The water produced is
seldom condensed to the liquid state and the heat absorbing fluid
never absorbs all of the heat transferred from the combustion
products, since some heat is always lost by radiation and
conduction.
Each of the foregoing deviations is a source of measurement error
and correction thereof requires complicated, expensive apparatus
and, often, special environmental control.
SUMMARY OF THE INVENTION
The basic method of this invention includes the following
steps:
1. the combustible gas is mixed with dry air or other
combustion-supporting or oxygen-containing gas;
2. the mixture is burned in one or more flames;
3. the temperature of these flames or burned gases is
monitored;
4. the volume ratio of the gases is adjusted so as to maintain said
temperature at substantially maximum; and
5. said volume ratio of said gases which produces said maximum
temperature is measured.
This measured volume ratio will be referred to hereinafter as
"critical combustion ratio" and may be defined as that volume ratio
of the gases which produces maximum flame temperature when said
gases are premixed and burned. It has been found that the critical
combustion ratio varies substantially directly with the calorific
value of the combustible gas and that a very accurate indication of
calorific value can be obtained by measuring said critical
combustion ratio.
The physical nature of the critical combustion ratio may be more
readily understood upon consideration of known flame phenomena. It
is well known that the adiabatic temperature of a flame that is
produced by burning a mixture of combustible and
combustion-supporting gases is a function only of the initial
temperature, pressure and chemical composition of the mixture and
that said adiabatic temperature would be reached in the combustion
zone of the flame only if there were no heat losses from the
burning gases. Also, it is well known that if the ratio of
combustion-supporting gas to combustible gas is varied in the
initial mixture, the adiabatic flame temperature varies and that a
critical ratio between the gases exists at which said adiabatic
flame temperature is at maximum. If the initial mixture contains
less combustion-supporting gas than required to achieve this
critical ratio, the adiabatic flame temperature is lower and this
is generally due to there being insufficient oxygen to achieve
complete combustion whereby less heat is released. In the event
that the initial mixture contains combustion-supporting gas in
excess of that required to achieve the critical ratio, the
adiabatic flame temperature is again lower and is generally due to
the necessity of heating such excess. Thus, the critical ratio
between the gases is equal to the critical combustion ratio defined
hereinbefore.
Objects of the invention are to provide improved methods of and
means for measuring the calorific value of combustible gases which
do not depend upon measuring the amount of heat released in
combustion, which are not affected by the errors set forth
hereinbefore, which are simple, which are capable of continuous
simple operation and which are not affected by ambient temperature
and other varying environmental factors.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a diagrammatic view illustrating an apparatus for
carrying out one of the methods of my invention,
FIG. 2 is a view, similar to FIG. 1, of a modified apparatus for
carrying out another method of the invention,
FIG. 2A is a diagrammatic view illustrating the time-dependent
behavior of the total flow of air to the burner of FIG. 2,
FIG. 2B is a diagrammatic view illustrating the effect of continual
small perturbations in the air flow rate on the burned gas
temperature,
FIG. 3 is a view, similar to FIG. 1, of another modified apparatus
for carrying out a third method of the invention,
FIG. 4 is a view, similar to FIG. 1, of a further modified
apparatus for carrying out a fourth method of the invention,
FIG. 4A is an enlarged elevational view, taken on the line 4A--4A
of FIG. 4, showing the recording chart and stylus,
FIG. 5 is a diagrammatic view of the components of the controller
and thermocouple of FIG. 1,
FIG. 6 is a view, similar to FIG. 5, of the components of the
controller and thermocouple of FIG. 2,
FIG. 7 is a view similar to FIG. 5, of the components of the
controller and thermocouple of FIG. 3.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
A preferred method of measuring the critical combustion ratio,
i.e., the measured volume ratio between the combustible gas and dry
air or combustion-supporting or oxygen-containing gas which
produces the maximum flame temperature when said gases are premixed
and burned in a flame, can be best understood by referring to FIG.
1 wherein a suitable apparatus 1 is illustrated diagrammatically.
For convenience, the combustion-supporting or oxygen-containing gas
will be referred to as "dry air" or "air" with the understanding
that any suitable gas is included in this designation. Likewise,
the combustible gas will be merely termed "gas."
The apparatus 1 includes a suitable flame using burner 2, which may
have a top 3 of the Meker type and which has a flame-supporting
grid 4 at its outlet, a dry air inlet line 5 and a gas inlet line
6, both leading to the burner. A Y 7 connects the inner ends of the
lines 5 and 6 to a common line or conduit 8 which functions as a
mixing chamber for feeding the mixed gas and air to the burner 2.
