CA1167771A - Gas compressor unit - Google Patents
Gas compressor unitInfo
- Publication number
- CA1167771A CA1167771A CA000382191A CA382191A CA1167771A CA 1167771 A CA1167771 A CA 1167771A CA 000382191 A CA000382191 A CA 000382191A CA 382191 A CA382191 A CA 382191A CA 1167771 A CA1167771 A CA 1167771A
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- Canada
- Prior art keywords
- gas
- intercooling
- compressor unit
- approximately
- gas compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A GAS COMPRESSOR UNIT
Abstract of the Disclosure In the embodiment depicted, the unit comprises three, serially-coupled, multi-stage axial-flow gas compressors, having intercooling and demisting assem-blies interposed therebetween. The compressor shafts are commonly coupled, in line, for powered drive from a single prime mover. The intercooling and demisting assemblies are of exceptionally short axial length, define gas-entry areas of exceptionally large dimen-sion, and cause a pressure drop thereacross (i.e., across the intercoolers and demisters) not in excess of one p.s.i. Each cooling assembly is only about one-third the total length of the compressor stages which deliver compressed gas thereinto, is fifteen to twenty-five times larger in area than a last-stage gas exit annulus, and constrains gas flow therethrough to unidirectional, axial conduct.
Abstract of the Disclosure In the embodiment depicted, the unit comprises three, serially-coupled, multi-stage axial-flow gas compressors, having intercooling and demisting assem-blies interposed therebetween. The compressor shafts are commonly coupled, in line, for powered drive from a single prime mover. The intercooling and demisting assemblies are of exceptionally short axial length, define gas-entry areas of exceptionally large dimen-sion, and cause a pressure drop thereacross (i.e., across the intercoolers and demisters) not in excess of one p.s.i. Each cooling assembly is only about one-third the total length of the compressor stages which deliver compressed gas thereinto, is fifteen to twenty-five times larger in area than a last-stage gas exit annulus, and constrains gas flow therethrough to unidirectional, axial conduct.
Description
I 1 ~ 7 r7 ~
This invention pertains to gas compressor units, and in particular to multi-stage, axial-flow gas com-pressors having gas cooling and demisting means in-corporated therewith.
Prior art gas compressor units of the aforesaid type to which the invention pertains typically have gas cooling means which cause the product gas to:
(1) follow serpentine flow paths, (2) be piped out to a separate cooler or heat exchanger, or (3) be conducted through considerably axially-extended coolers or heat exchangers. Exemplary of the first type are U.S. patents Nos. 2,925,954, issued to W. Spillmann et al., for a "Compressor Group with Intercooler", on 23 February 1960, and 912,882, issued to O. P. Oraker, for an "Air Compressor", on 16 February 1909. U.S. patent No. 2,478,504, issued to R. Ruegg, for a "Plant for the Production and Heating of Compressed Air7', on 9 August 1949, ls typical of the aforesaid second type. U.S. patent No. 2,073,833, 20 issued on 16 March 1937, to G. DeBothezat, for an "Air Conditioner", discloses an axially-extended cooler, of the third, aforesaid, prior art type, having a length equal to, or greater than the total length of the compressor stages which deliver gas thereto. This is true of the Spillmann et al. dis-closure also.
, . .
~ ~ ~7~'7 t All the aforesaid types, due to the configurations, dimensions, and fluid-flow conductances thereof, mani-fest a significant pressure drop through the coolers or heat exchangers.
Now, patently, the optimurn gas compressor unit should conduct all gas flow therethrough only substan-tially axially, to prevent undue pressure drop. To this end, then, it is necessary to have considerably axially-extended coolers and intercoolers, and conduct the gas product therethrough unidirectionally. Un-fortunately, however, such coolers and intercoolers of considerable length subject the product gas to pressure losses; these occur due to the relatively long residence time for the gas flow to negotiate the length of the coolers, and the turbulances, eddies, and friction arising therefrom.
Well, external piping of the product gas to separate coolers will not prevent the pressure drop, and coaxially linear, unldirectional coolers, having
This invention pertains to gas compressor units, and in particular to multi-stage, axial-flow gas com-pressors having gas cooling and demisting means in-corporated therewith.
Prior art gas compressor units of the aforesaid type to which the invention pertains typically have gas cooling means which cause the product gas to:
(1) follow serpentine flow paths, (2) be piped out to a separate cooler or heat exchanger, or (3) be conducted through considerably axially-extended coolers or heat exchangers. Exemplary of the first type are U.S. patents Nos. 2,925,954, issued to W. Spillmann et al., for a "Compressor Group with Intercooler", on 23 February 1960, and 912,882, issued to O. P. Oraker, for an "Air Compressor", on 16 February 1909. U.S. patent No. 2,478,504, issued to R. Ruegg, for a "Plant for the Production and Heating of Compressed Air7', on 9 August 1949, ls typical of the aforesaid second type. U.S. patent No. 2,073,833, 20 issued on 16 March 1937, to G. DeBothezat, for an "Air Conditioner", discloses an axially-extended cooler, of the third, aforesaid, prior art type, having a length equal to, or greater than the total length of the compressor stages which deliver gas thereto. This is true of the Spillmann et al. dis-closure also.
