US3355097A - Fluid machine - Google Patents

Fluid machine Download PDF

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Publication number
US3355097A
US3355097A US515559A US51555965A US3355097A US 3355097 A US3355097 A US 3355097A US 515559 A US515559 A US 515559A US 51555965 A US51555965 A US 51555965A US 3355097 A US3355097 A US 3355097A
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United States
Prior art keywords
outlet
casing
inlet
pump unit
air
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 - Lifetime
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US515559A
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English (en)
Inventor
Hornschuch Hanns
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ingersoll Rand Co
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Ingersoll Rand Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ingersoll Rand Co filed Critical Ingersoll Rand Co
Priority to US515559A priority Critical patent/US3355097A/en
Priority to GB55704/66A priority patent/GB1149960A/en
Priority to SE17299/66A priority patent/SE319263B/xx
Priority to DE1966J0032562 priority patent/DE1628299B2/de
Priority to FR88445A priority patent/FR1505948A/fr
Application granted granted Critical
Publication of US3355097A publication Critical patent/US3355097A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/163—Combinations of two or more pumps ; Producing two or more separate gas flows driven by a common gearing arrangement
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/913—Inlet and outlet with concentric portions

Definitions

  • ABSTRACT OF THE DISCLOSURE A multi-stage compressor package which is enclosed within a casing formed by a pair of separable casing members; and a centrifugal pump assembly for such a compressor package which includes an axial inlet, an outlet surrounding the inlet and coaxial therewith, heat exchange means disposed in the outlet, and moisture separator means disposed in the outlet downstream of the heat exchange means.
  • This invention is concerned with fluid pumps.
  • the invention is concerned with a multi-stage air compressor package wherein the exhaust or compressed air from each compression stage is cooled prior to its entry into the next succeeding stage and prior to its final discharge from the compressor package.
  • the invention is directly concerned with, and represents an improvement over, the single motor driven, multiple pump, multi-stage compressor packages of the type shown in United States Patent No. 3,001,692, issued Sept. 26, 1961, to Schierl.
  • the present invention has for an object the provision of an efiicient multi-stage compressor package.
  • a further object of the invention is to provide a highly efficient multi-stage compressor package which is free from external components, yet which provides for adequate cooling of air between compressor stages.
  • An additional object of the invention is to provide an economically manufactured multi-stage compressor package.
  • Still a further object of the invention is to provide a novel intercooler-pump assembly adapted particularly for use in multi-stage compressor packages while being capable of single stage use where desired.
  • a closed casing an inlet port and an outlet port in said casing; centrifugal pump means within the casing; means serially interconnecting said pump means between the casing inlet and outlet such that air from said inlet is directed serially through said pump means and then discharged through said outlet, said interconnecting means being comprised of a manifold assembly incorporated in the casing and in communication with the inlet and outlet of each serially connected pump; cooling means in heat exchange relation with the outlet of each pump and 3,355,697 Patented Nov. 28, 1967 common drive means for driving all of said serially connected pumps from a single prime mover.
  • each centrifugal pump assembly comprises impeller means; a cylindrical, co-axial inlet means leading to said impeller means; concentric cylindrical outlet means surrounding the cylindrical inlet means; diifuser means directing air from said impeller to said outlet means and cooling means disposed between the co-axial and cylindrical walls of the inlet and outlet means, said cooling means comprising a plurality of heat exchange tubes disposed axially parallel to each other and the center of the inlet and outlet means; header plates supporting the tube ends and defining with the walls of said cylindrical inlet and outlet means a sealed coolant chamber surrounding said tubes.
  • water separation means be disposed on the outlet side of the compress-or stages, same being also doughnut shaped and between the walls of the inlet and outlet means.
  • FIG. 1 is a perspective view showing a compressor package, same in this case having hinged casing or hous-v ing parts and being shown opened as when being serviced.
  • FIG. 2 is an elevational sectional view of a pump unit.