Suitable control valves 9 and 10 are mounted in the outer ends of
the air and gas lines for accurately regulating the flow through
said lines. Between the Y 7 and control valves 9 and 10, the lines
5 and 6 have have suitable metering devices, such as orifice flow
meters 11 and 12, connected therein. As shown by the numeral 13, a
large number of small flames or flamelets emanate from the grid 4
upon burning of mixed gas and air and for many carbon-containing
fuels the carbon monoxide combustion product burns in a large flame
14 as it mixes with ambient air.
A thermocouple 15 is disposed within the carbon monoxide flame 14
or immediately above the flamelets 13 to provide an input signal to
a controller 16 which is adapted to operate the air conrol valve 9
in such manner as to maximize the electrical signal from the
thermocouple. As a result, the temperature of the burned gas
measured by the thermocouple 15 and adiabatic flame temperature of
the flamelets 13 are always at maximum. It is noted, however, that
the inlet lines may be reversed, the dry air passing through the
valve 10 and inlet line 6 and the gas passing through the valve 9
and inlet line 5. In this case, the controller 16 is adapted to
operate the gas control valve 9 in such manner as to maximize the
electrical signal from the thermocouple. The resulting burned gas
temperature measured by the thermocouple 15 and the adiabatic flame
temperature of the flamelets 13 are always at maximum. An electric
or pneumatic signal FA, proportional to the air flow rate measured
by the meter 11, is transmitted through a conductor 17 to a divider
18. Likewise, an electric or pneumatic signal FG, proportional to
the gas flow rate measured by the meter 12, is transmitted to the
divider 18 through a conductor 19. The divider is a suitable
calculating device whose output is FA divided by FG or the critical
combustion ratio between the gas and air.
Another method is illustrated by the apparatus of FIG. 2 which is
similar to the apparatus 1 and wherein additional dry air or gas,
preferably air, is added intermittently to the mixture of gas and
air. In this embodiment of the invention, a modified controller 16'
is interposed between the thermocouple and the air control valve or
the gas control valve for imparting opening and closing movement to
said valve. A common or mixing chamber line 20 is provided at the
inner ends of the air and gas inlet lines 5 and 6 and has an
additional air inlet line 21 communicating therewith between the
burner 2 and Y 7. Mounted in the line 21 is a flow control valve 22
operated by a pulse controller 23 which is adapted to open the
valve for brief periods of time at regular intervals.
As shown by the curve of FIG. 2A, the resulting total flow of air
to the burner 2 has a time-dependent behavior. The pulse controller
23 operates continually so that the total air flow through the
burner is the sum of the air flow through the air inlet valve 9 and
a continuing series of air pulses through the valve 22, the
amplitude of these air pulses being small compared with the air
flow rate through said valve 9. The effect of the air pulses is to
provide a continuing series of small perturbations on the total air
flow rate through the burner 2. In the event that the temperature
of the burned gases, as measured by the thermocouple 15, is not at
maximum, the continual small perturbations in the air flow rate
cause a continuing series of small perturbations in the temperature
of the burned gases. This effect on the burned gas temperature is
illustrated by the curves of FIG. 2B.
The first or uppermost curve of the latter depicts the conditions
when the air flow rate through the air inlet valve 9 is in excess
of that required for the burned gas temperature to be at maximum
whereby said temperature is less than its maximum value. A small
pulse of air through the valve 22 temporarily increases the air
flow rate through the burner, thereby temporarily lowering the
burned gas temperature further. This corresponds to the continuing
series of air pulses producing a continuing series of negative
temperature pulses shown in the first curve of FIG. 2B. When the
control 16' senses these negative temperature pulses by means of
the thermocouple 15, said controller operates the valve 9 so as to
reduce the total air flow to burner 2.
The second curve of FIG. 2B depicts the situation when the air flow
rate through the air inlet valve 9 is less than that required for
the burned gas temperature to be at maximum. In this event, a small
pulse of air through the valve 22 temporarily increases the air
flow rate to the burner and thereby temporarily increases the
burned gas temperature. This corresponds to the continuing series
of air pulses producing a continuing series of positive temperature
pulses. When the modified controller senses these positive
temperature pulses through the thermocouple 15, said controller
operates the valve 9 so as to increase the total air flow to the
burner.
If the burned gas temperature is at maximum, then small
perturbations in the total air flow have essentially no effect on
this temperature. As illustrated by the last or lowermost curve of
FIG. 2B, the burned gas temperature is not affected by the
continuing series of air pulses (FIG. 2A). In this case, the
controller 16' senses no temperature pulses and does not operate
the valve 9. Accordingly, it is readily apparent that the
controller operates the air inlet valve in such manner as to
maintain the burned gas temperature at maximum.
Alternatively, it may be desirable to use air pulses through the
valve 22 of sufficient magnitude to produce small negative
temperature pulses when the burned gas temperature is at maximum.
