CA1168549A - Inlet throttling valve of gas fuel compressor - Google Patents
Inlet throttling valve of gas fuel compressorInfo
- Publication number
- CA1168549A CA1168549A CA000403911A CA403911A CA1168549A CA 1168549 A CA1168549 A CA 1168549A CA 000403911 A CA000403911 A CA 000403911A CA 403911 A CA403911 A CA 403911A CA 1168549 A CA1168549 A CA 1168549A
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- Prior art keywords
- gas fuel
- gas
- pressure
- supply system
- operable
- Prior art date
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Abstract
Inventor: Tadeusz Budzich Title Inlet Throttling Valve Of Gas Fuel Compressor ABSTRACT OF THE DISCLOSURE
A control valve automatically regulating the flow of gas fuel to the inlet of a gas fuel compressor to maintain the pressure in a gas fuel line, leading to an appliance, above a minimum predetermined level.
A control valve automatically regulating the flow of gas fuel to the inlet of a gas fuel compressor to maintain the pressure in a gas fuel line, leading to an appliance, above a minimum predetermined level.
Description
1~68549 BAC~GROUND OF THE INV~TION
Thls lnvention relates generally to a gas ~uel di3trl-bution system, supplying with gas fuel a number o~ appllcances and a gas ~uel compressor, storing the gas fuel under pr2s3ure ln a suitable pressure vessel.
In more partlcular aspects thls lnvention relate~ to a control ~alve, whlch regulate~ the flow o~ gas fuel to a gas ~uel compressor, to malntain an uninterrupted flow of gas fuel to other appliances, at a certain mlnlmum pressure level.
Gas fuel, for example methane, is supplied to indivldual houses from a main pipeline through a network of indivldual pipe-lines, whlch are of comparatively small diameter and the length of which may vary widely. The gas pressure in the maln pipelines not only varies conslderably from one location to another, but is also dependent on the rate~ at which the gas ls belng used. The gas line, supplylng with gas fuel an individual house, must have su~ficlent flow capacity, wlth main line at minimum pressure, to carry the maximum flow réquired by all gas applicances in t~
house at a certain mln~mum pressure level.
Methane gasg when compresse~ to say 2000 PSI and stored ln a pressure vessel, provides a very desirable clean burning fuel for use in a conventional passenger car, wlth only small modlflcations required to the existlng carburation system. 3ual carburation systems are available, which permit use of methane and once the supply of methane is exhausted, permit switching the englne operation to conventlonal gasollne fuel. With the present shortages and prlce of gasoline and with an abundant supply of comparatively lnexpensive natural gas, a passenger car, equipped with a dual carburation system and gas storage tanks, becomes very attractive, especlally for purposes o~ short range commuting.
In such service, with storage tanks charged with methane, the drlver can co~mute to work)within say,thirty miles radius using methane ruel only, after each trlp the methane storage tanks 1168~
being recharged. Since a very large number of individual houses are connected to a natural gas supply, using it for heatiny and cooking purposes, by installing an individual gas compressing facility in individual houses, recharging of the methane storage tanks of a passenger car during the night becomes possible, using the domestic natural gas supply. Under these conditions each domestic natural gas supply becomes automatically an individual recharging station at which the passenger car can be recharged with methane gas and used for commuting. In such a system, with low main line pressure and all of the house gas appliances working, the additional flow requirements of the gas compressor might excessively lower the gas fuel pressure.
SUMMARY OF THE INVENTION
It is therefore a principal object of this invention to provide, in a domestic natural gas distribution system inclu-ding gas appliances and a gas compressor, a control valve automatically regulating the flow of gas fuel to the gas compressor inlet, to maintain the pressure of the gas distri-bution system above a minimum predetermined level.