  • FIG. 3 is a sectional view taken along the line 33 of FIG. 1 and showing the port arrangement within the hinged casing part.
  • FIG. 4 is a view similar to FIG. 3 and taken along the line 44 of FIG. 3, to show additional port details.
  • FIG. 5 is a sectional view taken along the line 5-5 of FIG. 2 and showing the interior detail of a heat transfer tube
  • FIG. 6 is a view similar to that of FIG. 3, but taken along the line 6-6 of FIG. 4.
  • a multi-stage compressor package made according to the invention comprises a casing structure including a stationary casing member 10 and, in this instance, a swingable casing member 20 hinged thereto at hinge 1.
  • the hinge 1 may not be used, in which case the casing member 20 would simply be removable from the casing member 10.
  • the casing members It) 20 may be either hingedly or merely detachably connected, it will be understood that hereinafter the terms swingable and removable are used interchangeably to indicate that casing member 20 is movable with respect to casing member 10.
  • the stationary casing member 10 rests on supporting feet 3, 3 which are attached to a motor base 5.
  • a prime mover 7 mounted on base 5 is a prime mover 7, in this case an electric motor, although it will be appreciated that other prime movers, such as an internal combustion engine, can also serve equally well.
  • the prime mover is connected by a gear train (not shown), housed within the back of casing member 10, to a plurality of pump units or assemblies 30 which units will be described later.
  • the gear train arrangement purely conventional in the art, is so arranged as to drive the units 30 simultaneously.
  • Each unit 30 is mounted on the face of a vertical back plate 9 provided at its center with an internally threaded button 11 which receives a central clamping bolt 13 carried by the swingable casing member 20. It will be noted that the units 30 are so arranged as to project outwardly somewhat beyond the vertical plane in which the flanged edge 15 of casing 10 is disposed.
  • swingable or movable casing member 20 is generally dome shaped and also is provided with an interior vertical wall 17 recessed inwardly away from the vertical plane of the edge flange 19 of this member.
  • Wall 17, hereinafter called a manifold wall is provided with groupings of ports 21; each group including a central opening hereinafter referred to as a sun port surrounded by angularly spaced ports having their centers lying in a concentric circle around the sun port, and hereinafter called satellite ports, the function of same to be described later.
  • manifold wall 17, within casing member 20, is such that when same is swung closed or otherwise positioned against stationary casing member and flanges and 19 bolted together, along with threaded engagement of bolt 13 in button 11, the ends of pump units 30 are in face to face contact with wall 17.
  • Suitable gasket means may be interposed between the ends of pump units 30 and manifold wall 17 so that there is a complete sealing between the ends of the units and the wall and there is no communication between units 30 and the space defined between manifold wall 17 and back plate 9.
  • the upper ends of the casing members 10 and 20 are provided with paired and intercommunicating ports 23, 25, 23', 25', respectively. These ports define air inlet and outlet ports which, as will be described, are suitably placed in communication with pump units through the manifold portion of easing member 20 behind manifold wall 17.
  • FIG. 2 illustrating a preferred pump unit structure.
  • back plate 9 is provided with an aperture 29 provided with any form of suitable bushing or bearing member 31.
  • a shaft 33 driven from the mentioned gear train, projects through the opening and terminates in a threaded end receiving nut 35.
  • a conventional centrifugal impeller 37 is keyed on shaft 33.
  • the central portion of the diffuser spider 41 is open at 47 whereby fluid, in this case air, is drawn in axially toward, and centrally of, the impeller and discharged outwardly wherein the shape of passages 43 re-directs flow away from the impeller in a direction parallel to the axis of rotation of the impeller 37.
  • an elongated inlet cylinder 51 having structural means 53 and 54 whereby its inner terminal end may be mated against the spider 41.
  • This outlet cylinder serves along with passages 43 to redirect air from impeller 37 out of the pump unit 30 in a gi7rection parallel to the axis of rotation of the impeller
  • the efiicency of an air compressor can be improved if, at each stage, the outlet air is cooled to remove the heat of compression developed within the compressor.
  • the outlet duct 59 formed between cyllnders 51 and 63 is provided with heat exchanger 70.
  • the heat exchanger 70 is comprised of doughnut shaped headers 55 and 57 sealingly in engagement with the outer surface of cylinder 51 and the inner surface of cylinder 63.
  • the headers are pierced at angularly spaced points around the annular outlet chamber 59 and receive in angularly spaced, parallel relation a plurality of tubes 71.