In this event, the modified controller is so designated that it
operated the valve 9 only when the thermocouple 15 senses
temperature pulses of a magnitude or sign different from those
produced when the burned gas temperature is at maximum.
Again referring to FIG. 2, the electric or pneumatic signals FA and
FG, proportional to the air and gas flow rates respectively
measured by the meters 11 and 12, are transmitted by the conductors
17 and 19 to the divider 18 which produces an output of FA divided
by FG or the critical combustion ratio between the gas and air.
A third method of measuring the critical combustion ratio, or
calorific value of the gas, is shown by the apparatus circuit FIG.
3 which includes a second designs 2' similar or identical to the
constant current source and having an identical or similar top 3'
and grid 4' so as to produce identical small flames or flamelets
13', and for many carbon-containing fuels, a carbon monoxide flame
14'. A pair of Ys 27 and 27' and a pair of common or mixing chamber
conduits 28 and 28' connect the inner end portions of the dry air
and gas inlet lines 5 and 6 to the burners 2 and 2' respectively,
whereby the air is supplied equally to both burners. A flow
restriction orifice 29 is mounted in the gas inlet line 6 between
the leg of the Y 27' leading to the common conduit 28' and burner
2' and the leg of the Y 27 leading to the common conduit 28 and
burner 2 whereby the flow rate of gas through said conduit 28 to
said burner 2 is slightly less than the gas flow rate through the
said conduit 28' to said burner 2'. Although it is not necessary
for the burners to be identical, it is essential that both burners
have the same heat loss and that equal amounts of air are fed
thereto. A pair of thermocouples 25 and 25' are disposed within the
carbon monoxide flames 14 and 14' or above the flamelets 13 and 13'
and are connected in parallel to a controller 26 which operates the
gas inlet control valve 10 in such manner as to hold the electric
signal from the thermocouples at a characteristic value. Except for
the foregoing, this embodiment of the invention is identical to the
apparatus 1 of FIG. 1.
The temperature difference between the thermocouples 25 and 25' is
equal to the temperature of the thermocouple 25' above the
flamelets 13' minus the temperature of the thermocouple 25 above
the flamelets 13. When the ratio of the flow of dry air passing
through the meter 11 to the flow rate of gas passing through the
meter 12 is equal to the critical combustion ratio, then the
adiabatic flame temperatures for the mixtures going to the two
burners will be essentially the same. Due to the operation of the
orifice 29, the dry air of air flow rate to gas flow rate in the
conduit 28' leading to burner 2' is slightly lower than the
critical combustion ratio and the ratio of dry air flow rate to gas
flow rate in the conduit 28 leading to the burner 2 is slightly
higher than the critical combustion ratio. Thus, the adiabatic
flame temperatures of the mixtures being burned in the burners 2
and 2' are each slightly less than maximum and essentially the
same. The average temperature of the burned gases in the two
burners is at substantially maximum, and any charge in the flow
rate will either lower the temperature of both flames or lower the
temperature of one flame more than enough to offset any increase in
the temperature of the other. Any difference between the
temperatures measured by the thermocouples 25 and 25' is due to a
difference in their relative position with respect to the flamelets
13 and 13' and this relative position is fixed. Thus, when the
ratio of the flow of dry air passing through the meter 11 to the
flow rate of gas passing through the meter 12 is equal to the
critical combustion ratio, the temperature difference between the
two thermocouples has a characteristic value which is independent
of the composition of said gas.
The controller 26 is set so that it does not activate the valve 10
when the difference between the thermocouples is at this
characteristic value. If the ratio of the air flow rate through the
meter 11 to the gas flow rate through the meter 12 is greater than
the critical combustion ratio, the temperature difference between
the thermocouples 25 and 25' is greater than this characteristic
value. In this event, the gaseous mixture in the burner 2 always
contains a greater excess of air than the burner 2'. The
thermocouples sense the resulting temperature difference between
the two flames 14 and 14' and the resulting signal causes the
controller 26 to operate the valve 10 so as to increase the total
gas flow through the meter 12.
When the ratio of the flow rate of air passing through the meter 11
to the flow rate of gas passing through the meter 12 is less than
the critical combustion ratio, the temperature difference between
the thermocouples 25 and 25' is less than the aforesaid
characteristic value. In this case, the gaseous mixture in burner
2' always contains a greater excess of gas than the burner 2. The
thermocouples sense the resulting temperature difference between
the flames and the resulting signal causes the controller 26 to
operate the valve 10 so as to decrease the total gas flow through
the meter 12. As described hereinbefore, the action of the
controller is such as to maintain the total air flow rate through
the meter 11 in a ratio to the total gas flow rate through the
meter 12. This ratio is essentially equal to the critical
combustion ratio which is produced by the divider 18 whose output
is the electric or pneumatic signal FA divided by the electric or
pneumatic signal FG.