According to one aspect of the invention, there is provided a gas fuel supply system comprising means supplying gas fuel, appliance means operable above a certain predetermined minimum fuel pressure level connected to said means supplying gas fuel, a gas fuel compressing means connected to said means supplying gas fuel, and gas fuel flow control means interposed between said means supplying gas fuel and said gas fuel com-pressing means, said fuel flow control means having means operable to progressively vary the quantity of gas fuel flow between said means supplying gas fuel and said gas fuel com-pressing means to maintain the pressure at said appliance means above said certain predetermined minimum pressure level ~ -3-1~6~549 According to another aspect of the invention, there is provided a gas fuel supply system comprising means supply-lng gas fuel, appliance means connected to said means supply-ing gas fuel and operable above a certain predetermined minimum gas fuel pressure level, a gas fuel compressing means connected to said means supplying gas fuel, and control means operable to vary the mass of said gas fuel being com-pressed per unit time by said gas fuel compressing means to maintain pressure in said means supplying gas fuel above said predetermined minimum pressure level.
. -3a-11~8549 Addltlonal ob~ects of this in~entlon will become appar-ent when referring to the pre~erred embod~ment o~ the lnventlon as shown ln the single accompanylng drawing and descrlbed in the . rollowing detailed descrlptlon.
DESCRIPTION OF THE DRA',~ING
The sln~le drawing shows a ~ectlonal elevation of the control valve o~ this invent1on with ~chematlcally shown gas fuel lines and appllances of a domestic gas ~uel distrlbution system and wlth the gas ~uel compressor shown dlagrammatically.
lt~8549 DESCRIPTION OF THE PR~FERRED E~BODIMENT
A control valve, generally designated as 10, ls inter-posed between a domestlc ~uel distrlbutlon system, ~enerall~
deslgnated as 11 and a gas fuel compressor, generally designated as 12, supplylng w~th compressed gas through line 13 a ga~ s,orage vessel 14. The domestic gas ~uel distributlon system 11 is con-nected by supply llne 15 wlth a main gas line 16, which supplies gas ~uel under pressure. The dlstrlbution system 11 consists o~
a furnace 17, a water heater 18 and ~ cooking range 19, all provided with sultable pressure regulators 20, 21 and 22, supplied wlth gas ~uel under pressure through a gas meter 23 and line 24~
The control valve 10 is connected to s~pply line 15 by llne 25, gas meter 26 and llne 2i. The control valve 10 comprlses a houslng 28, provlded with a diaphragm 29, secured ln position by a cover 30. Cylindrical end of the cover 30, suitably de~ormed over a flange 31 Or the housing 28, malntains in sealing engage-ment enlarged rim of the diaphragm 29. A sleeve 32, a spring guide ~3 and a stop 34 are ce,ntrally secured to the diaphragm 29 by a rivet 35. A control spring 36 is lnterposed between the spring guide 33 and internal surface of the cover 30. The sleeve valve 32 ls slidably guided in sealing engagement in bore 37, provided ln the housing 38. The sleeve valve 32 has throttling ports 38 cooperating with annular space 39, which is connected by port 40 and line 41 wlth inlet check val~e 42 and 43 of the compressor 12.
The sleeve valve 32 protrudes with one end lnto space 44, while the other end wlth internal passage 4S communicates with an inlet chamber 46 r which ls connected through port 47, line 27, gas meter 26 and line 25 with supply llne 15~ Port 47 is also con-nected by passage 48 with space 44. Space 4g, contained between the dlaphragm 29 and the co~er 30, is cornected through port 50 3o wlth atmospherlc pressure.
Pistons 51 and 52 of the compressor 10, slidabiy guided i~ cylinders 53 and 54, define ~lrst stage compression chambers :: ~168549 55 and 56~ ~econd stage compresslon chamber~ 57 and 5~ and oil chambers 59 and 60. The first stage compresslon chambers 55 ~nd 56 are connected through eheck valves 62 and 63 with an inter-cooler chamber 61 and through suction check val~es 42 and 43 wlth port 40 of the control valve 10. The second stage compress~
chambers 57 and 58 are connected through check ~alves 64 and 65 with the lntercooler chamber 61 and through discharge chec~
valves 66 and 67 and lines 68 and 13 and a disconnect coupling 69 to the storage ~essel 14. Oil chambers 59 and 60 are sequent-lally connected by a directlon control valve 70, oper~ted by an actuator 71 ln response to control signal 72, either to z_fluid power pump 73 or a reservolr 74, which mlght be provided wlth a negative precsure chamber 75.