  • the tube ends are swaged or otherwise locked into immobile relation in the pierced headers 55 and 57, as is conventional practice in the art.
  • air exiting from the impeller 37 is caused to pass through tubes 71 and, if the coolant chamber 72 surrounding the tubes is filled with a suitable coolant fluid, such as water flowing therethrough, the air will be cooled prior to its exit from pump unit 30.
  • FIG. 5 a preferred form of heat exchange tube is shown in section.
  • the center of the tube contains a small diameter core 73 of a good heat conductive metal.
  • a fluted fin element 75 Surrounding the core 73 is a fluted fin element 75 formed so as to contact both the inner surface of tube 71 and the outer surface of core 73 in heat exchange and core supporting relationship.
  • core 73 and fin 75 carry heat outwardly to the tube wall where it is carried to the coolant surrounding the tube.
  • a doughnut shaped separator 80 Immediately succeeding the heat exchanger 70 is a doughnut shaped separator 80. Separator is comprised of annular, axially spaced, concentric frame members 82, 84 having therebetween a vapor entrapping material such as stainless steel crinkle mesh 86, and perforated or screen type of face plates 88, 88. During the operation of the separator 80, the crinkle mesh 86, as will be understood. tends to separate and condense water vapor entrained in the compressed gas emitted from the intercooler 70. Suitable drain means, designated generally as 90 in both FIGS. 1 and 2, is provided to convey the water from separator 80 outside of the casing structure 10.
  • a vapor entrapping material such as stainless steel crinkle mesh 86, and perforated or screen type of face plates 88, 88.
  • each pump unit 30 is disclosed as being identical as to over-all operation and general structure, though there may be variations in capacity between the units, and that if outlet air is properly conducted from inlet 23 through each unit 30, successively, and then to outlet 25' in casing 10, a very simply maintained, highly efficient multi-stage compressor package can be produced.
  • each unit 30 is in cimmunication with the satellite ports of one of the port groups 21 in manifold plate 17, while the inlet cylinder 51 of each unit 30 is in communication with the central or sun port of such group of ports.
  • port groups 21, in turn, are suitably arranged in manifold wall 17 so that casing member 20, in effect, acts as a manifold system directing the fluid from inlet 23 through the successive pump units 30 and then to outlet 25.
  • FIGS. 3 and 4 One manner of forming a manifold system is illustrated in FIGS. 3 and 4 wherein the manifolding or ducting of the casing member 20 is shown as fabricated of welded components.
  • air from inlet 23' in stationary casing member 10 enters the casing member 20 through inlet 23 and thence flows into an upper inlet chamber 81 which is defined by the end wall 83 of easing member 20, a horizontal dividing wall 85 and a vertical duct wall disposed parallel to, but spaced from, manifold wall 17. From chamber 81 the fluid enters the upper right hand pump unit 30 (as viewed from the motor end of casing member 10) through the sun port 87 of upper right hand port group 21 in casing member 20.
  • the inlet chamber 95 is formed by end wall 83 of casing 10, duct wall 90, horizontal divider wall 85 and the lower portion of an additional divider wall 99 which is located on a vertical diametric line and extends completely from top to bottom of casing member 20.
  • fluid discharged from the second pump unit 30 must pass across this wall to reach the third and lower left hand pump unit 30.
  • this is accomplished via port 101 which permits second stage discharged air to enter chamber 103 in the lower left hand quadrant of the swingable casing member 20, said chamber being defined by manifold wall 17, duct wall 90, the exterior wall of easing member 20 and a further horizontal divider wall 102.
  • the chamber 110 as illustrated in FIG. 6, is defined by the casing wall 83, vertical divider wall 99 and a further horizontal divider wall 107, which, with duct wall 90, forms a closed chamber provided with an outlet port 109 which feeds air from third stage pump unit 30 to the fourth and final unit disposed in the upper left hand side of easing member 10.
  • the manifold system is fabricated of suitably welded chambers, ports and baffles, it will be appreciated that same can be incorporated in the movable casing member by forming the casing member as a cast unit with the porting means incorporated therein during the casting process.
  • This latter arrangement which will be simpler and more economical to produce, is particularly attractive for use in, for example, compressor packages of a capacity having the most general industry utility and subject to repetitive manufacture, as distinguished from special order items, that is items of very high capacity suitable for a particular or peculiar industrial application not likely to be repeated.