A fourth method of measuring the critical combustion ratio and
thereby the calorific value of the gas is illustrated
diagrammatically in FIG. 4 wherein a dry air inlet line 30 and a
combustible gas inlet line 31 are connected by a Y 32 and a common
or mixing chamber conduit 33 to a burner 34 which may be
substantially identical to the burner 2. Pressure regulators 35 and
36 are mounted in the air and gas inlet lines 30 and 31 for
maintaining constant pressures in said lines. Inwardly of the
pressure regulator 35, the air inlet line has a control valve 37
connected therein for providing a specific flow ratio of air to
gas. The valve 37 includes a valve element 38 mounted on one end of
an elongate valve stem or shaft 39 screwthreaded into the bonnet 40
of said valve, whereby rotation of the shaft imparts opening and
closing movement to the valve element. Inwardly of the pressure
regulator 36 a flow restriction orifice 41 is disposed in the gas
inlet line. The pressure regulator 36 keeps the pressure drop
across the orifice 41 constant, thereby achieving a constant flow
rate of combustible gas in the conduit 31. Preferably, the burner
34 includes a Meker type top 42 and a grid 43 for producing a
plurality of flamelets 44 and, for many carbon-containing fuels, a
carbon monoxide flame 45.
Suitable bearings 47 and 47 rotatably support the shaft 39 and a
recording chart support or disk 48 fixed on the free end of said
shaft for rotation therewith. As best shown in FIG. 4A, a
conventional circular chart 49 is adapted to be detachably mounted
on the disk 48 for coaction with a stylus 50 which is pivotally
connected to an actuator 51. The latter is activated electrically
by an amplifier 52 which is energized by a thermocouple 53 disposed
above the flamelets 44 and/or within the carbon monoxide flame 45.
An electric motor 54 is provided for rotating the shaft in either
direction and a cycling unit 55 is interposed between the motor and
its power source for controlling the direction and extent of such
rotation. The motor 54 has its drive shaft 56 operatively connected
to the shaft 39 by coacting gears 57 and 58.
It is noted that each position of the chart 49 and it supporting
disk 48 corresponds to a specific setting of the control valve 37
and, thus, to a specific flow rate ratio of dry air to gas. The
stylus 50 indicates and records on the chart the temperature of the
burned gases for each position of said chart and this temperature
is characteristic of the specific flow rate ratio of dry air to gas
corresponding to each such position. When it is desired to measure
the critical combustion ratio of the gas, the motor 54 is actuated
by the cycling unit 55 to rotate the shaft in first one direction
and then in the other. This rotation may be a complete revolution
or a portion thereof, such as 30.degree., in each direction. The
stylus scribes twice, once for each direction of rotation. The
shaft 39 is rotated through an angle or arc sufficient for one of
its positions during such rotation to correspond to a specific flow
rate ratio of dry air to gas which equals the critical combustion
ratio.
The coaction of the rotating chart 49 and recording stylus 50
produces a graph of the burned gas temperature as a function of the
ratio of the air flow rate to the gas flow rate. The ratio which
produces the maximum temperature or critical combustion ratio can
be read directly from the chart after the shaft has traversed its
rotational path. If desired, the chart 49 may be printed so that
the circular coordinate thereon reads directly in units of
calorific value such as BTU/SCF, since caloric value is
proportional to the critical combustion ratio. Also, it is manifest
that the control valve 37 and orifice restriction 41 may be
reversed in effect with the gas being fed through line 30 and the
air through the line 31 so as to provide a specific flow rate of
gas to air rather than air to gas. Manifestly, the first three
methods (FIG. 1) are adaptable to the continuous recording of this
method.
Although the controllers 16, 26 and 16' are not available as
standard stock items, they may be constructed from stock items or
readily built by competent instrument companies from available
components. In each controller, the gas flow is controlled by a
reversible direct current motor and in controllers 16 and 26, the
power connections to the motor pass through a pair of relays which
in turn are operated by an electric current from an electronic
control circuit. The relays have different threshold current values
at which they operate. If this current is above the threshold
values of both relays, the latter are placed in such position that
the power drives the motor in a direction which closes one of the
inlet valves of the apparatus. If this current is below the
threshold values of both relays, they are moved to a different
position whereby the power drives the motor in the opposite
direction. In the event this current is between the two threshold
values, the relay positions are such that the motor does not
operate. The input to the electronic control circuit is connected
to the thermocouple wires. In the case of element 26, the
electronic control circuit is an EMF or voltage to current
converter which is a stock item.