Wlth the appllances 17, 18 and 19 worklng, the resist-ance to ~10N of gas fuel in supply line 15 results in a pressure drop. The-slze of supply llne 15 is so selected that wlth minimum pressure in line 16 and maximum pressure drop in supply line 15, the pressure in llne 24, upstream of pressure regulators 20, 21 and 22, will be malntained above a certain minimum pressure level at which the appliances 17, 18 and 19 can work at rated output.
At gas pressures lower than this minimum level the heat output o~ the appliances wlll reduce, until a pressure level is reached, at which the appliances will cease to function. '~ith all o~ the appliances working, the additional pressure drop in supply line 15, due to the iniet flow requirement of gas compressor 12, mlght bring the gas pressure, upstream of pressure regulators 20, 21 and 22, below the critical level. Thls condltion ls prevented ~y action of the control valve 10. The sleeve ~alve 32 is shown in an equilibrlum posltion, in which the throttling actlon of 3o throttllng ports 38, in respect to edge of annular space 39, will regulate at port 40 the inlet pressure of the gas compressor 12, to reduce the lnlet flow requ:Lrement of the gas compressor 12 to a level, at which the gas pressure in line 24 will be automat-ically maintalned above a certain minimum pressure level, as 1 lB8549 required by the appliances 17, 18 and 19. ~his control action ls accompllshed in the following way. The pressure ln supply line 15, conducted by port 47 to the lnlet chamber 46, reacts on the cross-sectlonal area of the sleeve ~alve 32 tending to move it upward.
This force i9 supplemented by the gas pressure conducted by passage 48 to space 44 reacting on the net effectlve area of the diaphragm 29. Therefore the diaphragm 29 on one side is subJected, on its total ef~ective area, to the gas pressure, generating a ~orce which is opposed only by the biasing ~orce of the control spring 36, since the other side of the dlaphragm 29 is vented to atmospheric pressure. I~lth drop in pressure in supply line 15 the sleeve valve 32 moves downwards, gradually restricting with throttling ports 38 the gas flow to the gas compressor 12, until a position is reached, at which tbe communication bet~een supply line 15 and the gas compressor 12 is completely cut orf. 7~ith gas pressure ln supply line 15 reaching a speci~ic hlgher level the diaphragm 29 wlll move ~11 the way up, li~ting the sleeve valve 32 and engaging the cover 30 wlth the stop 34. In this posltion minimum resistance to gas flow is provided through the control valve 10. Within the controlllng range of the control valve 10 each specific pressure level will generate a specif~c force on the diaphra~m 29, corresponding to a specific de~lection of the control spring 36 and therefore also corresponding to a speci~ic position of sleeve ~alve 32. Therefore, by regulating gas flow lnto the gas compressor 12, the control valve 10 will automaticall~ , maintain the gas pressure in supply line 15 above a m nimum preselected level, equivalent tO the preload of the control sprin~
36.
The gas compressor 12 is of a double acting t~pe one of the pistons being subJected to the discharge stroke while the other is sub~ected to the suctlon stroke~ lhen the direction of the plston ls being reversed small pressure fluctuations will ta~e place at the compres~or inlet. Those small fluctuations can be ~ ~168549 easily attenuated by the use of a ~uitable decoupllng device, posltioned for example between the compressor lZ and the control valve 10. For better synchronl2ation the plstons of ~he ga3 l compreSsor may be mechanically connected, while 5till being oper-¦ ated by the power deriv d from the system pump. The motion o~ the compressor plstons is controlled by the four way valve 70 through the actuator 71, which may respond to the position of compressor pl tons, gas or pump pre~sure, or to any type o~ timing devlce.
