US3202343A - Compressor arrangement - Google Patents

Compressor arrangement Download PDF

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Publication number
US3202343A
US3202343A US195118A US19511862A US3202343A US 3202343 A US3202343 A US 3202343A US 195118 A US195118 A US 195118A US 19511862 A US19511862 A US 19511862A US 3202343 A US3202343 A US 3202343A
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United States
Prior art keywords
blades
compressor
hub
pair
bore
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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
Application number
US195118A
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English (en)
Inventor
Dieter K Emmermann
John H Davids
Wallace E Johnson
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.)
Desalination Plants Developers of Zarchin Process Ltd
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Desalination Plants Developers of Zarchin Process Ltd
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
Priority to NL288322D priority Critical patent/NL288322A/xx
Application filed by Desalination Plants Developers of Zarchin Process Ltd filed Critical Desalination Plants Developers of Zarchin Process Ltd
Priority to US195118A priority patent/US3202343A/en
Priority to GB40285/62A priority patent/GB1024574A/en
Priority to DE19621428074 priority patent/DE1428074A1/de
Priority to DE19621794308 priority patent/DE1794308A1/de
Priority to DE19621728495 priority patent/DE1728495A1/de
Priority to NL63288322A priority patent/NL146578B/xx
Priority to CH561466A priority patent/CH434547A/de
Priority to CH578963A priority patent/CH421005A/de
Priority to US415345A priority patent/US3255514A/en
Application granted granted Critical
Publication of US3202343A publication Critical patent/US3202343A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • C—CHEMISTRY; METALLURGY
    • C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F1/00—Treatment of water, waste water, or sewage
    • C02F1/22—Treatment of water, waste water, or sewage by freezing
    • 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
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F04D29/305—Flexible vanes
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/382—Flexible blades
    • C—CHEMISTRY; METALLURGY
    • C02—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F—TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F2103/00—Nature of the water, waste water, sewage or sludge to be treated
    • C02F2103/08—Seawater, e.g. for desalination
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A20/00—Water conservation; Efficient water supply; Efficient water use
    • Y02A20/124—Water desalination
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/4932—Turbomachine making
    • Y10T29/49321—Assembling individual fluid flow interacting members, e.g., blades, vanes, buckets, on rotary support member