Referring again to FIG. 5, the controller 16 of FIG. 1 comprises a
reversible direct current motor 60 having the sprocket 61 of its
drive shaft 62 meshing with a driven sprocket 63 fixed on a
rotatable shaft or stem 64 for opening and closing the dry air
inlet valve 9 or the gas inlet valve 10. The polarity of the power
connections of the motor are arranged to be reversed in order to
reverse the direction of rotation of the shaft of said motor and
thereby open and close one of the valves. A pair of commercially
available alarm switching units 65 and 66, such as Foxboro M/63R
Electronic Consotrol Alarm Units, are connected in series by an
electrical lead or conductor 69 and includes a pair of single pole
double throw switches or relays 67 and 68, respectively, having
their poles 70 and 71 connected by respective electrical conductors
or leads 72 and 73 to the power connections of the reversible motor
60. The threshold value of each alarm unit is adjustale and is
slightly higher in the unit 65 than in the unit 66. Each of the
relays 67 and 68 have contacts A and B, with the contact B of the
relay 67 and the contact A of the relay 68 connected by a positive
electrical lead or conductor 74 to a power supply 76. A negative
lead or conductor 75 electrically connects the power supply to the
contact A of the relay 67 and to the contact B of the relay 68,
whereby the motor shaft 62 is rotated in one direction when the
poles 70 and 71 are engaged with the contacts A and in the opposite
direction when said poles engage the contacts B to impart closing
and opening movement to the valve 9 or 10.
The electronic control circuit of the controller 16 is constituted
of the remaining elements of said controller and includes a double
pole double throw electronically controlled switch or relay 77
electrically connected in a conductor 78 extending between the
alarm unit 65 and a suitable constant current source 79 and
controlled at its terminal 80 by the output signals of a
differentiating circuit 81 which is connected directly to the
thermocouple 15. It is noted that the design of the differentiating
circit is subject to variation and such designa are well-known in
this art. Also, the constatcurrent asource is electrically
connected by a conductor or lead 82 to the alarm unit 68.
For imparting a series of positive current pulses to one set 83 of
dual contacts of the switch 77, a pair of electrical leads or
conductors 84 connect an oscillator 85 to said contacts. Another
electrical oscillator 86 imparts a series of negative current
pulses to a second set 87 of dual contacts through a pair of
conductors or leads 88. Since the switch 77 has its double pole 89
interposed in the conductor 78, a constant current is delivered by
the source 79 to the double pole of the electronic switch. A
combined current is supplied to the units 65 and 66, due to said
units being connected in series by the lead 69 and is composed of
the constant current and either a series of positive or negative
current pulses dependent upon whether the double pole 89 is engaged
with the contacts 83 or 87. This combined current forms the output
of the electronic control circuit and, at any given time, the
output from either one or the other of the oscillators 85 and 86 is
superimposed on a constant current from the source 79 and the
latter current is between the threshold values of the alarm
switching units.
When the EMF of the thermocouple or flame temperature is increasing
with time, the output of the differentiating circuit 81 is such
that the electronic switch is not activated or triggered and the
double pole of the latter remains in the same position. In this
event, the output of the electronic control circuit is a continual
series of either positive or negative current pulses from the
oscillator 85 or 86 so as to effect an intermittent opening or
closing movement of the inlet valve due to the intermittent
operation of the motor 60 and thereby continually increase the
flame temperature. After the flame temperature has passed through
maximum, the output signal of the differentiating circuit 81
reverses and activates or triggers the double pole 89 of the
electronic switch and the other oscillator is connected to the
electronic control circuit output so as to reverse the polarity or
sign of the current pulses which form said output. The effect is to
reverse the direction in which the inlet valve is moved whereby the
flame temperature is caused to reapproach its maximum value.
If the current or output from the electronic control circuit is
above the upper thresholds of the units 65 and 66, the poles 70 and
71 move into engagement with the respective contacts B of the
relays 67 and 68 whereby the current from the power supply 76 flows
through the conductors 74 and 72 and drives the motor shaft 62 in a
direction imparting closing movement to the inlet valve. The poles
of the relays engage the contacts A of said relays so that the
current from the power supply flows through the conductors 94 and
93 so as to reverse the motor 60 and impart opening movement to the
valve. Thus, the controller 16 functions to maintain the flame
temperature at or near its maximum value.
As shown in FIG. 7, the controller 26 of the apparatus of FIG. 3
includes a reversible direct current motor 90 having the sprocket
91 of its drive shaft 92 meshing with a driven sprocket 93 fixed on
a rotatable shaft or stem 94 for opening and closing the
combustible gas inlet valve 10. The direction of rotation of the
motor is adapted to be reversed by reversing the polarity of its
power connections. A pair of alarm switching units 95 and 96, such
as Foxboro M/63R Electronic Consotrol Alarm Units, are connected in
series by a lead or conductor 99 and include a pair of single pole
double throw relays or switches 97 and 98, respectively, having
their respective poles 100 and 101 connected by electrical
conductors or leads 102 and 103 to the power connections of the
reversible motor 90. Each of the relays 97 and 98 have a pair of
opposed contacts A and B, with the contacts A and B and B and A of
the relays 97 and 98, respectively, connected by respective
positive and negative electrical conductors or leads 104 and 105 to
a power supply 106 whereby the motor shaft 92 is rotated in one
direction when the poles 100 and 101 are engaged with the contacts
A and in the opposite direction when the contacts B are engaged by
said poles. Each of the units 95 and 96 has an adjustable threshold
current at which its relay or switch is activated and this
threshold current is slightly higher in the unit 95 than in the
unit 96. The burner temperature difference, which is sensed by the
thermocouples 25 and 25' and which corresponds to the critical
combustion ratio or maximum flame temperature, is intermediate or
between the temperature differences corresponding to the threshold
values of the alarm units.