  • the porting arrangement will be such as to isolate the output of each stage from the output of any other stage so that passage of the fluid or gas is successive through the compressor stages.
  • movable casing member 20 defines essentially a manifold for conducting air or other fluid from stage to stage or successively to and through the pump units 30.
  • this casing member contains no working parts and may easily be made swingable about hinge 1, where used, or easily removed from casing member 10 where same is not hingedly connected to casing member 10.
  • each pump unit 30 with its associated intercooler is easily serviced with the casing open. All components are so affixed to wall 9 of the stationary casing member 10 as to be easily and readily removed for servicing. Further, all external components are eliminated.
  • An air compressor comprising a casing having an inlet and an outlet, centrifgual pump unit means disposed within said casing, means serially connecting said pump unit means between said casing inlet and outlet such that said pump unit means compress the air in successive stages, means disposed within the outlet of each pump unit means for cooling the air compressed in each pump unit means before its entry into the next succeeding pump unit means, and water separation means disposed in the outlet of each pump unit means, all of said means being totally enclosed within said casing.
  • An air compressor comprising a casing including two separable members and having an inlet and an outlet, centrifugal pump unit means disposed within said casing, means serially connecting said pump unit means between said casing inlet and outlet such that said pump unit means compress the air in successive stages, said serial connecting means being completely housed in one of said casing members, and means disposed within the outlet of each pump unit means for cooling the air compressed in each pump unit means before its entry into the next succeeding pump unit means, all of said means being totally enclosed within said casing.
  • a multi-stage air compressor comprising a closed casing including a stationary casing member and a removable casing member connected to said stationary casing member, an inlet port and an outlet port in said casing, centrifugal pump means disposed within the stationary casing member, said removable casing member comprising a manifold for serially connecting the pump means between said inlet port and said outlet port in said casing for communicating such inlet port and such outlet port with the inlet and outlet of each pump, cooling means in heat exchange relationship with the outlet of each pump within the casing and common drive means for powering all of the pumps simultaneously.
  • a compressor as defined in claim 5 wherein said pump means is comprised of a plurality of substantially identical pump assemblies, each of said assemblies including an outlet intercooler integrated therein and a moisture separator disposed downstream of said outlet intercooler.
  • a multi-stage compressor package including a casing and a duct system for serially directing air through successive compression stages; a pump assembly, said pump assembly including an impeller; a diffuser spider containing said impeller; an inlet means associated with said diffuser spider for supplying air to said impeller in a direction co-axial with the axis of rotation of said impeller; an outlet means surrounding said inlet means; passage means formed within said diffuser spider for communicating said outlet means with said inlet means; heat exchanger means disposed within said outlet means; and a fluid separator disposed in said outlet means for separating entrained moisture from the air after its flow through said heat exchange means.
  • a centrifugal pump assembly comprising an impeller; a diffuser spider containing said impeller; inlet means arranged to supply fluid to said impeller in a direction co-axial with said impeller; outlet means surrounding said inlet means; means for communicating said outlet means with said inlet means such that fluid discharged from said impeller is discharged through said outlet means; heat exchange means disposed within said outlet means peripherally of said inlet means; and moisture separator means disposed in said outlet means downstream from said heat exchange means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US515559A 1965-12-22 1965-12-22 Fluid machine Expired - Lifetime US3355097A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US515559A US3355097A (en) 1965-12-22 1965-12-22 Fluid machine
GB55704/66A GB1149960A (en) 1965-12-22 1966-12-13 Multi-stage compressor
SE17299/66A SE319263B (enrdf_load_html_response) 1965-12-22 1966-12-16
DE1966J0032562 DE1628299B2 (de) 1965-12-22 1966-12-20 Mehrstufiger radialturboverdichter mit einem aus mehreren gehaeuseteilen bestehenden gehaeuse
FR88445A FR1505948A (fr) 1965-12-22 1966-12-22 Compresseur