I In a well known manner the gas ~uel in the first stage compresslon 1~ ¦ chamber, at compressor inlet pressure, is compressed and trans-¦ ~erred through the check valve 62 to the intercooler chamber 61,~rom which lt supplies at intermediate gas pressure, through the check valve 65, the ~econd stage compression chamber 58. The ¦ compressed gas ~rom the second stage Compression chamber 57 is 1 d~rectly trans~erred through the discharge check valve 66, line 13 and the coupling 69 to the storage vessel 14. Once the piston 51 will reach the end o~ it~ discharge stroke, the piston 52, then at the end of its sUction stroke, connected to the source of l hydraulic pressUre by the ~our way valve 70, will start moving 1 upwards durlng its dlscharge stroke. The plstons of the gas compressor 12 during suction stroke wlll move downward sub~ected to negative presYure developed in the reservoir 74 by negative pressure chamber 75 and also sub~ected to the intermediate pres-I sure developed in the intercooler chamber 61. By varying the l compressor inlet pressure, delivered to the ~lrst stage compressiorchambers 55 and 56, the quantlty o~ gas being compressed and there ore the quantity of the gas delivered to the compressor from supply llne 15 can be e~fectively regulated, since the weight of l the compressed gas ~s dlrectly proportlonal to the absolute gas 3o l pressure at the compressor inlet check valves 42 and 43. Reduction in inlet pressure wlll reduce compressor delivery, but will not ad~ersely a~fect the basic compreSsion cycle of the compressor~
¦For example~ with the ~urnaCe 17 and the water heater 18 workln~
I
I
~ ~16~5~9 and the cooklng range 19 disconnected, the gas compres30r 12 ,rill~
¦ automatically supply, depending on the pressure in line lo, at least the maximum gas flow, equlvalent to the maximum gas ~low l requlred by the cooklng range 19. Slnce the furnace 17 is a~slc-¦ all~ an on/of~ device, worklng lntermittently, ~ith furnace 17not working the gas compressor 12 will automatically compress a quantity of gas equivalent to the rate of maximum flow capacit~
of the furnace 17 and the cooklng range 18. Therefore, the contro~
l valve lO wlll automatlcally regulate the pressure at the lnlet of -10 ¦ the compressor 12 to permit the maxlmum rate of gas compresslon, whlch wlll still not lower the pressure in the supply line 15 below a certaln minimum predetermined pressure level, as dictated by the mlnimum gas pressure level required for the rated oper-l ation of the appllances 17, 18 and l9.
l Although the preferred embodiment of this inventlon has been shown and described ln detall it is recognized that the lnvention ls not limlted to the preclse form and structure shown and various modlflcations and rearrangements as wlll occur to l those skllled ln the art upon ~ull comprehension of this inventio~
¦ may be resorted to without departing ~rom the scope of the 'A~A~ - n ~- ~e~ G ~
Thls lnvention relates generally to a gas ~uel di3trl-bution system, supplying with gas fuel a number o~ appllcances and a gas ~uel compressor, storing the gas fuel under pr2s3ure ln a suitable pressure vessel.
In more partlcular aspects thls lnvention relate~ to a control ~alve, whlch regulate~ the flow o~ gas fuel to a gas ~uel compressor, to malntain an uninterrupted flow of gas fuel to other appliances, at a certain mlnlmum pressure level.
Gas fuel, for example methane, is supplied to indivldual houses from a main pipeline through a network of indivldual pipe-lines, whlch are of comparatively small diameter and the length of which may vary widely. The gas pressure in the maln pipelines not only varies conslderably from one location to another, but is also dependent on the rate~ at which the gas ls belng used. The gas line, supplylng with gas fuel an individual house, must have su~ficlent flow capacity, wlth main line at minimum pressure, to carry the maximum flow réquired by all gas applicances in t~
house at a certain mln~mum pressure level.