Definitions

  • This application relates to the construction and arrangement of a compressor which may be employed in this system.
  • sea water is flash-evaporated in a lowpressure evaporating chamber to form pure water vapor, pure ice, and concentrated brine.
  • the compressor withdraws the vapor from that chamber and delivers it to a low-pressure condensing chamber where the vapor and ice and brought together to condense the vapor and simultaneously melt the ice to produce the final sea-water product.
  • a compressor of this type for use in vacuum-freezing systems must move and handle a large volume of vapor at low pressure, will be of great size and have a rotor which operates at high speed.
  • the compressor is subject to low pressure at both its intake It is important that the impeller be as light as possible, because of the speed at which it operates.
  • an object of the invention is to provide a compressor of improved, simplified, economical construction.
  • a further object is to provide such a compressor which can operate under subatmospheric pressure conditions.
  • Another object is to provide an improved arrangement of a compressor, an evaporating chamber, and a condensing chamber for a vacuum-freezing system, for delivering vapor from the evaporating chamber into the condensing chamber.
  • Another object is to provide an improved compressor rotor assembly.
  • a still further object is to provide an improved compressor rotor assembly, including rotor blades of thin sheet material flexibly mounted on a central hub wherein the thin rotor blades assume operative positions due to centrifugal forces.
  • Another object is to provide an improved compressor rotor construction which can handle large volumes of vapor and yet is of relatively lightweight construction.
  • Another object of the present invention is to provide a new and improved method of assemblying rotor blades and rotor.
  • FIG. 1 is a schematic layout of a desalination system
  • FIG. 2 is an enlarged fragmentary view in partial sec- 3,2@Z,343 Patented Aug. 24, 1965 J tion of the compressor and chambers arrangement of FIG. 1;
  • FIG. 3 is an enlarged fragmentary detailed view of the connection between the inducer rotor and blades of the inducer assembly of FIG. 2;
  • FIG. 4 is an enlarged fragmentary detailed view of a compressor rotor employed in the arrangement of FIG. 2;
  • FIG. 5 is a detailed side view of a pair ofinducer blades before bending thereof to seat the blades in the rotor hub;
  • FIG. 6 is a view in side elevation of an inducer blade blank from which the blades of FIG. 5 are formed;
  • FIG. 7 is a view in top elevation of the blades of FIG.
  • FIG. 8 is a view in section taken along line 8-8 of FIG. 5;
  • FIG. 9 is a view in section taken along line 9-9 of FIG. 5;
  • FIG. 10 is a View in section taken along line 1010 of FIG. 5;
  • FIG. 11 is a View in section taken along line 11-11 of FIG. 5;
  • FIG. 12 is a view similar to FIG. 6 illustrating a pair of compressor blades before bending thereof for seating in the rotor hub;
  • FIG. 13 is a fragmentary view of the inducer rotor with the blade blank of FIG. 5 bent to form a pair of blades having the common bight thereof disposed in the rotor;
  • FIG. 14 is a view in section taken along line 1414 of FIG. 13 illustrating the first step in contouring the blade common bight to the rotor;
  • FIG. 15 is a view similar to FIG. 14 illustrating the second step in contouring the blade bight
  • FIG. 16 is a view similar to FIG. 14 illustrating the blade bight contoured to the rotor and locked in place;
  • FIG. 17 is an enlarged fragmentary view in elevation illustrating the step of spreading the common bight of a pair of blades.
  • FIG. 1 The desalination system, with which the compressor of the present invention is used, is shown as a general layout in FIG. 1, the novel compressor being disposed in the upper central portion of FIG. 1. The general arrangement of this system will be first briefly described.
  • Sea water which is at ambient temperature, and which has been filtered to remove floating material and other solids is brought into the system through sea water inlet pipe 10 and passes through deaerator 12 where dissolved gas is removed fromthe sea water.
  • the sea water is then delivered by pump 14 to heat exchanger 16, where the incoming sea water is placed in heat-exchange relationship with the potable water final product and concentrated brine being withdrawn from the system.
  • the sea water entering the system will be normally at ambient temperature,'such as for example 77 F. and normally contains about 3.5% by weight of salt,
  • the sea water leaving heat exchanger 16 will be at a temperature of approximately 302 F. and is delivered through pipe 18 into the evaporating chamber 20.
  • the sea water enters the evaporating chamber at the central hub of a distributor 22 (FIG. 2) and the water'thereafter flows downwardly over depending sheets on the distributor so that the incoming sea water has a large surface proportional to surface area.
  • the heat of vaporization is approximately 1074 Btu. per pound and the heat of fusion of ice is about 1144 B.t.u. per pound.
  • heat is removed from the remaining liquid and ice is formed therein. Due to the differences in heat of vaporation and heat of fusion, approximately 7 /2 pounds of ice will be produced for each pound of water vapor.
  • the ice so produced is substantially pure water ice with no appreciable amount of salt contained therein.
  • the temperature within the evaporating chamber will be approximately 24.8" F.
  • the vapor formed will be pure water vapor.
  • the remaining sea water becomes a more concentrated salt solution.
  • a distributor means (not shown) is disposed within evaporating chamber 20.
  • the brine, with the ice crystals therein, is withdrawn from the bottom of evaporating chamber 20 through pump 24, and this mixture has a temperature of approximately 24.8 F.
  • the mixture is delivered to separator washer or counter washer 26, in which the ice is separated from the concentrated brine and the ice is washed free of salt adhering to the surface of the ice crystals.
  • a motor-driven scraper r wiper 34 which wipes off the top of the upwardly moving column of ice and delivers the ice into trough 36.
  • Spray heads 38 are provided at the top of count-er washer 26 for spraying sweet water supplied by pipe 40 onto the top of the porous column of ice, which water runs downwardly over the advancing column of ice to wash away any adhering brine on the surface or in the interstices of the ice.
  • Sweet water is added by means of pipe 42 to the icein trough 36 so as to produce a solution of sweet water and ice suspended therein which can be pumped.
  • the radial compressor generally indicated at 54 which forms the subject of this application, is positioned within the upper end of condensing chamber 50 and has an axial intake opening 56 in communication with evaporating chamber and a circular outlet 58 communicating with condensing chamber 50.
  • Vapor formed in evaporating chamber 20 is drawn into central inlet 56 of compressor 54 and delivered radially outward into condensing chamber 50 through outlet 58.
  • the vapor is thus compressed and compressor 54 maintains condensing chamber 50 at a pressure of approximately 4.6 mm. Hg.
  • the vapor delivered by the compressor into the condensing chamber passes downwardly on the compressor.
  • the sweet water thus produced is withdrawn from the lower end of condensing chamber 50 through pipe 60, which delivers a portion of the sweet water back to counter-washer 26 through pipes 40 and 42 for ice washing and for mixing with the ice.
  • the majority of the sweet water product passes through pipe 62 to heat exchanger 16.
  • the housing of the vessel into which the compressor discharges is the real structural support housing of the compressor.
  • the compressor serves as a self-regulator upon the system since the amount of vapor that can be handled by the compressor will control the rate atwhich vapor is formed by vap0rization and the rate at which it is condensed.
  • the vapor should be delivered to the evaporating chamber at saturation conditions of pressure and temperature so that the vapor will condense on the 32 F. ice will take out of the vapor 1,074 Btu. per pound of vapor condensed and thereby cause the 32 F. ice to melt by each pound absorbing 144 B.t.u.