, . .
~ ~ ~7~'7 t All the aforesaid types, due to the configurations, dimensions, and fluid-flow conductances thereof, mani-fest a significant pressure drop through the coolers or heat exchangers.
Now, patently, the optimurn gas compressor unit should conduct all gas flow therethrough only substan-tially axially, to prevent undue pressure drop. To this end, then, it is necessary to have considerably axially-extended coolers and intercoolers, and conduct the gas product therethrough unidirectionally. Un-fortunately, however, such coolers and intercoolers of considerable length subject the product gas to pressure losses; these occur due to the relatively long residence time for the gas flow to negotiate the length of the coolers, and the turbulances, eddies, and friction arising therefrom.
Well, external piping of the product gas to separate coolers will not prevent the pressure drop, and coaxially linear, unldirectional coolers, having
2~ appreciable length to insure adequate residence time and a resulting efficient cooling appears to be the only option available. The undue pressure drop pro-ceeding therefrom is not avoidable. Thus is the state of the art. However, I have discovered that there does obtain another, heretofore not recognized option. I have conceived a gas compressor unit which ~ ~ ~7~
will efficiently cool the product gas and will not cause a pressure drop across the intercoolers and demisters in excess of approximately one p.s.i. It is my object to disclose such a gas compressor unit.
It is particularly an object of this invention to set forth a gas compressor unit, for compressing gas to a pressure taken from a range of pressures of from approximately seventy-five to approximately one hundred and fifty p.s.i~, comprising a plurality of serially-arranged, multi-staged, axially flow gas compressors; gas intercooling and demisting means; and means coupling said intercooling and demisting means interpositionally between said compressors of said plurality thereof; said coupling means and said intercooling and demisting means comprising structure having such configuration, dimensions and fluid-conductance as to prevent a pressure drop9 across said intercooling and demisting means, of - compressed gas conducted therethrough, of more than approximately one p.s.i.
According to the above objects, from a broad aspect, the present invention provides a gas compressor unit for compressing gas to a pressure taken from a range of pressures from approximately seventy-five to one hundred and fifty p.s.i. The compressor unit comprises a plurality of serially-arranged-multi-staged, axial-flow gas compressors. Gas intercooling and demisting means of annular configuration are also _3_ i ~6~7~
p.rovidedO Means is provided for coupling the inter-cooling and demisting means interpositionally between the compressors. The coupling means and the inter-cooling and demisting means comprises structure having such configuration, dimensions and fluid-conductance as to prevent a pressure drop, across the intercooling and demisting means 9 of compressed gas conducted therethrough, of more than approximately one p.s.i.
The.unit has a gas inlet capacity of at least one hundred thousand cubic feet a minute. The intercooling and demisting mean.s has an outside diameter of at least a given dimension, and an axial length of not more than twenty-five percent of the given dimension.
Further objects of this invention, as well as the novel features thereof 9 will become more apparent 9 by reference to the following description, taken in conjunction with the accompanying Figures, in which:
Figure 1 is a side elevational view of an embodiment of the invention:
Figures 2A and 2B comprise an axial, cross-sectional view, in elevation, of the Figure 1 embodiment of the invention, the same being enlarged over the scale of Figure 1: and .~
, I ~ 677 7 1 Figure 3 is a fragmentary, cross-sectional view of one of the intercoolers, taken along section 3-3 of Figure 1, the same being considerably enlarged over the scale of Figure 1.
As shown in the figures, an em~odiment of the novel gas compressor unit 10, comprises first, second, and third multi-stage, axial-flow compressors 12, ].4, and 16, respectively, serially arranged, and joined through a common drive shaft assembly 13. Intercoolers 20 and 22 and demisters 24 and 26 are lnterpositioned between the compressors. The unit 10 is supported by stanchions 28, 30, 32 and 34, and has a first stage wheel 36 having a diameter which, in this embodiment, is of approximately sixty-four inches in dimension.
Intercoolers 20 and 22 and demisters 24 and 26 are almost two hundred and sixty per cent larger than the diameter of the first stage wheel 36, as they have diameters of approximately one hundred and sixty-four inches.