Methane gasg when compresse~ to say 2000 PSI and stored ln a pressure vessel, provides a very desirable clean burning fuel for use in a conventional passenger car, wlth only small modlflcations required to the existlng carburation system. 3ual carburation systems are available, which permit use of methane and once the supply of methane is exhausted, permit switching the englne operation to conventlonal gasollne fuel. With the present shortages and prlce of gasoline and with an abundant supply of comparatively lnexpensive natural gas, a passenger car, equipped with a dual carburation system and gas storage tanks, becomes very attractive, especlally for purposes o~ short range commuting.
In such service, with storage tanks charged with methane, the drlver can co~mute to work)within say,thirty miles radius using methane ruel only, after each trlp the methane storage tanks 1168~
being recharged. Since a very large number of individual houses are connected to a natural gas supply, using it for heatiny and cooking purposes, by installing an individual gas compressing facility in individual houses, recharging of the methane storage tanks of a passenger car during the night becomes possible, using the domestic natural gas supply. Under these conditions each domestic natural gas supply becomes automatically an individual recharging station at which the passenger car can be recharged with methane gas and used for commuting. In such a system, with low main line pressure and all of the house gas appliances working, the additional flow requirements of the gas compressor might excessively lower the gas fuel pressure.
SUMMARY OF THE INVENTION
It is therefore a principal object of this invention to provide, in a domestic natural gas distribution system inclu-ding gas appliances and a gas compressor, a control valve automatically regulating the flow of gas fuel to the gas compressor inlet, to maintain the pressure of the gas distri-bution system above a minimum predetermined level.
According to one aspect of the invention, there is provided a gas fuel supply system comprising means supplying gas fuel, appliance means operable above a certain predetermined minimum fuel pressure level connected to said means supplying gas fuel, a gas fuel compressing means connected to said means supplying gas fuel, and gas fuel flow control means interposed between said means supplying gas fuel and said gas fuel com-pressing means, said fuel flow control means having means operable to progressively vary the quantity of gas fuel flow between said means supplying gas fuel and said gas fuel com-pressing means to maintain the pressure at said appliance means above said certain predetermined minimum pressure level ~ -3-1~6~549 According to another aspect of the invention, there is provided a gas fuel supply system comprising means supply-lng gas fuel, appliance means connected to said means supply-ing gas fuel and operable above a certain predetermined minimum gas fuel pressure level, a gas fuel compressing means connected to said means supplying gas fuel, and control means operable to vary the mass of said gas fuel being com-pressed per unit time by said gas fuel compressing means to maintain pressure in said means supplying gas fuel above said predetermined minimum pressure level.
. -3a-11~8549 Addltlonal ob~ects of this in~entlon will become appar-ent when referring to the pre~erred embod~ment o~ the lnventlon as shown ln the single accompanylng drawing and descrlbed in the . rollowing detailed descrlptlon.
DESCRIPTION OF THE DRA',~ING
The sln~le drawing shows a ~ectlonal elevation of the control valve o~ this invent1on with ~chematlcally shown gas fuel lines and appllances of a domestic gas ~uel distrlbution system and wlth the gas ~uel compressor shown dlagrammatically.