  • the drive mechanism between the motor and the compressor is of a unique type. Motor is flooded with water delivered to the motor housing by pump 72 through pipe 74 and this water is circuated through the motor housing and discharged through pipe 76.
  • This drive mechanism provides an effective seal for the drive shaft of the compressor, withoutthe use of expensive and elaborate mechanical seals, which are normally required for such high pressure difierentials by allowing leakage of sweet water from the motor hous- 1ng into the condensing chamber.
  • Sweet water flowing in the motor housing cools the motor and that portion of the sweet water leaking into the condensing chamber flash-evaporates to cool the compressed vapor and partially reduce the super-heat in the vapor.
  • the final product potable water
  • the final product is delivered from condensing chamber 50 through pipe 62 to the heat exchanger 16 and is at a temperature of approximately 32 F.
  • the concentrated brine which has been separated from the ice in counterwasher 25 is delivered Via pump 30 to the heat exchanger through pipe 78 and is at a temperature of approximately 24.8 F.
  • the purpose of the heat exchanger is to cool the incoming sea water to the maximum extent possible by withdrawing heat therefrom and delivering it to the cold brine and sweet water produced, and it is important that the sea water be cooled as efficiently as possible.
  • approach temperatures of about 2 F. have been achievedand, thus, sea water entering the system through cold sea water pipe 18 is at about 302 F.
  • the sweet water, as it leaves heat exchanger 16 through pipe 80, is the principal product of this system and is delivered to storage tank 82 from which it may be withdrawn for use.
  • the warmed concentrated brine, as it leaves heat exchanger 16 through pipe 84, is delivered to the waste outlet 68 for return to the sea or for other use or disposal.
  • a higher pressure is necessary in the condensing chamber than in the evaporating chamber because the vapor pressure of the freezing brine is lower than the vapor pressure of the ice-water mixture at 32 F.
  • the vapor pressure of brine of 7% by weight salinity at 24.8 is about 3.2 mm. Hg, while the vapor pressure of ice-water mixture at 32 F. is about 4.6 mm. Hg.
  • compressor 54 is disposed within the outer housing of the condensingevaporating chambers.
  • the compressor is disposed immediately below cover 110 of chamber and above cylindrical walls 94 of evaporating chamber 20.
  • the compressor is actually supported by this cover and comprises a housing or shroud 134, having a top housing 136 and a lower housing or shroud 138, which are preferably constructed of fiber glass and which are secured together but spaced apart around the periphery of the compressor by-attachment means 140.
  • Bottom shroud 138 is provided with the previously mentioned central inlet 56, and the annular space between the top and bottom shrouds, extending completely around the compressor, provides the circular outlet 58 previously identified.
  • Shrouds 136 and 138 are so sealed to the walls of the chambers that the only communication between the chambers is through central inlet 56, the interior of the compressor, and circular outlet 58.
  • Impeller 142 comprises a plurality of pairs of radially extending blades 144, each pair having a common bight, and central hub 146 and is rotated bymotor 70 within housing 134.
  • this compressor in order to move the volume of vapor required, this compressor is large and rotates at a relatively high speed.
  • the diameter of impeller 142 will be approximately 7 feet and the speed of rotation will be 3,600 r.p.m.
  • cover 110 is a substantial structural member, it is able to afford the necessary shroud or covering for the impeller and is of relatively light material.
  • the chamber into which the compressor is discharging serves here as the housing for the compressor and support for the drive.
  • vapor formed within evaporating chamber 20 is drawn into central'inlet 56, and is moved by rotating bladed inducer 143 and rotating blades 144 radially outward at progressively increasing pressure for ultimate discharge through circular outlet 58 into condensing chamber 50.
  • the compressor affords a direct radial path for movement of the vapor.
  • vapor will be drawn into the compressor throughout the entire area of central inlet opening 56 and discharged throughout the entire area of circular outlet 58.
  • vapor will be delivered around the entire annular area of condensing chamber 50 for movement into contact with the ice that has been spread out within substantially the entire of the condensing chamber.
  • the presently improved compressor generally indicated at 54 is particularly suitable for use in the aforementioned Compressor 54 is lies the upper end of evaporating chamber 20 with its intake port 56 open to chamber 20.
  • the compressor discharge outlet 58, peripherally thereof, is directly open to the condensing chamber 50.
  • the compressor 54 is an axial h intake, raclial discharge unit of improved and compact construction.
  • It includes a two-part housing or casing 134 of metallic or non-metallic material, as suitable sheet metal of corrosion-resistant character or suitable plastic,
  • fiber glass, or other similar material comprising an upper wall-forming member or housing 136 of circular periphery and a lower member or shroud 138, also of circular periphery and spaced from the upper member to form the rotor chamber 164 therebetween.
  • Assembly connection of the members 136 and 138 is made by a plurality of attachment means and spacer elements 140 relatively spaced about the peripheral region of the housing in connection to the respective peripheral end portions 166 and 168 of the members.
  • .ber 138 is formed to provide a wall 1'70 of predetermined shallow frusto-conical form between the generally radial end portion'168 and an out-turned circular flange 172, the latter defining the axial inlet eye or intake port 56
  • the upper member 136 is formed to' provide a similar but oppositely directed shallow frusto-conicalwall section 174 inwardly from its generally radial end portion 166, merging into the inner wall section176 which lies in a radial plane normal to the rotor axis of the compressor.
  • the two wall sections 170 and 174 converge toward the discharge outlet 58 from a zone which, in the present example, is slightly radially beyond the inlet flange 172.
  • the lower housing member 138 includes an ex ternal, depending annular flange 184 which seats in compressive engagement with resilient seal element 186, of rubber or the like, carried in an annular channel 187 on the outer overhanging margin 190 of the end wall 132 of chamber 20.
  • Each rib 182 terminates in a lateral projection forming a pad against which the flange 1% of the compressor housing wall 134 abuts, such pad serving to effect the desired assembly location of the wall. Due to the vacuum .in the chambers, considerable load will be exerted on cover 110 to cause deflection thereof, but since compressor 54 is supported and carried thereby, no problems to the compressor result from this deflection.
  • a compressor rotor assembly or rotatable impeller 142 comprising a hub structure 146 on a vertical drive shaft 196, and a plurality of generally radial blades 144, constructed in accordance with the present invention, projecting from the hub.
  • the hub structure comprises a shaft-mounting sleeve hub 198 keyed to, pressed on, or otherwise fixed to drive shaft 196' and held thereon as by a retainer plate 200 bolted to the shaft, and a blade hub 202, here shown constructed in one piece, secured as by bolts 204 to the I flange portion 206 of shaft hub 198.
  • each bore 208 has a radial slot 210 of predetermined width, opening the bore to the hub periphery, the slots as well as the bores being open at each side face 212 of the hub.
  • the bores and slots form blade mounting seats.
  • Each blade 144 is formed from a strip of flexible sheet material having a predetermined thickness.
  • the blade material here used is fiber glass, or corrosion-resistant metal, as stainless steel or the like.
  • an elongate rectangular strip of predetermined'length and width is lengthwise reversely turned or folded upon itself, folding being about a round bar or arbor (not shown) at the strip center, to provide a pair of blades 144 having a common bight or a hollow circular enlarged or eye portion 218 at one common end.