Compressor 12 has an exit annulus 40 which encom-passes approximately seven square feet of area, and the intercooler 20 has an entry annulus 42 which encompasses approximately one hundred and forty-three square feet of area. Hence, the latter area is approximately twenty times greater than the former area. The exit annulus 40' of compressor 14 occupies an area of approximately four and a half square feet. Accordingly, the entry annulus 42' of intercooler 22 is approximately thirty-two times larger than annulus 40'.
t :~67~'71 Notwithstanding the considerable diameters of inter-coolers 20 and 22, they occupy not more than one-third the total axial length of the stages of the respective compressors 12 and 14. That is, while the stages' total axial length of compressor 12 is approximately one hun-dred and four inches, the intercooler 20 is only approxi mately twenty-six inches in axial length. The demisters 24 and 26 are only approximately nine inches in axial length; i.e., they have a length of about five and a half per cent their diameter. The intercoolers have a length of about sixteen per cent of their diameter.
Such short length intercoolers 20 and 22, and de-misters 24 and 26, insure that the residence time or confinement of gas therewithin will be exceedingly brief.
Thereby, the incidence of turbulence, eddies and friction is markedly reduced and the pressure drop, across the inter-coolers and demisters, does not exceed approximately one p.s.i.
While it may seem that such short-length inter-coolers 20 and 22 cannot have adequate capacity for gas cooling, in fact they are novelly designed for such.
Each has a gross capacity of almost one hundred and forty-three cubic feet. Within this total volume are a multiplicity of finned heat exchanger tubes 44. In this embodiment 10, approximately sixty-eight hundred and fifty tubes 44 are employed. They accommodate a product gas capacity of slightly more than one hundred and fifty cubic feet, while the coolant-water channels, 1 3 6 ~7'7 ~
which the tubes 44 traverse, accommodate a capacity of slightly more than one hundred and forty cubic feet.
The intercoolers 20 and 22 are identical in struc-ture, so the fragmentary depiction in figure 3 is ex-emplar~ of both. The tubes 44 are held at either endsin side plates 46 and 48, and a peripheral wall 50 sealingly circumscribes the plates. ~he wall 50 is replaceably bolted, through flanges 52 and 54, to an intercooler inlet diffuser 56 and an outlet plenum 58.
In the lower portion of the wall 50 are formed water inlet and discharge ports (not shown) which admit coolant water to a first section 60 of the intercooler and discharge it from a second section 62. A pump 63 supplies the water, providing a flow through the inter-cooler at a velocity of slightly more than five feet of flow a second between the tubes 44. A barrier plate 64, which subdivides the intercooler into the aEoresaid sections, has a termination 66 at the top to allow the sections to communicate thereat.
Gas-product flow through the intercoolers 20 and 22 is linear, unidirectional, and axial. The generous expanse of the entry annuli 42 and 42' accommodates the Eull discharge of the exit annuli 40 and 40', subdividing the flow into the aforesaid approximately sixty-eight hundred and fifty tubes 44 for efficient cooling in a short axial travel. The approximately sixty-eight ~ 1 ~;7~
hundred and fifty discrete streams of product-gas are uniformly addressed to the large-diameter demisters 24 and 26, thereafter. Due to this wide dispersion of the product-gas into such a multiplicity of separate streams, no areas of the demisters are more burdened than others thereof. Hence, the demisters 24 and 26, although ex-periencing rapid through-flows of the gas -- due to the extremely short axial extent of the demisters -- knock out approximately ninety-eight per cent of the moisture content (of 13 microns and larger).
The unit 10 is designed for facile maintenance, in that the whole outer shell therof is horizontally split.
. .
The upper half of the inlet throat 37, the upper half of the diffuser 5~, and the therebetween upper half of the shell of compressor 12 can be unbolted together from the corresponding lower halves, and from the ad-jacent upper half of intercooler 20, and lifted orf in one piece. This is shown, in phantom, in Figure 1.
Also, the intercooler 20 (or 22) can be unbolted from the adjacent diffuser 56 and plenum 58 and lifted out for servicing and/or replacementO The throat 37, or upper and lower halves of diffuser 56, or halves of plenum 58, or halves of the compressor shell may be removed and replaced at will.
The most si~nificant teaching herein, however, is the structuring of an axial-flow gas compressor unit with gas coollng and demisting means which suffers not more than a one p.s.i. pressure drop across the inter-coolers and demisters, and in which the cooling and demisting means add insignificant axial length. Pur-suant to my disclosure herein, t:he latter have pre-scribed areas and volumes efficiently to process theproduct gas without diminishing the optimum performance of the unit 10, and the invention comprehends a speci-fied flow of coolant water through the sections of the intercoolers. A]l said features of my conception and calculation define an exemplary embodiment of the in-vention which teaches the art a new option in multi-stage, axial-flow gas compressor design.