lt~8549 DESCRIPTION OF THE PR~FERRED E~BODIMENT
A control valve, generally designated as 10, ls inter-posed between a domestlc ~uel distrlbutlon system, ~enerall~
deslgnated as 11 and a gas fuel compressor, generally designated as 12, supplylng w~th compressed gas through line 13 a ga~ s,orage vessel 14. The domestic gas ~uel distributlon system 11 is con-nected by supply llne 15 wlth a main gas line 16, which supplies gas ~uel under pressure. The dlstrlbution system 11 consists o~
a furnace 17, a water heater 18 and ~ cooking range 19, all provided with sultable pressure regulators 20, 21 and 22, supplied wlth gas ~uel under pressure through a gas meter 23 and line 24~
The control valve 10 is connected to s~pply line 15 by llne 25, gas meter 26 and llne 2i. The control valve 10 comprlses a houslng 28, provlded with a diaphragm 29, secured ln position by a cover 30. Cylindrical end of the cover 30, suitably de~ormed over a flange 31 Or the housing 28, malntains in sealing engage-ment enlarged rim of the diaphragm 29. A sleeve 32, a spring guide ~3 and a stop 34 are ce,ntrally secured to the diaphragm 29 by a rivet 35. A control spring 36 is lnterposed between the spring guide 33 and internal surface of the cover 30. The sleeve valve 32 ls slidably guided in sealing engagement in bore 37, provided ln the housing 38. The sleeve valve 32 has throttling ports 38 cooperating with annular space 39, which is connected by port 40 and line 41 wlth inlet check val~e 42 and 43 of the compressor 12.
The sleeve valve 32 protrudes with one end lnto space 44, while the other end wlth internal passage 4S communicates with an inlet chamber 46 r which ls connected through port 47, line 27, gas meter 26 and line 25 with supply llne 15~ Port 47 is also con-nected by passage 48 with space 44. Space 4g, contained between the dlaphragm 29 and the co~er 30, is cornected through port 50 3o wlth atmospherlc pressure.
Pistons 51 and 52 of the compressor 10, slidabiy guided i~ cylinders 53 and 54, define ~lrst stage compression chambers :: ~168549 55 and 56~ ~econd stage compresslon chamber~ 57 and 5~ and oil chambers 59 and 60. The first stage compresslon chambers 55 ~nd 56 are connected through eheck valves 62 and 63 with an inter-cooler chamber 61 and through suction check val~es 42 and 43 wlth port 40 of the control valve 10. The second stage compress~
chambers 57 and 58 are connected through check ~alves 64 and 65 with the lntercooler chamber 61 and through discharge chec~
valves 66 and 67 and lines 68 and 13 and a disconnect coupling 69 to the storage ~essel 14. Oil chambers 59 and 60 are sequent-lally connected by a directlon control valve 70, oper~ted by an actuator 71 ln response to control signal 72, either to z_fluid power pump 73 or a reservolr 74, which mlght be provided wlth a negative precsure chamber 75.
Wlth the appllances 17, 18 and 19 worklng, the resist-ance to ~10N of gas fuel in supply line 15 results in a pressure drop. The-slze of supply llne 15 is so selected that wlth minimum pressure in line 16 and maximum pressure drop in supply line 15, the pressure in llne 24, upstream of pressure regulators 20, 21 and 22, will be malntained above a certain minimum pressure level at which the appliances 17, 18 and 19 can work at rated output.
At gas pressures lower than this minimum level the heat output o~ the appliances wlll reduce, until a pressure level is reached, at which the appliances will cease to function. '~ith all o~ the appliances working, the additional pressure drop in supply line 15, due to the iniet flow requirement of gas compressor 12, mlght bring the gas pressure, upstream of pressure regulators 20, 21 and 22, below the critical level. Thls condltion ls prevented ~y action of the control valve 10. The sleeve ~alve 32 is shown in an equilibrlum posltion, in which the throttling actlon of 3o throttllng ports 38, in respect to edge of annular space 39, will regulate at port 40 the inlet pressure of the gas compressor 12, to reduce the lnlet flow requ:Lrement of the gas compressor 12 to a level, at which the gas pressure in line 24 will be automat-ically maintalned above a certain minimum pressure level, as 1 lB8549 required by the appliances 17, 18 and 19. ~his control action ls accompllshed in the following way. The pressure ln supply line 15, conducted by port 47 to the lnlet chamber 46, reacts on the cross-sectlonal area of the sleeve ~alve 32 tending to move it upward.