  • Each pair of blades over their outer end section 222 (FIG. '12) is marginally cut or reduced on one side to provide a blade margin 224 such that the blade will have a running clearance in the converging zone of the compressor housing formed by the wall portions and 174, FIG. 2.
  • the inducer hub 300 is provided with a plurality of circular through bores 302 extending parallel to the shaft axis and being inwardly adjacent to the hub peripherally and equi-angularly spaced circumferentially of the hub.
  • Each bore has a radial slot 304 of predetermined Width opening the bore to the hub periphery, the slots as well as the bores being open at each side face 306 of the hub (FIG. 3).
  • the bores and slots form inducer blade mounting seats.
  • a pair of inducer blades 308 and 310 are formed from a flexible single stock blank of strip sheet material (FIG. 6), such as metal or a plastic fiber glass material, having a predetermined thickness and contour (FIGS. 3, 611, and 13).
  • the strip of sheet material is bent around a round bar or arbor (not shown) at the strip center to form a common bight 311 (FIG. 13) and thereby provides a pair of blades '(FIG. 3) having an enlarged common eye portion at one end.
  • An inducer The inducer blades are preferably provided with a bucket shape for efficient operation thereof. To this end, the outer ends 318 of each blade 308 and 310 are pre-formed before bending of the stock strip (FIG. 6) to provide the bucket shape thereto.
  • the strip 312 is bent at a plurality of locations at predetermined angles at each end thereof substantially along the dotted lines shown in FIG. 6 to provide flanges defining the desired bucket shape.
  • a strip 312 having the exemplary dimensions shown in FIGS. 5-7, may be bent along line 8-8 of FIG. 6 and at the angle indicated in FIG. 8 to provide the flange 316 with the dimensions indicated in FIG. 8.
  • the strip may be bent at other locations as indicated in FIGS. 9, 10 and 11 at locations shown in FIG. 6 and at the angles indicated in these figures to provide the flanges 316 with the dimensions noted in these figures.
  • the dimensions given are exemplary only and that, depending upon the requirements of the rotor arrangement desired, these parameters of the inducer blade may be determined by employment of known computation methods.
  • the strip 312 may be bent at its center around an arbor (not shown) to form the two blades 308 and 310 having the common bight 311 (FIG. 13).
  • a mounting plate 318 for a rod 320 which carries a semi-hemispherical shell 322 of rigid material, such as fiber glass or stainless steel.
  • the shell is centrally carried near the top of the chamber 20 and serves as a streamline surface which cooperates with the inducer arrangement of the present invention to direct the flow of vapor from chamber 20 to the impeller of the compressor.
  • the compressor blade mounting arrangement is similar in construction to the inducer blade mounting arrangement, and, thus, the description to follow of the inducer blade mounting arrangement, it will be appreciated, applies equally to the description of the impeller blade mounting arrangement.
  • the bight of each pair of blades is longitudi nally inserted in a bore 302 of the blade hub 300 in such a manner that the blades 308 and 310 extend through the corresponding slot 304 in the hub 300 (FIG. 13).
  • the bight 311 of the blades 308 and 310 is of lesser dimension than the bore 302. Such sizing of the bight 311 facilitates contouring of the bight to the bore 302 and permits expansion of the bight to the dimension of the bore.
  • a tapered tap tool 322 (FIG. 14) is forced from the top or bottom of the rotor 300 into the space defined by the bight 311 to spread and contour the bight.
  • the tap tool 322 is provided with a tapered elongated conical portion 323 which is inserted first into the space defined by the bight 311 and is also provided with a head 324 of cylindrical external configuration which is of a diameter corresponding generally to the diameter of a removable pin 326 (FIG. 15) which is employed to secure the common bight in the bore and to prevent lateral translation of the blades 308 and 310.
  • the hollow pin.326 (FIG. 15 is placed on top of the head 324 and forced into the space occupied by the head 324 which results in removal of the tool 322 from the said space.
  • the hollow pin 326 is forced into the spaced defined by the inner surface of the bight 302 until the top surface 327 and bottom surface 328 of the pin are flush with the corresponding surfaces 301 of the hub 300 as appears in FIG. 16.
  • a feature of the present invention resides in the provision of means for initially contouring the blades at points a to correspond to arcuate surfaces 330 of the webs 332 defined by adjacent bores 302 and by the provision of strengthening means hereinafter described which are employed to maintain the blades contoured at points a during operation of the impeller and inducer assemblies.
  • Means for initially contouring the blades at points a to the arcuate surfaces 330 may take the form of a wedging tool, generally indicated by the numeral 334 in FIG. 17, and which comprises a handle 336 and a head 338.
  • the head 338 is provided with a concave outer surface 340 having a curvature corresponding to the outer curvature of the pin 326 against which the surface 340 is designed to rest.
  • the side walls 342 and 344 of the head 338 are convergingly tapered and of a width dimension corresponding to the width dimension of the blades 308 and 310.
  • the tool head is inserted between the blades 308 and 310 when in the positions shown in dotted lines in FIG. 17 and the tool pushed inward to spread the blades 308 and 310 until the head surface 340 engages the outer surface of the pin 326, as shown in full lines in FIG. 17.
  • the side walls 342 and 344 of the head 338 spread the blades 308 and 310 and in so doing bend and contour the blades at points a to the configuration of the arcuate surfaces 330 of the webs 332.
  • the tool head 338 is removed from contact with the pin 326 and after removal of the tool, the blades will have a pro-formed contour at points a.
  • the means for maintaining the blades in position with the common bight seated in the bore of the rotor hub may, in accordance with the present invention, take the form of a U-shaped wedge shoe 346 (FIG. 3) of a length corresponding to the thickness of the hub 300.
  • the shoe 346 is provided with an arcuate body portion 348 and depending parallel flanges 350 and 352.
  • the flanges each have an edge in line contact with pin 326 when the shoe is removably secured to the pin 326 by a screw 354 threaded through an aperture in the shoe 346 and through a corresponding aperture 356 in the pin 326.
  • the shoe 346 spreads the blades 308 and 310 when in threaded engagement with the pin 326 in such a manner that the side Walls 358 and 360 of the flanges 352 and 350 urge the blades 308 and 310 against the webs 332 and cooperate with the pin 326 and webs 332 at points a to maintain the blades at these points in contact with the arcuate surfaces 330 of the webs 332.
  • the blades do not have a tendency to break at points a during the normal expected use life of the compressor assembly.
  • a plurality of U-shaped damping clamp wedge members 364 are employed around the periphery of the hub 300, Where, for example, sixteen bores are formed in the hub thus providing for employment of sixteen pairs of blades 308 and 310.
  • the wedge members 364 are U-shaped or wing-shaped ill in configuration and comprise a body portion 366 in engagement with the body 348 of the shoe 346.
  • the body has extending therefrom flexible flanges 367 and 368.
  • the flanges 367 and 368 each engage the inner surfaceof the blades 308 and 310, respectively.
  • the Wedge member 364 is preferably secured in engagement with the shoe 346 by means of the screw 354 passing through a threaded aperture in the body portion 366 thereof. When in the position shown in FIG. 3, the flanges 367 and 368 maintain the blades 308 and 310 in spaced-apart relation.
  • a plate 37% may be employed to distribute the pressure applied to the wedge during threading of the screw 354.
  • the wedge members 364 may be constructed of sheet material formed with the flanges 367 and 368 and bored and threaded for receiving the screw 354.
  • a plurality of second clamping clamp wedge members 372, corresponding to the configuration of the wedge members 364, are provided with a body portion 374 and flexible flanges 376 and 378.