The embodiment 10 shown comprises a unit configured to deliver approximately three hundred thousand inlet c.f.m. compressed to a product gas pressure taken from a range of pressures or from approximately seventy-five to one hundred and fifty p.s.i. However, the novel teachings and structures can be used to define a units delivering one hundred thousand to approximately six hundred thousand c.f.m. within the aforesaid said pressure range.
To apply the inventive teachings herein to define units having capacities of from fifty or one hundred thousand to approximately six hundred thousand c.f.m.
it is necessary to dimension the intercooler and de-mister diameters accordingly. While doing this, however, they must be maintained at their limited axial lengths ` -8-1 :~ 67~
of twenty-six and nine inches, respectively. Otherwise, if the intercoolers and demis~ers are given greater axial lengths, the units constructed therewith will manifest a greater than one p.s.i. pressure drop acro.ss the intercoolers and demisters.
Diameter sizing, then, of t:he intercoolers and de-misters, while holding them to t:heir aforesaid lengths, is fairly critical. It is a teaching of my invention to use formulas of my conception to define acceptable diameters. ~roadly, to determine the diameters for the intercoolers and demisters for a unit having an inlet capacity of from less than one hundred thousand cubic feet a minute to approximately six hundred thousand cubic feet a minute, I set forth ,the following foxmula:
the diameter shall be 1.15~inch, approximately, times each 1000 c.f.m. of inlet capacity, to an inlet capacity of approximately 100,000 c.f.m., plus 0.25-inch, approxi-mately, times each increment of 1000 c.f.m., of inlet capacity, which is in excess of 100,000 c.f.m. More definitively, the diameter shal] be l.lS-inch, approxi-mately, times each 1000 c.f.m. of inlet capacity, to an inlet capacity of approximately 100,000 c.f.m., plus not less than 0.21-inch and not more than 0.28-inch, times each increment of 1000 c.f.m., of inlet capacity, which is in excess of 100,000 c.f.m.
Such formulae determinations of intercooler and de-mister diameters will prescribe intercoolers having _9_ t 1 67~
diameters which are from four and a half to nine times greater than their twenty-six-inch axial lengths, and demisters having diameters which are from twelve and a half to twenty-six times greater than their nine-inch axial lengths. However, as unconventional as this teaching may be, it provides gas compressor units of serially-arranged, multi-staged, axial flow compressors having a pressure drop, across the intercoolers and demisters, of not more than approximately one p.s.i., and accommodating gas flow into such intercoolers and demisters at a velocity of not more than approximately twenty-two feet per second.
Typically, multi-staged, axial-flow, gas compressor units, having intercooling ~and demisting) means have the intercoolers set apart from the axis of the units, and the compressed ga.s product must be conducted thereto and therefrom. This prior art practice was cited earlier in this specification. Now, it is further a typically required practice to mount the intercoolers on mezzanine-type supports, or in below-flow-level bays. Accordingly, the installation structures and requirements for such units are both complex and expensive. My novel gas com-pressor unit, however, comprises a plurality of com-pressors and intercoolers all serially-arranged in a single-axis alignment, on stanchions. Therefore, my I :167~'7~
inventive unit can be, and is intended to be, floor-mounted, fully, from end-to-end. Too, as can be appre~
ciated from the foregoing, the in-line coolers and de-misters do not contribute, signi.ficantly, to the over-all lenyth of the unit. Each interstage set of inter-cooler and demister (excluding entry and exit plenums or shrouds) add less than three feet to the unit length.
This remains so, whether the unit is configured to de-liver one hundred thousand or six hundred thousand cubic feet a minute. For greater capacities, within the afore-said range, it is only necessary to increase the inter-cooler and demister diameter according to my disclosed formulae.
While I have described my invention in connection with a specific embodiment thereof, it is to be clearly understood that this is done only by way of example and not as a limitation to the scope of my invention as set forth in the objects thereof and in the appended claims.
will efficiently cool the product gas and will not cause a pressure drop across the intercoolers and demisters in excess of approximately one p.s.i. It is my object to disclose such a gas compressor unit.
It is particularly an object of this invention to set forth a gas compressor unit, for compressing gas to a pressure taken from a range of pressures of from approximately seventy-five to approximately one hundred and fifty p.s.i~, comprising a plurality of serially-arranged, multi-staged, axially flow gas compressors; gas intercooling and demisting means; and means coupling said intercooling and demisting means interpositionally between said compressors of said plurality thereof; said coupling means and said intercooling and demisting means comprising structure having such configuration, dimensions and fluid-conductance as to prevent a pressure drop9 across said intercooling and demisting means, of - compressed gas conducted therethrough, of more than approximately one p.s.i.