This force i9 supplemented by the gas pressure conducted by passage 48 to space 44 reacting on the net effectlve area of the diaphragm 29. Therefore the diaphragm 29 on one side is subJected, on its total ef~ective area, to the gas pressure, generating a ~orce which is opposed only by the biasing ~orce of the control spring 36, since the other side of the dlaphragm 29 is vented to atmospheric pressure. I~lth drop in pressure in supply line 15 the sleeve valve 32 moves downwards, gradually restricting with throttling ports 38 the gas flow to the gas compressor 12, until a position is reached, at which tbe communication bet~een supply line 15 and the gas compressor 12 is completely cut orf. 7~ith gas pressure ln supply line 15 reaching a speci~ic hlgher level the diaphragm 29 wlll move ~11 the way up, li~ting the sleeve valve 32 and engaging the cover 30 wlth the stop 34. In this posltion minimum resistance to gas flow is provided through the control valve 10. Within the controlllng range of the control valve 10 each specific pressure level will generate a specif~c force on the diaphra~m 29, corresponding to a specific de~lection of the control spring 36 and therefore also corresponding to a speci~ic position of sleeve ~alve 32. Therefore, by regulating gas flow lnto the gas compressor 12, the control valve 10 will automaticall~ , maintain the gas pressure in supply line 15 above a m nimum preselected level, equivalent tO the preload of the control sprin~
36.
The gas compressor 12 is of a double acting t~pe one of the pistons being subJected to the discharge stroke while the other is sub~ected to the suctlon stroke~ lhen the direction of the plston ls being reversed small pressure fluctuations will ta~e place at the compres~or inlet. Those small fluctuations can be ~ ~168549 easily attenuated by the use of a ~uitable decoupllng device, posltioned for example between the compressor lZ and the control valve 10. For better synchronl2ation the plstons of ~he ga3 l compreSsor may be mechanically connected, while 5till being oper-¦ ated by the power deriv d from the system pump. The motion o~ the compressor plstons is controlled by the four way valve 70 through the actuator 71, which may respond to the position of compressor pl tons, gas or pump pre~sure, or to any type o~ timing devlce.
I In a well known manner the gas ~uel in the first stage compresslon 1~ ¦ chamber, at compressor inlet pressure, is compressed and trans-¦ ~erred through the check valve 62 to the intercooler chamber 61,~rom which lt supplies at intermediate gas pressure, through the check valve 65, the ~econd stage compression chamber 58. The ¦ compressed gas ~rom the second stage Compression chamber 57 is 1 d~rectly trans~erred through the discharge check valve 66, line 13 and the coupling 69 to the storage vessel 14. Once the piston 51 will reach the end o~ it~ discharge stroke, the piston 52, then at the end of its sUction stroke, connected to the source of l hydraulic pressUre by the ~our way valve 70, will start moving 1 upwards durlng its dlscharge stroke. The plstons of the gas compressor 12 during suction stroke wlll move downward sub~ected to negative presYure developed in the reservoir 74 by negative pressure chamber 75 and also sub~ected to the intermediate pres-I sure developed in the intercooler chamber 61. By varying the l compressor inlet pressure, delivered to the ~lrst stage compressiorchambers 55 and 56, the quantlty o~ gas being compressed and there ore the quantity of the gas delivered to the compressor from supply llne 15 can be e~fectively regulated, since the weight of l the compressed gas ~s dlrectly proportlonal to the absolute gas 3o l pressure at the compressor inlet check valves 42 and 43. Reduction in inlet pressure wlll reduce compressor delivery, but will not ad~ersely a~fect the basic compreSsion cycle of the compressor~
¦For example~ with the ~urnaCe 17 and the water heater 18 workln~
I
I
~ ~16~5~9 and the cooklng range 19 disconnected, the gas compres30r 12 ,rill~
¦ automatically supply, depending on the pressure in line lo, at least the maximum gas flow, equlvalent to the maximum gas ~low l requlred by the cooklng range 19. Slnce the furnace 17 is a~slc-¦ all~ an on/of~ device, worklng lntermittently, ~ith furnace 17not working the gas compressor 12 will automatically compress a quantity of gas equivalent to the rate of maximum flow capacit~
of the furnace 17 and the cooklng range 18. Therefore, the contro~
l valve lO wlll automatlcally regulate the pressure at the lnlet of -10 ¦ the compressor 12 to permit the maxlmum rate of gas compresslon, whlch wlll still not lower the pressure in the supply line 15 below a certaln minimum predetermined pressure level, as dictated by the mlnimum gas pressure level required for the rated oper-l ation of the appllances 17, 18 and l9.