  • the body portion 374 is apertured and threaded to receive a threaded screw 330 which secures the wedge member 372 to the web 352 which is bored and threaded to receive the screw 380.
  • the flanges 376 of the wedge members 372 cooperate with the adjacent flanges 368 of the wedges sm to support the blades 31!) adjacent the common bight 311.
  • the flanges 378 of the wedge members 372 cooperate with the adjacent flanges 367 of the wedges 364 to strengthen and support the blades 3% adjacent the common bight 311.
  • the plurality of alternative first Wedge members 3&4 and second wedge members 372 positioned around the periphery of the hub 360 cooperate to provide a blade support and strengthening arrangement for a plurality of pairs of blades 368 and 310, each pair having a common bight 311.
  • a plurality of plates 332 and 384 may be provided for distributing the force applied to body 374 of the wedge members 372 by the screws 38h.
  • pipe plugs may be threaded into the ends of the pins 326 (FIG. 16) and the pins may be provided with slots 3% for expansion thereof by the pipe plugs to lock the blades in position.
  • the blades 144 as aforesaid are formedin pairs having a common bight, are flat, and do not have flanges 316.
  • each pair of blades has a common enlarged end, or eye 218 inserted and seated in one of the hub bores 2% with the blades projecting outwardly therefrom through the associated bore slot 210.
  • the outer diameter of the common bight or blade eye 218 is such as to effect a snug fit thereof in the bore, while the width of the bore slot 21% is such as to closely confine the blade portions extending therethrough.
  • the webs 395 (FIG. 4) of the hub are provided with an arcuate surface 397 at points a and the blades are bent at these points as indicated above in connection with the description of the mounting of the inducer blades 3% and 31%.
  • Pipe plugs may be employed to close the ends of the pins 326 having the slots 3% therein.
  • the blades 144 thus mounted on hub 202 extend therefrom in the compressor housing rotor chamber 164 with the reduced or convergingly tapered end portions 224- thereof in close running fit in the converging zone of the housing provided by walls 170 and 174.
  • These rotor blades M4 being'constructed of thin sheet strips in the manner described, afford lightweight flexible blades which, mounted as shownand described, permit highspeed operation of the rotor.
  • the blades have a predetermined minimum thickness as, for example, ap proximately two hundredths of an inch (.02 inch) in a blade having a length of about thirty one (31) inches and a width of about nine (9) inches inwardly of its tapered end.
  • the improved rotor structure is one which will be economically constructed with easy-to-fabricate blades and a simple yet highly blade-mounting and damping arrangement.
  • the thin blades formed in the manner described facilitate desired high-speed rotation of the rotor under vacuum conditions and such high-speed operation is further facilitated by the absence of rotating blade shrouds.
  • the compressor as herein illustrated and now described is designed and fully effective for handling water vapor in large amounts and at a relatively low compression ratio, under the desired sub-atmospheric conditions.
  • the opening sides or diameter of the compressor inlet eye 56 is determined-in accordance with the desired velocity of vapor intake and flow rate in the compressor.
  • the inlet is of relatively large diameter and open to the blades over approximately the inner half lengths there- 0 pendent on rotor speed and the outer diameter of the rotor blading, these factors are selected to obtain the desired compression ratio suitable to the purpose of the system referred to.
  • a compressor constructed in accordance with the present invention under operating conditions is required to move approximately two hundred thousand ft. vapor per minute to obtain sixty thousand gallons per day of the final product, sweet water.
  • the weight of the compressor assembly is relatively light when compared to comparable compressor assemblies.
  • the rotor itself, serves as a tool in the formation and mounting of the pairs of blades, which formation would be otherwise diflicult to achieve because of the high-spring back characteristics of the material employed for blade construction.
  • the rotor hubs and the pin 326 are plated with a corrosive resistant material, such as tin. It will also be appreciated that with the present invention the area of greatest cost of manufacture, i.e., blade construction and mounting to the hub, has been minimized.
  • the straight peripheral portions or margins 166 and 168 of the compressor housing defining the compressor outlet 58 which is open circumferentially of the compressor, forms a diffuser wherein the dynamic energy ofthe discharged vapor is converted to static pressure.
  • Such diffuser may be extended to form a con tinuation of the compressor housing wall member 138 and, cooperating with the adjacent top portion 110, provides a downwardly directed annular outlet into condensing chamber 5i).
  • the compressor and compressor rotor are of extremely simple, compact and emcient construction and yet economical incest and high speed in operation.
  • the rotor assembly has blades of thin sheet material in a flexible mounting on' a central hub and can handle large volumes of vapor at a relatively low compression ratio under the given sub-atmospheric pressure conditions with the blades assuming operative positions responsive to centrifugal force.
  • a compressor arrangement adapted to be disposed between said compartments with an inlet opening into said first compartment and an outlet opening into said second compartment, said compressor including a rotatable hub carrying at least one pair of flexible, elongated blades of thin cross section, said hub being provided with a bore extending parallel to the axis of rotation of the hub, said bore opening to the periphery of the hub, each compressor blade being joined to another compressor blade to form a pair of blades having a common bight portion, said common bight portion of said pair of blades being seated in the bore with the pair of blades extending through the opening of the bore, and means for mounting the common bight portion of said pair of compressor blades to said compressor, said mounting means incuding a pin in the space defined by the common bight portion for urging the bight portion against the wall of the bore and
  • said strengthening means includes a first wedge member located between said blades for urging the pair of blades in spaced relation to each other, said "wedge member cooperating with said pin to hold said pair of blades to said hub.
  • a radial compressor arrangement adapted to be disposed between said compartments with an inlet opening into said first compartment and an outlet opening into said second compartment, said radial compressor including a rotatable hub carrying a plurality of flexible, elongated blades of thin cross-section, a two-part housing comprising a first wall forming member and a spaced second wall forming member, the second member having an intake port adapted to open directly into said first compartment, the compressor blades being carried by the hub in the space between said members, said outlet of said compressor being the space between said members defined by the peripheries of said members, said outlet adapted to open directly into said second compartment, each of'said compressor blades be ing joined to another compressor blades to form a pair of blades having a common bight portion, said bight portions being carried by said compressor hub, said hub having a pluralit
  • each shoe member is mounted to the corresponding pin.
  • a compressor arrangement adapted to be disposed between said compartments with an inlet opening into said first compartment and an outlet opening into said second compartment, said compressor including a rotatable hub carrying a plurality of flexible elongated blades of thin crosssection, and a bladed inducer rotor having an inducer hub axially aligned with the compressor hub and located between said compressor hub and the inlet opening to said first compartment, said inducer blades being elongate and of thin cross-section, at least two of said inducer blades being joined to form a common bight portion, said inducer hub being provided with a bore extending parallel to the axis of rotation of the inducer hub and opening to the periphery of the hub, said common bight portion of said pair of inducer blades being seated in the bore with the pair of inducer blades extending through the opening of the bore,