According to the above objects, from a broad aspect, the present invention provides a gas compressor unit for compressing gas to a pressure taken from a range of pressures from approximately seventy-five to one hundred and fifty p.s.i. The compressor unit comprises a plurality of serially-arranged-multi-staged, axial-flow gas compressors. Gas intercooling and demisting means of annular configuration are also _3_ i ~6~7~
p.rovidedO Means is provided for coupling the inter-cooling and demisting means interpositionally between the compressors. The coupling means and the inter-cooling and demisting means comprises structure having such configuration, dimensions and fluid-conductance as to prevent a pressure drop, across the intercooling and demisting means 9 of compressed gas conducted therethrough, of more than approximately one p.s.i.
The.unit has a gas inlet capacity of at least one hundred thousand cubic feet a minute. The intercooling and demisting mean.s has an outside diameter of at least a given dimension, and an axial length of not more than twenty-five percent of the given dimension.
Further objects of this invention, as well as the novel features thereof 9 will become more apparent 9 by reference to the following description, taken in conjunction with the accompanying Figures, in which:
Figure 1 is a side elevational view of an embodiment of the invention:
Figures 2A and 2B comprise an axial, cross-sectional view, in elevation, of the Figure 1 embodiment of the invention, the same being enlarged over the scale of Figure 1: and .~
, I ~ 677 7 1 Figure 3 is a fragmentary, cross-sectional view of one of the intercoolers, taken along section 3-3 of Figure 1, the same being considerably enlarged over the scale of Figure 1.
As shown in the figures, an em~odiment of the novel gas compressor unit 10, comprises first, second, and third multi-stage, axial-flow compressors 12, ].4, and 16, respectively, serially arranged, and joined through a common drive shaft assembly 13. Intercoolers 20 and 22 and demisters 24 and 26 are lnterpositioned between the compressors. The unit 10 is supported by stanchions 28, 30, 32 and 34, and has a first stage wheel 36 having a diameter which, in this embodiment, is of approximately sixty-four inches in dimension.
Intercoolers 20 and 22 and demisters 24 and 26 are almost two hundred and sixty per cent larger than the diameter of the first stage wheel 36, as they have diameters of approximately one hundred and sixty-four inches.
Compressor 12 has an exit annulus 40 which encom-passes approximately seven square feet of area, and the intercooler 20 has an entry annulus 42 which encompasses approximately one hundred and forty-three square feet of area. Hence, the latter area is approximately twenty times greater than the former area. The exit annulus 40' of compressor 14 occupies an area of approximately four and a half square feet. Accordingly, the entry annulus 42' of intercooler 22 is approximately thirty-two times larger than annulus 40'.
t :~67~'71 Notwithstanding the considerable diameters of inter-coolers 20 and 22, they occupy not more than one-third the total axial length of the stages of the respective compressors 12 and 14. That is, while the stages' total axial length of compressor 12 is approximately one hun-dred and four inches, the intercooler 20 is only approxi mately twenty-six inches in axial length. The demisters 24 and 26 are only approximately nine inches in axial length; i.e., they have a length of about five and a half per cent their diameter. The intercoolers have a length of about sixteen per cent of their diameter.
Such short length intercoolers 20 and 22, and de-misters 24 and 26, insure that the residence time or confinement of gas therewithin will be exceedingly brief.
Thereby, the incidence of turbulence, eddies and friction is markedly reduced and the pressure drop, across the inter-coolers and demisters, does not exceed approximately one p.s.i.
While it may seem that such short-length inter-coolers 20 and 22 cannot have adequate capacity for gas cooling, in fact they are novelly designed for such.
Each has a gross capacity of almost one hundred and forty-three cubic feet. Within this total volume are a multiplicity of finned heat exchanger tubes 44. In this embodiment 10, approximately sixty-eight hundred and fifty tubes 44 are employed. They accommodate a product gas capacity of slightly more than one hundred and fifty cubic feet, while the coolant-water channels, 1 3 6 ~7'7 ~
which the tubes 44 traverse, accommodate a capacity of slightly more than one hundred and forty cubic feet.
The intercoolers 20 and 22 are identical in struc-ture, so the fragmentary depiction in figure 3 is ex-emplar~ of both. The tubes 44 are held at either endsin side plates 46 and 48, and a peripheral wall 50 sealingly circumscribes the plates. ~he wall 50 is replaceably bolted, through flanges 52 and 54, to an intercooler inlet diffuser 56 and an outlet plenum 58.
In the lower portion of the wall 50 are formed water inlet and discharge ports (not shown) which admit coolant water to a first section 60 of the intercooler and discharge it from a second section 62. A pump 63 supplies the water, providing a flow through the inter-cooler at a velocity of slightly more than five feet of flow a second between the tubes 44. A barrier plate 64, which subdivides the intercooler into the aEoresaid sections, has a termination 66 at the top to allow the sections to communicate thereat.