Electrical leads or conductors 107 and 108 respectively connect the
units 95 and 96 to an electronic control circuit or converter 109,
commercially available as a Foxboro EMF-To-Current Converter and
preferably set at a current output range from 10 to 50 ma when the
voltage input ranges between 1.5 and 3.5 mv. For producing a
current which is a linear function of the thermocouple 25'
temperature minus the temperature of the thermocouple 25, the
converter 109 is connected directly to said thermocouples and this
output current is conducted to the alarm switching units through
the conductors 107 and 108. When the flow of the combustible gas is
too low to maximize the flame temperature, the difference between
the temperatures of the thermocouples is higher than the
characteristic value which does not activate the valve 10 and the
current supplied by the converter exceeds the threshold values of
both units 95 and 96. The poles of the relays 97 and 98 engage the
contacts B thereof so as to connect the motor 90 to the power
supply 106 through the conductors 102-105 and thereby rotate said
motor shaft 92 in a direction to open the valve 10 and increase the
combustible gas flow, the electrical current flowing through the
conductors 104 and 102 and said relay 97 from said power supply to
said motor.
If the latter flow is too high to maximize the flame temperature,
the difference between the temperatures of the thermocouples 25'
and 25 is lower than the aforesaid characteristic value and the
current resulting from the converter 109 is below the threshold
value of each alarm unit. The pole of each relay is engaged with
the contact A and the motor 90 is connected to the power supply 106
so that the electrical current flows through the conductors 104 and
103 as well as the relay 98 from said power source to said motor so
as to drive the motor shaft 92 in an opposite or reverse direction
and move the valve 10 toward its closed position for decreasing the
flow of combustible gas. Since the threshold value of the unit 96
is lower than that of the unit 95, its pole 101 moves toward the
contact B of the relay 98 before the pole 100 of the relay 97 moves
toward its contact B upon the increasing of the current from the
converter above said threshold values and said pole 100 moves
toward the contact A of said relay 97 prior to the movement of said
pole 101 toward the contact A of said relay 98 when said converter
current decreases below said threshold values.
The operation of the controller 26 is such that the final value of
the optimum ratio of air to combustible gas produces a temperature
difference between the thermocouples and a resulting current from
the converter 109 which activates only the unit 96 and not the unit
95, whereby the pole of the relay 98 engages its contact B and the
contact A of the relay 97 is engaged by its pole. Consequently,
both leads 102 and 103 to the motor are connected to and only to
the same terminal of the power supply by the negative conductor
105, thereby rendering said motor inoperative and maintaining the
combustible gas flow constant at its final desired value. Likewise,
the motor 90 is inoperative when the positions of the poles 100 and
101 are reversed so as to engage the contact B of the relay 97 and
the contact A of the relay 98 whereby the motor leads are connected
and only to the same terminal of the power supply 106 by the
positive conductor 104. Manifestly, the fluctuation of the current
from the converter 109 in accordance with the thermocouple
temperature difference provides the ratio of air to combustible gas
at essentially that value which maximizes the flame temperature. It
is noted that the controller 26 is of a preferred design, although
other switching circuits can be utilized to control the combustible
gas inlet valve, and that the important feature of this design is
its three different states which depend upon the voltage output of
the thermocuples 25 and 25' and which effect three modes of
operation of the valve 10, namely, stationary, opening and closing
movement. Of course, the air or combustion supporting gas inlet
valve 9 may be controlled rather than the combustible gas inlet
valve.
As shown in FIG. 6, the controller 16' of the apparatus of FIG. 2
includes a reversible direct current motor 110 having the sprocket
111 of its drive shaft 112 meshing with a driven sprocket 113 fixed
on a rotatable shaft or stem 114 for opening and closing the air
inlet valve 9 or combustible gas inlet valve 10. The direction of
rotation of the motor is adapted to be reversed by reversing the
polarity of its power connections. A double pole double throw
electronic switch or relay 115 is electrically connected to the
power input terminals of the motor through conductors or leads 116
and 117 and connected to the motor power supply 118 through
electrical leads or conductors 119 and 120. The relay is controlled
at its terminal 121 by the output signals of a pulse amplitude
measuring circuit 122 which is connected directly to the
thermocouple 15. It is noted that the design of the pulse amplitude
measuring circuit is subject to variation and such designs are
well-known in this art.