  • a rotor assembly adapted for moving a fluid at high speed comprising a rotor having a hub and a plurality of pairs of flexible blades, each of said pairs of blades having a common bight portion mounted to said rotor hub,
  • said rotor hub having a plurality of spaced bores, each of said bores having a slot opening the bore to the periphery of the rotor hub, one of said pairs of blades extending through the slot opening of each of said bores with the common bight portion thereof seated in said bore, means carried by the hub between each pair of blades having a common bight portionfor maintaining each pair of said blades having acommon bight portion in spaced-apart relation and means for strengthening each of said pairs of blades adjacent the corresponding bore opening of the rotor hub.
  • a rotor assembly adapted for moving a fluid at high speed comprising a rotor having a hub and a plurality of pairs of flexible blades, each of said pairs of blades having a common bight portion mounted to said rotor hub, said rotor hub having a plurality of spaced bores, each of said bores having a slot opening the bore to the periphery of the rotor hub, one of said pairs of blades extending through the slot opening of each of said bores with the common bight portion thereof seated in said bore, means carried by the hub between each pair of blades having a common bight portion for maintaining each pair of said blades having a commonbight portion in spaced-apart relation, said means including a plurality of shoe members carried by the hub, one of said shoe members being disposed between the blades of each of said pairs of blades, and a pin disposed in the space defined by each of said common bight portions for contouring the bight portion and for securing the bight portion in its hub bore
  • each of said shoe members is secured to the corresponding one of said pins.
  • a rotor assembly adapted for moving a fluid at high speed comprising a rotor having a hub and a plurality of pairsof flexible blades, each of said pairs of blades having a common bight portion mounted to said rotor hub, said rotor hub having a plurality of spaced bores, each of said bores having slot opening the bore to the periphery of the rotor hub, one of said pairs of blades extending through the slot opening of each of said bores with the common bight portion thereof seated in said bore, means carried by the hub between each pair of blades having a common bight portion for maintaining each pair of said blades having a common bight portion in spaced-apart relation, said means including a plurality of shoe members carried by the hub, one of said shoe members being disposed between the blades of each pair of said pairs of blades, and means for strengthening each pair of said pairs of blades adjacent the corresponding bore opening of the rotor hub, said strengthening means including a plurality of shoe members carried by the hub,
  • said strengthening means includes a plurality of second wedge members carried by the rotor hub, each of said second wedge members being mounted to the rotor hub in a location between two of said first wedge members and in contact with sides of two blades of two different pairs of said blades, said sides being opposite the sides of said blades contacted by the corresponding first wedge members, said second wedge members cooperating with said first wedge members and said shoe members to hold and strengthen the blades therebetween adjacent the bores of the rotor hub.
  • a rotor assembly adapted for moving a fluid at hub and at least one pair of rotor blades having a common bight portion mounted to said rotor hub, said blades being flexible and formed from a strip of flexible sheet material bent lengthwise 'upon itself at approximately its center to define said common bight portion, said common bight seated in a bore formed in the rotor hub with said pair of blades extending through a slot opening the bore to the periphery of the rotor hub, means at least partially portion being disposed in said slot and carried between said blades for maintaining said blades in spread-apart relation, and means for strengthening the pair of blades adjacent the bore opening of the rotor hub, said strengthening means being located between pairs of blades and between blades of pairs of blades.
  • a rotor assembly adapted for moving a fluid at high speed comprising a rotor hub and at least one pair of rotor blades having a common bight portion mounted to said rotor hub, said blades being flexible and formed from a strip of flexible sheet material bent lengthwise upon itself at approximately its center to define said common bight portion, said common'bight portion being seated in a bore formed in the rotor hub with said pair of blades extending through a slot opening the bore to the periphery of the rotor hub, means at least partially disposed in said slot and carried between said blades for maintaining said blades in spread-apart relation, said means for spreading said blades including a shoe memhas ber disposed between said blades and mounted to said rotor hub for maintaining said pair of blades in spaced apart relation, and means for strengthening the pair of blades adjacent the bore opening of the hub, said means including a first wedge member which is disposed between the blades and which cooperates with the shoe member to maintain the pair of blades in spaced apart relation
  • a rotor assembly adapted for moving a fluid at high speed comprising a rotor hub and at least one pair of rotor blades having a common bight portion mounted to said rotor hub, said blades being flexible and formed from a strip of flexible sheet material bent lengthwise upon itself at approximately its center to define said common bight portion, said common bight portion being seated in a bore formed in the rotor hub with said pair of blades extending through a slot opening the bore to the periphery of the rotor hub, and means at least disposed in said slot and carried between said blades for maintaining said blades in spread-apart relation, said means for spreading said blades including a shoe mem ber disposed between said blades and mounted to said rotor hub for maintaining said pair of blades in spacedapart relation, and a pin in the space defined by the common bight portion for contouring the bight portion and for securing the bight portion in the bore, said shoe member and pin cooperating to hold said pair of blades to said
  • said strengthening means includes a pair of second wedge members carried by the rotor hub on the sides of the blades opposite the sides of the blades contacted by the shoe member, said second wedge members cooperating with said first wedge member and said shoe member to hold the blades 'therebetween adjacent said bore.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Hydrology & Water Resources (AREA)
  • Environmental & Geological Engineering (AREA)
  • Water Supply & Treatment (AREA)
  • Chemical & Material Sciences (AREA)
  • Organic Chemistry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US195118A 1962-05-16 1962-05-16 Compressor arrangement Expired - Lifetime US3202343A (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
NL288322D NL288322A (de) 1962-05-16
US195118A US3202343A (en) 1962-05-16 1962-05-16 Compressor arrangement
GB40285/62A GB1024574A (en) 1962-05-16 1962-10-24 Rotor assemblies for compressors and apparatus including such rotor assemblies
DE19621794308 DE1794308A1 (de) 1962-05-16 1962-11-20 Einrichtung zum Abscheiden eines Loesungsmittels,insbesondere von Suesswasser aus einer Salzwasserloesung
DE19621428074 DE1428074A1 (de) 1962-05-16 1962-11-20 Kompressor fuer Entsalzungssystem
DE19621728495 DE1728495A1 (de) 1962-05-16 1962-11-20 Vorrichtung zur bewegung eines mediums
NL63288322A NL146578B (nl) 1962-05-16 1963-01-30 Compressorrotor.
CH561466A CH434547A (de) 1962-05-16 1963-05-08 Kompressor für eine Einrichtung zur Bewegung von gas- oder dampfförmigen Medien
CH578963A CH421005A (de) 1962-05-16 1963-05-08 Einrichtung zur Bewegung von gas- oder dampfförmigen Medien zwischen zwei Kammern, insbesondere zur Erzeugung von Trinkwasser aus Meerwasser
US415345A US3255514A (en) 1962-05-16 1964-12-02 Method of fabricating rotor assemblies