Gas-product flow through the intercoolers 20 and 22 is linear, unidirectional, and axial. The generous expanse of the entry annuli 42 and 42' accommodates the Eull discharge of the exit annuli 40 and 40', subdividing the flow into the aforesaid approximately sixty-eight hundred and fifty tubes 44 for efficient cooling in a short axial travel. The approximately sixty-eight ~ 1 ~;7~
hundred and fifty discrete streams of product-gas are uniformly addressed to the large-diameter demisters 24 and 26, thereafter. Due to this wide dispersion of the product-gas into such a multiplicity of separate streams, no areas of the demisters are more burdened than others thereof. Hence, the demisters 24 and 26, although ex-periencing rapid through-flows of the gas -- due to the extremely short axial extent of the demisters -- knock out approximately ninety-eight per cent of the moisture content (of 13 microns and larger).
The unit 10 is designed for facile maintenance, in that the whole outer shell therof is horizontally split.
. .
The upper half of the inlet throat 37, the upper half of the diffuser 5~, and the therebetween upper half of the shell of compressor 12 can be unbolted together from the corresponding lower halves, and from the ad-jacent upper half of intercooler 20, and lifted orf in one piece. This is shown, in phantom, in Figure 1.
Also, the intercooler 20 (or 22) can be unbolted from the adjacent diffuser 56 and plenum 58 and lifted out for servicing and/or replacementO The throat 37, or upper and lower halves of diffuser 56, or halves of plenum 58, or halves of the compressor shell may be removed and replaced at will.
The most si~nificant teaching herein, however, is the structuring of an axial-flow gas compressor unit with gas coollng and demisting means which suffers not more than a one p.s.i. pressure drop across the inter-coolers and demisters, and in which the cooling and demisting means add insignificant axial length. Pur-suant to my disclosure herein, t:he latter have pre-scribed areas and volumes efficiently to process theproduct gas without diminishing the optimum performance of the unit 10, and the invention comprehends a speci-fied flow of coolant water through the sections of the intercoolers. A]l said features of my conception and calculation define an exemplary embodiment of the in-vention which teaches the art a new option in multi-stage, axial-flow gas compressor design.
The embodiment 10 shown comprises a unit configured to deliver approximately three hundred thousand inlet c.f.m. compressed to a product gas pressure taken from a range of pressures or from approximately seventy-five to one hundred and fifty p.s.i. However, the novel teachings and structures can be used to define a units delivering one hundred thousand to approximately six hundred thousand c.f.m. within the aforesaid said pressure range.
To apply the inventive teachings herein to define units having capacities of from fifty or one hundred thousand to approximately six hundred thousand c.f.m.
it is necessary to dimension the intercooler and de-mister diameters accordingly. While doing this, however, they must be maintained at their limited axial lengths ` -8-1 :~ 67~
of twenty-six and nine inches, respectively. Otherwise, if the intercoolers and demis~ers are given greater axial lengths, the units constructed therewith will manifest a greater than one p.s.i. pressure drop acro.ss the intercoolers and demisters.
Diameter sizing, then, of t:he intercoolers and de-misters, while holding them to t:heir aforesaid lengths, is fairly critical. It is a teaching of my invention to use formulas of my conception to define acceptable diameters. ~roadly, to determine the diameters for the intercoolers and demisters for a unit having an inlet capacity of from less than one hundred thousand cubic feet a minute to approximately six hundred thousand cubic feet a minute, I set forth ,the following foxmula:
the diameter shall be 1.15~inch, approximately, times each 1000 c.f.m. of inlet capacity, to an inlet capacity of approximately 100,000 c.f.m., plus 0.25-inch, approxi-mately, times each increment of 1000 c.f.m., of inlet capacity, which is in excess of 100,000 c.f.m. More definitively, the diameter shal] be l.lS-inch, approxi-mately, times each 1000 c.f.m. of inlet capacity, to an inlet capacity of approximately 100,000 c.f.m., plus not less than 0.21-inch and not more than 0.28-inch, times each increment of 1000 c.f.m., of inlet capacity, which is in excess of 100,000 c.f.m.
Such formulae determinations of intercooler and de-mister diameters will prescribe intercoolers having _9_ t 1 67~
diameters which are from four and a half to nine times greater than their twenty-six-inch axial lengths, and demisters having diameters which are from twelve and a half to twenty-six times greater than their nine-inch axial lengths. However, as unconventional as this teaching may be, it provides gas compressor units of serially-arranged, multi-staged, axial flow compressors having a pressure drop, across the intercoolers and demisters, of not more than approximately one p.s.i., and accommodating gas flow into such intercoolers and demisters at a velocity of not more than approximately twenty-two feet per second.