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US515559A US3355097A (en) 1965-12-22 1965-12-22 Fluid machine

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DE (1) DE1628299B2 (enrdf_load_html_response)
FR (1) FR1505948A (enrdf_load_html_response)
GB (1) GB1149960A (enrdf_load_html_response)
SE (1) SE319263B (enrdf_load_html_response)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3658442A (en) * 1970-06-08 1972-04-25 Northern Research And Engineer Compressor
US4010016A (en) * 1975-05-27 1977-03-01 Ingersoll-Rand Company Gas compressor
US4050846A (en) * 1975-06-25 1977-09-27 Klein, Schanzlin & Becker Aktiengesellschaft Fluid circulating apparatus
US4685509A (en) * 1984-08-17 1987-08-11 Mannesmann Aktiengesellschaft Cooling device for a multistage compressor
US4874575A (en) * 1987-07-06 1989-10-17 Rockwell International Corporation Multiple discharge cylindrical pump collector
US20090155096A1 (en) * 2007-12-13 2009-06-18 Cameron International Corporation Heat exchanger
US20100303658A1 (en) * 2009-05-29 2010-12-02 Hitachi Industrial Equipment Systems Co., Ltd. Water-Cooled Oil-Free Air Compressor
WO2013184367A1 (en) * 2012-06-08 2013-12-12 Oxea Corporation Vertical cooler with liquid removal and mist eliminator
WO2019229533A3 (en) * 2018-05-31 2020-03-19 Palma Maria Yzabell Angel V Airdisc technology: centrifugal compression and decompression for cooling
US20220388374A1 (en) * 2017-08-04 2022-12-08 Tesla, Inc. Technologies for manifolds

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RO111492B1 (ro) * 1995-12-21 2003-08-29 Comoti S.A. Compresor centrifugal cu multiplicator încorporat

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1265650A (en) * 1917-04-14 1918-05-07 Escher Wyss Maschf Ag Cooling device in multistage centrifugal compressors.
US2518246A (en) * 1945-07-20 1950-08-08 Garrett Corp Expansion means for cooling an aircraft cabin
US3001692A (en) * 1949-07-26 1961-09-26 Schierl Otto Multistage compressors
US3211362A (en) * 1963-04-05 1965-10-12 Int Harvester Co Turbochargers

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1265650A (en) * 1917-04-14 1918-05-07 Escher Wyss Maschf Ag Cooling device in multistage centrifugal compressors.
US2518246A (en) * 1945-07-20 1950-08-08 Garrett Corp Expansion means for cooling an aircraft cabin
US3001692A (en) * 1949-07-26 1961-09-26 Schierl Otto Multistage compressors
US3211362A (en) * 1963-04-05 1965-10-12 Int Harvester Co Turbochargers

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3658442A (en) * 1970-06-08 1972-04-25 Northern Research And Engineer Compressor
US4010016A (en) * 1975-05-27 1977-03-01 Ingersoll-Rand Company Gas compressor
US4087197A (en) * 1975-05-27 1978-05-02 Ingersoll-Rand Company Gas compressor, and for use with a gas compressor: gear housing and gas-handling assembly, and heat exchanging assembly
US4050846A (en) * 1975-06-25 1977-09-27 Klein, Schanzlin & Becker Aktiengesellschaft Fluid circulating apparatus
US4685509A (en) * 1984-08-17 1987-08-11 Mannesmann Aktiengesellschaft Cooling device for a multistage compressor
US4874575A (en) * 1987-07-06 1989-10-17 Rockwell International Corporation Multiple discharge cylindrical pump collector
US20090155096A1 (en) * 2007-12-13 2009-06-18 Cameron International Corporation Heat exchanger
US8393860B2 (en) * 2007-12-13 2013-03-12 Cameron International Corporation Heat exchanger
EP2235464B1 (en) * 2007-12-13 2019-05-08 Ingersoll-Rand Company Heat exchanger
US20100303658A1 (en) * 2009-05-29 2010-12-02 Hitachi Industrial Equipment Systems Co., Ltd. Water-Cooled Oil-Free Air Compressor
WO2013184367A1 (en) * 2012-06-08 2013-12-12 Oxea Corporation Vertical cooler with liquid removal and mist eliminator
US20220388374A1 (en) * 2017-08-04 2022-12-08 Tesla, Inc. Technologies for manifolds
US12151539B2 (en) * 2017-08-04 2024-11-26 Tesla, Inc. Technologies for manifolds
WO2019229533A3 (en) * 2018-05-31 2020-03-19 Palma Maria Yzabell Angel V Airdisc technology: centrifugal compression and decompression for cooling

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DE1628299A1 (de) 1970-08-20
DE1628299B2 (de) 1977-04-21
SE319263B (enrdf_load_html_response) 1970-01-12
GB1149960A (en) 1969-04-23
FR1505948A (fr) 1967-12-15

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