When the air flow rate is higher than required for maximum flame
temperature, the thermocouple 15 senses a continuing series of
negative temperature pulses. The input to the pulse amplitude
measuring circuit 122 is a continuing series of negative voltage
pulses produced by the thermocouple 15 in response to the
temperature pulses. The output from the pulse amplitude measuring
circuit 122 is a constant negative voltage equal to the amplitude
of the negative voltage pulses and applied to the control terminal
121 of the switch 115.
When the voltage at the terminal 121 is negative, terminals 123 of
the conductors 116 and 117 are connected to a pair of contacts 124
of the electronic switch. Current proceeds from the power supply
118 through the conductors 120 and 116 to the motor 110, causing
said motor to drive the air control valve in a closing
direction.
When the air flow rate is lower than required for maximum flame
temperature, the thermocouple 15 senses a continuing series of
positive temperature pulses. The input to the pulse amplitude
measuring circuit 122 is a continuing series of positive voltage
pulses produced by the thermocouple 15 in response to the
temperature pulses. The output from the pulse amplitude measuring
circuit 122 is a constant positive voltage equal to the amplitude
of the aforesaid positive voltage pulses and is applied to the
control terminal 121 of the switch 115.
When the voltage at the latter terminal is positive, the terminals
123 are connected to the contacts 125 of the electronic switch.
Current flows from the power supply through the conductors 120 and
117 to the reversible motor, whereby the latter drives the air
control valve in an opening direction.
Thus, the controller 16' functions to maintain the flame
temperature at or near its maximum value.
A preferred embodiment of the invention has been illustrated for
each of the four methods described heretofore. Many changes and
modifications may be made therein, however, without departing from
the spirit of the invention. In particular: any
combustion-supporting gas can be used instead of dry air; any
controllable method of metering the combustible gas and
combustion-supporting gas prior to mixing and burning can be
employed as long as the relative proportions of each are controlled
as set forth herein; any method of determining the temperature of
the burned gases may be used; whenever a numerical value of the
ratio of combustion-supporting gas to combustible gas is required,
any method of determining this numerical value may be utilized.
I have discovered that the critical combustion ratio measured in
accordance with my invention varies directly with the calorific
value of the combustible gas. The calorific value in BTU/SCF is
determined by measuring the critical combustion ratio and
multiplying this measurement by a suitable calibration constant.
This method has been applied to the measurement of the calorific
value of a number of combustible gases for the purpose of
illustrating my invention. In each case, the calorific value was
also obtained by complete chemical analysis of the combustible gas
to determine its constituents. The contribution of each constituent
to the total calorific value was determined by well-known
thermodynamic methods using published heat of combustion and heat
capacity data as set forth in "Selected Values of Physical and
Thermodynamic Properties of Hydrocarbons and Related Compounds,"
API Research Project 44, Carnegie Press, Pittsburgh, 1953.
The combustible gas mixtures were prepared by simultaneously
flowing methane and a second gas through individual rotameters to
measure their flow rates, mixing the two gases, and then passing
the mixture to the combustible gas inlet of a Meker burner. The
methane was C.P. (Chemically Pure) Grade obtained from a commercial
source. The gases added to the methane to form the combustible
mixtures were C.P. nitrogen, C.P. ethane, and Instrument Grade
propane, all obtained from a commercial source. These gases are
representative of major constituents that occur in natural gas.
Each of these commercial gases was analyzed quantitatively by gas
chromotography.
Table 1 shows the chemical composition of each combustible gas
mixture tested and the calorific value of the mixture as determined
by its composition. ##SPC1##
Natural gas has a nominal calorific value of about 1,000 BTU/SCF
and the normal variation in such value is well within the range of
the mixtures in Table 1. A standard ASTM (American Society For
Testing Materials) method for measuring calorific value, in which
air is used as a heat-absorbing fluid and upon which most
commercial instruments are based, is limited in range to about 300
BTU/SCF without recalibration. Thus, as will be evident
hereinafter, an advantage of the present invention is that a wider
range of calorific values can be measured with a single calibration
than has been heretofore possible.