Typically, multi-staged, axial-flow, gas compressor units, having intercooling ~and demisting) means have the intercoolers set apart from the axis of the units, and the compressed ga.s product must be conducted thereto and therefrom. This prior art practice was cited earlier in this specification. Now, it is further a typically required practice to mount the intercoolers on mezzanine-type supports, or in below-flow-level bays. Accordingly, the installation structures and requirements for such units are both complex and expensive. My novel gas com-pressor unit, however, comprises a plurality of com-pressors and intercoolers all serially-arranged in a single-axis alignment, on stanchions. Therefore, my I :167~'7~
inventive unit can be, and is intended to be, floor-mounted, fully, from end-to-end. Too, as can be appre~
ciated from the foregoing, the in-line coolers and de-misters do not contribute, signi.ficantly, to the over-all lenyth of the unit. Each interstage set of inter-cooler and demister (excluding entry and exit plenums or shrouds) add less than three feet to the unit length.
This remains so, whether the unit is configured to de-liver one hundred thousand or six hundred thousand cubic feet a minute. For greater capacities, within the afore-said range, it is only necessary to increase the inter-cooler and demister diameter according to my disclosed formulae.
While I have described my invention in connection with a specific embodiment thereof, it is to be clearly understood that this is done only by way of example and not as a limitation to the scope of my invention as set forth in the objects thereof and in the appended claims.
Claims (12)
1. A gas compressor unit, for compressing gas to a pressure taken from a range of pressures from approxi-mately seventy-five to one hundred and fifty p.s.i., comprising:
a plurality of serially-arranged-multi-staged, axial-flow gas compressors;
gas intercooling and demisting means of annular configuration; and means coupling said intercooling and demisting means interpositionally between said compressors of said plurality thereof;
said coupling means and said intercooling and demisting means comprising structure having such confi-guration, dimensions and fluid-conductance as to prevent a pressure drop, across said intercooling and demisting means, of compressed gas conducted there-through, of more than approximately one p.s.i., said unit has a gas inlet capacity of at least one hundred thousand cubic feet a minute; and said intercooling and demisting means having an outside diameter of at least a given dimension, and an axial length of not more than twenty-five percent of said given dimension.
a plurality of serially-arranged-multi-staged, axial-flow gas compressors;
gas intercooling and demisting means of annular configuration; and means coupling said intercooling and demisting means interpositionally between said compressors of said plurality thereof;
said coupling means and said intercooling and demisting means comprising structure having such confi-guration, dimensions and fluid-conductance as to prevent a pressure drop, across said intercooling and demisting means, of compressed gas conducted there-through, of more than approximately one p.s.i., said unit has a gas inlet capacity of at least one hundred thousand cubic feet a minute; and said intercooling and demisting means having an outside diameter of at least a given dimension, and an axial length of not more than twenty-five percent of said given dimension.
2. A gas compressor unit, according to claim 1, wherein;
said configuration, dimensions and fluid-conductance of said structure comprises means accommodating gas flow into said intercooling and demisting means at a velocity of not more than approximately twenty-two feet per second.
said configuration, dimensions and fluid-conductance of said structure comprises means accommodating gas flow into said intercooling and demisting means at a velocity of not more than approximately twenty-two feet per second.
3. A gas compressor unit, according to claim 1, wherein:
said unit has a gas inlet capacity of greater than one hundred thousand cubic feet a minute;
and said intercooling and demisting means have an outside diameter greater than said given dimension, which greater diameter is defined by the formula:
greater diameter = 0.25 inch (approx.) times each increment of 1000 c.f.m.
(of said greater capacity) which is in excess of 100,000 c.f.m., plus said given dimension.
said unit has a gas inlet capacity of greater than one hundred thousand cubic feet a minute;
and said intercooling and demisting means have an outside diameter greater than said given dimension, which greater diameter is defined by the formula:
greater diameter = 0.25 inch (approx.) times each increment of 1000 c.f.m.
(of said greater capacity) which is in excess of 100,000 c.f.m., plus said given dimension.
4. A gas compressor unit, according to claim 1, wherein:
said unit has a gas inlet capacity of greater than one hundred thousand cubic feet a minute; and said intercooling and demisting means have an outside diameter greater than said given dimension, which greater diameter is defined by the formula:
greater diameter = not less than 0.21 inches and not more than 0.28 inch, times each increment of 1000 c.f.m.
(of said greater capacity) which is in excess of 100,000 c.f.m., plus said given dimension.
said unit has a gas inlet capacity of greater than one hundred thousand cubic feet a minute; and said intercooling and demisting means have an outside diameter greater than said given dimension, which greater diameter is defined by the formula:
greater diameter = not less than 0.21 inches and not more than 0.28 inch, times each increment of 1000 c.f.m.