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US195118A US3202343A (en) 1962-05-16 1962-05-16 Compressor arrangement

Publications (1)

Publication Number Publication Date
US3202343A true US3202343A (en) 1965-08-24

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US195118A Expired - Lifetime US3202343A (en) 1962-05-16 1962-05-16 Compressor arrangement

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US (1) US3202343A (de)
CH (2) CH434547A (de)
DE (1) DE1428074A1 (de)
GB (1) GB1024574A (de)
NL (2) NL146578B (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3860361A (en) * 1972-07-06 1975-01-14 Rolls Royce 1971 Ltd Multi-bladed fans
US3973865A (en) * 1974-02-07 1976-08-10 Siemens Aktiengesellschaft Side-channel ring compressor
WO1982003679A1 (en) * 1981-04-13 1982-10-28 Villadsen Vagn Hovgaard A method and a system for production of loose ice at large capacity
DE3213415A1 (de) * 1981-04-13 1982-10-28 Aktieselskabet Thomas Ths. Sabroe & Co., 8270 Hoejbjerg Verfahren zur verwendung von kaltem wasser als waermeabgebendes medium fuer ein waermepumpensystem sowie system zur durchfuehrung dieses verfahrens
US4547126A (en) * 1983-12-08 1985-10-15 Jackson Samuel G Fan impeller with flexible blades
US4845954A (en) * 1987-06-10 1989-07-11 Stal Refrigeration Ab Method and device for the manufacture of an ice slurry
US5584656A (en) * 1995-06-28 1996-12-17 The Scott Fetzer Company Flexible impeller for a vacuum cleaner
US5642986A (en) * 1995-06-28 1997-07-01 The Scott Fetzer Company Flexible impeller with one-piece hub
US20190162201A1 (en) * 2017-11-24 2019-05-30 Pegatron Corporation Impeller, fan and method for manufacturing fan blade

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006056820A1 (de) * 2006-03-01 2007-09-13 Institut für Luft- und Kältetechnik gGmbH Wasseraufbereitungsanlage