The calorific value of each combustible gas mixture shown in Table
1 was measured by the first method of this invention and the
results are shown in Table 2. ##SPC2##
First, the critical combustion ratio was determined for each
combustible gas mixture using the apparatus illustrated in FIG. 1;
however, gas flow rates were varied manually rather than
automatically in the experiments. The flow of dry air which
maximized the flame temperature was determined by measuring the
temperature with the thermocouple 15 at three different air flow
rates close to the maximum conditions. Then, these data points were
fitted to a parabolic curve representing the variation of
temperature with dry air flow. Although this technique was
convenient in the laboratory, in a preferred embodiment of the
invention the dry air flow would be continuously and automatically
varied such as to maximize the signal from the thermocouple and,
thus, the temperature. Gas and air flow rates were measured with
rotameters, which had been calibrated using a wet test meter, and
the critical combustion ratio was calculated from these flow rates
using the following equation: ##SPC3##
Although in these experiments the dry air flow rate was varied to
achieve maximum temperature, substantially the same results are
obtained by varying the flow rate of the combustible gas mixture or
both flow rates. It is only the ratio of the two flow rates that is
significant.
Second, the calorific value was calculated from the measured
critical combustion ratio using the following equation:
(Calorific Value) = (Calibration Factor) X ("Critical Combustion
Ratio")
This equation gives the calorific value as measured by the method
of my invention employing the apparatus illustrated in FIG. 1. In
practice, the calibration factor is determined by applying the
method to combustible gas mixtures of known calorific value.
Calibrating the apparatus in this manner and utilizing the above
equation tends to correct for constant errors made in metering the
gases and, thus, further improve the precision of the method. To
obtain the results of Table 2, a single calibration factor was used
and was chosen by the least squares method so as to maximize the
agreement between the calorific values measured by my method and
those values determined from the known composition of the
combustible gas mixture. The agreement is within 0.5 percent over
the entire range of calorific values and the results show that the
calorific value is indeed proportional to the critical combustion
ratio.
It has also been discovered that my methods for measuring critical
combustion ratio have two unexpected advantages. First, the
measurement is independent of the exact position of the
thermocouples shown in FIGS. 1-4. As long as the thermocouple is
close to and above the flamelets and/or within the cone or flame
formed by the burning of the carbon monoxide combustion product,
the measured value of critical combustion ratio is not affected by
the thermocouple position even though the thermocouple temperature
varies with its position whereby the construction of the depicted
apparatuses is greatly simplified. Second, the measured value of
the critical combustion ratio is independent of temperature over a
wide range, and this is a very significant advantage.
Consequently, my methods of measuring calorific value and the
illustrated apparatuses can be used in a wide range of ambient
temperatures without taking special precautions to control the
initial temperature of the combustible gas and ambient air. This is
one of the prime disadvantages of prior known methods of and means
for measuring calorific value. In prior known methods and means, it
usually is necessary to operate the calorimetric apparatus in a
temperature controlled environment, held to within
1.degree.-2.degree.F., in order to achieve a precision of 0.5
percent. In some cases, a special building is required for this
purpose. No such precautions need be taken with the methods of my
invention.
That the measured calorific value using my methods is independent
of initial gas temperature and thermocouple position is shown by
the data in Table 3. ##SPC4##
The apparatuses of FIGS. 1-3, which measure the critical combustion
ratio, may also be employed in automatic control systems. These
apparatuses have application in any system in which the mixing
ratio of various gases is controlled either to achieve a constant
calorific value or to maximize the combustion temperature in a
furnace.
For example, assume it is desired to control the addition of
propane to natural gas in order to keep the calorific value of the
resulting combustible gas constant. The controllers in the
apparatuses of FIGS. 1-3 can be caused to directly control propane
addition instead of controlling the gas. In this event, the flow
rate of a sample of the combustible gas and the flow rate of dry
air to the apparatuses would be held constant. The controllers
would vary the percent propane in the combustible gas rather than
the dry air or combustible gas flow rate and said controllers would
operate so as to keep the calorific value of the combustible gas
constant. This constant calorific value corresponds to a critical
combustion ratio which is equal to the constant ratio of dry air to
combustible gas entering the apparatuses.
If it is desired to control the air or gas flow to a furnace in
order to maximize combustion temperature, the apparatuses of FIGS.
1-3 could be utilized. The controllers would function not only as
shown and described, but would also directly control the
appropriate gas flow rate to the furnace.
In summary, methods have bpen discovered for measuring the
calorific value of combustible gases which require relatively
simpler apparatuses than prior methods. Errors due to heat losses
have been completely eliminated since the only thermal quantity
measured is a relative temperature. It is not necessary to measure
the absolute value of any temperature, but only the conditions for
which the temperature of burned gases produced in a flame is a
maximum and these conditions are not affected by heat losses from
the flame. Other than calibration against known mixtures, no
corrections are required to achieve precision comparable to that
provided by prior, more complex methods. My methods are insensitive
to ambient temperature which may vary between -40.degree. F. and
130.degree. F. which has a large effect on the results of prior
methods. In addition, methods have been discovered for
automatically controlling the mixing of various gases in order to
hold the calorific value constant or maximize combustion
temperature.
* * * * *