(of said greater capacity) which is in excess of 100,000 c.f.m., plus said given dimension.
5. A gas compressor unit, according to claim 1, wherein:
said given dimension is approximately one hundred and fifteen inches.
said given dimension is approximately one hundred and fifteen inches.
6. A gas compressor unit, according to claim 1, wherein:
said intercooling and demisting means comprises a plurality of separate intercoolers and demisters;
each of said intercoolers has an axial length of not more than approximately twenty-six inches; and each of said demisters has an axial length of not more than approximately nine inches.
said intercooling and demisting means comprises a plurality of separate intercoolers and demisters;
each of said intercoolers has an axial length of not more than approximately twenty-six inches; and each of said demisters has an axial length of not more than approximately nine inches.
7. A gas compressor unit, according to claim 1, wherein:
the first, upstream compressor of said serially-arranged plurality thereof has a first stage wheel diameter of a prescribed dimension; and said given dimension of said intercooling and demisting means is a multiple of said prescribed dimension.
the first, upstream compressor of said serially-arranged plurality thereof has a first stage wheel diameter of a prescribed dimension; and said given dimension of said intercooling and demisting means is a multiple of said prescribed dimension.
8. A gas compressor unit, according to claim 7, wherein:
said given dimension is approximately two hundred and sixty percent larger than said first stage wheel diameter.
said given dimension is approximately two hundred and sixty percent larger than said first stage wheel diameter.
9. A gas compressor unit, according to claim 7, wherein:
said intercooling and demisting means comprises a plurality of separate intercoolers and demisters;
a plurality of said compressors have a given axial length; and each demister has an axial length which is not more than approximately one-tenth said given axial length.
said intercooling and demisting means comprises a plurality of separate intercoolers and demisters;
a plurality of said compressors have a given axial length; and each demister has an axial length which is not more than approximately one-tenth said given axial length.
10. A gas compressor unit; according to claim 9, wherein:
each intercooler has an axial length which is not more than approximately one-fourth said given axial length.
each intercooler has an axial length which is not more than approximately one-fourth said given axial length.
11. A gas compressor unit, according to claim 9, wherein:
at least one compressor of said plurality thereof has a last stage wheel exit annulus of a given area; and each intercooler has an entry annulus with an area which is not less than approximately twenty times greater than said given area.
at least one compressor of said plurality thereof has a last stage wheel exit annulus of a given area; and each intercooler has an entry annulus with an area which is not less than approximately twenty times greater than said given area.
12. A gas compressor unit, according to claim 9, wherein:
at least one compressor of said plurality thereof has a last stage wheel exit annulus of a given area; and each intercooler has an entry annulus with an area which is not less than ten times greater than said given area.
at least one compressor of said plurality thereof has a last stage wheel exit annulus of a given area; and each intercooler has an entry annulus with an area which is not less than ten times greater than said given area.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US22205981A | 1981-01-02 | 1981-01-02 | |
| US222,059 | 1981-01-02 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1167771A true CA1167771A (en) | 1984-05-22 |
Family
ID=22830626
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000382191A Expired CA1167771A (en) | 1981-01-02 | 1981-07-21 | Gas compressor unit |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS57114000A (en) |
| CA (1) | CA1167771A (en) |
| CH (1) | CH655364A5 (en) |
| DE (1) | DE3131720A1 (en) |
| GB (1) | GB2090631B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5722241A (en) * | 1996-02-26 | 1998-03-03 | Westinghouse Electric Corporation | Integrally intercooled axial compressor and its application to power plants |
| US8376718B2 (en) | 2009-06-24 | 2013-02-19 | Praxair Technology, Inc. | Multistage compressor installation |
| US20140000841A1 (en) * | 2012-06-29 | 2014-01-02 | Robert L. Baker | Compressed gas cooling apparatus |
-
1981
- 1981-07-21 CA CA000382191A patent/CA1167771A/en not_active Expired
- 1981-07-24 GB GB8122942A patent/GB2090631B/en not_active Expired
- 1981-08-11 DE DE19813131720 patent/DE3131720A1/en not_active Withdrawn
- 1981-09-25 JP JP15085881A patent/JPS57114000A/en active Pending
- 1981-11-12 CH CH727981A patent/CH655364A5/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| DE3131720A1 (en) | 1982-08-05 |
| GB2090631A (en) | 1982-07-14 |
| CH655364A5 (en) | 1986-04-15 |
| GB2090631B (en) | 1984-10-31 |
| JPS57114000A (en) | 1982-07-15 |
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| Date | Code | Title | Description |
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| MKEX | Expiry |