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US1035364A (en) * 1911-12-05 1912-08-13 Ame Pour L Expl Des Procedes Westinghouse Leblanc Soc Elastic-fluid compressor.
US1426954A (en) * 1920-09-02 1922-08-22 Gen Electric Impeller for centrifugal compressors and the like
GB332859A (en) * 1928-11-15 1930-07-31 Siemens Ag Improvements in or relating to centrifugal compressors and pumps
US1880665A (en) * 1930-01-06 1932-10-04 Cinderella Washing Machine Com Combination washing machine and dust collector
US2114780A (en) * 1935-04-15 1938-04-19 Juelson Agnes Suction cleaner
GB662517A (en) * 1948-11-01 1951-12-05 Oerlikon Maschf Inlet guide rotor for radial-flow compressors
US2579583A (en) * 1945-01-29 1951-12-25 Allis Chalmers Mfg Co Segmental blading
US2620554A (en) * 1948-09-29 1952-12-09 Westinghouse Electric Corp Method of manufacturing turbine blades
US2638663A (en) * 1948-10-23 1953-05-19 Thompson Prod Inc Method of making turbine blades
US2652191A (en) * 1942-02-21 1953-09-15 Buchi Alfred Rotor for compressing machines such as centrifugal blowers and pumps
US2656146A (en) * 1948-04-08 1953-10-20 Curtiss Wright Corp Turbine blade construction
US2656973A (en) * 1949-06-09 1953-10-27 Reliance Electric & Eng Co Electric motor for driving a device within a compartment
GB787500A (en) * 1955-05-12 1957-12-11 Rolls Royce Improvements relating to axial flow compressor blading and methods of manufacture thereof
US2889107A (en) * 1955-01-03 1959-06-02 Stalker Corp Fluid rotor construction
CA614971A (en) * 1961-02-21 The British Thomson-Houston Company Limited Blades of axial flow machines

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CA614971A (en) * 1961-02-21 The British Thomson-Houston Company Limited Blades of axial flow machines
BE561554A (de) *
US881409A (en) * 1906-08-28 1908-03-10 Belliss & Morcom Ltd Guide-blade and vane for turbines.
US1035364A (en) * 1911-12-05 1912-08-13 Ame Pour L Expl Des Procedes Westinghouse Leblanc Soc Elastic-fluid compressor.
US1426954A (en) * 1920-09-02 1922-08-22 Gen Electric Impeller for centrifugal compressors and the like
GB332859A (en) * 1928-11-15 1930-07-31 Siemens Ag Improvements in or relating to centrifugal compressors and pumps
US1880665A (en) * 1930-01-06 1932-10-04 Cinderella Washing Machine Com Combination washing machine and dust collector
US2114780A (en) * 1935-04-15 1938-04-19 Juelson Agnes Suction cleaner
US2652191A (en) * 1942-02-21 1953-09-15 Buchi Alfred Rotor for compressing machines such as centrifugal blowers and pumps
US2579583A (en) * 1945-01-29 1951-12-25 Allis Chalmers Mfg Co Segmental blading
US2656146A (en) * 1948-04-08 1953-10-20 Curtiss Wright Corp Turbine blade construction
US2620554A (en) * 1948-09-29 1952-12-09 Westinghouse Electric Corp Method of manufacturing turbine blades
US2638663A (en) * 1948-10-23 1953-05-19 Thompson Prod Inc Method of making turbine blades
GB662517A (en) * 1948-11-01 1951-12-05 Oerlikon Maschf Inlet guide rotor for radial-flow compressors
US2656973A (en) * 1949-06-09 1953-10-27 Reliance Electric & Eng Co Electric motor for driving a device within a compartment
US2889107A (en) * 1955-01-03 1959-06-02 Stalker Corp Fluid rotor construction
GB787500A (en) * 1955-05-12 1957-12-11 Rolls Royce Improvements relating to axial flow compressor blading and methods of manufacture thereof

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3860361A (en) * 1972-07-06 1975-01-14 Rolls Royce 1971 Ltd Multi-bladed fans
US3973865A (en) * 1974-02-07 1976-08-10 Siemens Aktiengesellschaft Side-channel ring compressor
WO1982003679A1 (en) * 1981-04-13 1982-10-28 Villadsen Vagn Hovgaard A method and a system for production of loose ice at large capacity
DE3213415A1 (de) * 1981-04-13 1982-10-28 Aktieselskabet Thomas Ths. Sabroe & Co., 8270 Hoejbjerg Verfahren zur verwendung von kaltem wasser als waermeabgebendes medium fuer ein waermepumpensystem sowie system zur durchfuehrung dieses verfahrens
US4547126A (en) * 1983-12-08 1985-10-15 Jackson Samuel G Fan impeller with flexible blades
US4845954A (en) * 1987-06-10 1989-07-11 Stal Refrigeration Ab Method and device for the manufacture of an ice slurry
US5584656A (en) * 1995-06-28 1996-12-17 The Scott Fetzer Company Flexible impeller for a vacuum cleaner
US5626461A (en) * 1995-06-28 1997-05-06 The Scott Fetzer Company Stranded impeller
US5642986A (en) * 1995-06-28 1997-07-01 The Scott Fetzer Company Flexible impeller with one-piece hub
US5655884A (en) * 1995-06-28 1997-08-12 The Scott Fetzer Company Flexible impeller with overmolded hub
US20190162201A1 (en) * 2017-11-24 2019-05-30 Pegatron Corporation Impeller, fan and method for manufacturing fan blade
US10794393B2 (en) * 2017-11-24 2020-10-06 Pegatron Corporation Impeller, fan and method for manufacturing fan blade

Also Published As

Publication number Publication date
NL288322A (de)
CH421005A (de) 1966-09-15
NL146578B (nl) 1975-07-15
GB1024574A (en) 1966-03-30
DE1428074A1 (de) 1968-11-07
CH434547A (de) 1967-04-30

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