l Although the preferred embodiment of this inventlon has been shown and described ln detall it is recognized that the lnvention ls not limlted to the preclse form and structure shown and various modlflcations and rearrangements as wlll occur to l those skllled ln the art upon ~ull comprehension of this inventio~
¦ may be resorted to without departing ~rom the scope of the 'A~A~ - n ~- ~e~ G ~
Claims (9)
1. A gas fuel supply system comprising means supplying gas fuel, appliance means operable above a certain predetermined minimum fuel pressure level connected to said means supplying gas fuel, a gas fuel compressing means connected to said means supplying gas fuel, and gas fuel flow control means interposed between said means supplying gas fuel and said gas fuel compress-ing means, said fuel flow control means having means operable to progressively vary the quantity of gas fuel flow between said means supplying gas fuel and said gas fuel compressing means to maintain the pressure at said appliance means above said certain predetermined minimum pressure level.
2. A gas fuel supply system as set forth in Claim 1 wherein said fuel flow control means includes gas fuel throttling means having means responsive to gas pressure in said means supplying gas fuel.
3. A gas fuel supply system as set forth in Claim 2 wherein said gas fuel throttling means includes force generating means operable to generate force proportional to pressure in said means supplying gas fuel, and spring biasing means opposing said force generating means.
4. A gas fuel supply system as set forth in Claim 1 wherein said gas fuel flow control means includes means operable to vary gas inlet pressure of said gas fuel compressing means.
5. A gas fuel supply system as set forth in Claim 1 wherein said gas fuel flow control means includes shut-off means operable to shut off the gas flow between said means supplying gas fuel and said gas fuel compressing means when the pressure in said means supplying gas fuel drops to said certain predetermined minimum level.
6. A gas fuel supply system comprising means supplying gas fuel, appliance means connected to said means supplying gas fuel and operable above a certain predetermined minimum gas fuel pressure level, a gas fuel compressing means connected to said means supplylng gas fuel, and control means operable to vary the mass of said gas fuel being compressed per unit time by said gas fuel compressing means to maintain pressure in said means supply-ing gas fuel above said predetermined minimum pressure level.
7. A gas fuel supply system as set forth in Claim 6 wherein said control means has means operable to vary gas inlet pressure of said gas fuel compressing means.
8. A gas fuel supply system as set forth in Claim 6 wherein said control means has gas fuel pressure throttling means interposed between said means supplying gas fuel and said gas fuel compressing means.
9. A gas fuel supply system as set forth in Claim 6 wherein said control means includes shut-off means operable to shut off the gas flow between said means supplying gas fuel and said gas fuel compressing means when the pressure in said means supplying gas fuel drop to said certain predetermined minimum level.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000403911A CA1168549A (en) | 1982-05-27 | 1982-05-27 | Inlet throttling valve of gas fuel compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000403911A CA1168549A (en) | 1982-05-27 | 1982-05-27 | Inlet throttling valve of gas fuel compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1168549A true CA1168549A (en) | 1984-06-05 |
Family
ID=4122882
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000403911A Expired CA1168549A (en) | 1982-05-27 | 1982-05-27 | Inlet throttling valve of gas fuel compressor |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1168549A (en) |
-
1982
- 1982-05-27 CA CA000403911A patent/CA1168549A/en not_active Expired
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