US3289923A - Multi-stage pump - Google Patents

Multi-stage pump Download PDF

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Publication number
US3289923A
US3289923A US407764A US40776464A US3289923A US 3289923 A US3289923 A US 3289923A US 407764 A US407764 A US 407764A US 40776464 A US40776464 A US 40776464A US 3289923 A US3289923 A US 3289923A
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United States
Prior art keywords
impeller
pumping
stage
fluid
diffusing
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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
US407764A
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English (en)
Inventor
William V Millman
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.)
American Air Filter Co Inc
Original Assignee
American Air Filter Co Inc
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 American Air Filter Co Inc filed Critical American Air Filter Co Inc
Priority to US407764A priority Critical patent/US3289923A/en
Priority to GB39786/65A priority patent/GB1126342A/en
Priority to CH1430765A priority patent/CH447460A/fr
Priority to SE13666/65A priority patent/SE312074B/xx
Priority to NL6513964A priority patent/NL6513964A/xx
Priority to DE19651528642 priority patent/DE1528642A1/de
Application granted granted Critical
Publication of US3289923A publication Critical patent/US3289923A/en
Assigned to CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING ASSOCIATION AS TRUSTEE, WOODS KATHLEEN D., AS TRUSTEE reassignment CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING ASSOCIATION AS TRUSTEE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ALLIS-CHALMERS CORPORATION A DE CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/42Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44Fluid-guiding means, e.g. diffusers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06Multi-stage pumps
    • F04D1/063Multi-stage pumps of the vertically split casing type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08Centrifugal pumps
    • F04D17/16Centrifugal pumps for displacing without appreciable compression
    • F04D17/164Multi-stage fans, e.g. for vacuum cleaners
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/40Casings; Connections of working fluid
    • F04D29/42Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4266Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps made of sheet metal

Definitions

  • Many conventional multi-stage compressors are provided with a diffuser arrangement in which'the difiuser channels, with or without vanes, are disposed radially about and in line with the impellers of the pumping stage.
  • the flow in such multi-stage compressors is generally radially outwardly from the impeller, then at a right angle .in a direction axially of the housing, and then inwardly to the inlet of the succeeding pumping stage.
  • the housings for such arrangements are generally concentric about the axis of rotation of the impellers and are of heavy cast construction. Typically, the cast housing includes surfaces which must be machined to close tolerances to provide precision fits.
  • An object of the present invention is to provide a multistage compressor construction which lends itself to fabrication out of relatively inexpensive sheet form material, and which is operable with reasonable efficiency without the requirements of close tolerances or fits in the assembly.
  • Another object is the provision of a low flow-high head centrifugal compressor of multi-stage design of a character which accommodates selecting as many or as few stages as necessary to accomplish the intended result.
  • Another object is the provision of an arrangement in which the well-recognized scroll or volute configuration, known to yield eflicient results in simple centrifugal fans, is incorporated in a multi-stage design to good advantage.
  • each stage of the multi-stage arrangement includes a pumping section formed of an impeller surrounded by a volute, and a successive diffusing section which includes both a diffuser segment and a lead-in segment, with the outlet of the volute of the pumping stage being connected through a gradual and smooth flow transfer zone to the inlet of the diffusion section.
  • a feature of the arrangement is the provision of flow passages in which cross-sectional changes are made gradually, and in which the passages are generally aligned so that as the flow progresses circumferentially and in succession through the volute, transfer duct, diffuser segment and lead-in segment, abrupt changes in flow direction are substantially minimized.
  • a multi-stage compressor may include, for example, a right cylindrical outer casing containing a series of substantially flat, axially spaced walls arranged transverse to the axis of the casing to divide the easing into alternate pumping layers and intermediate diffusing layers.
  • Each pumping layer includes an impeller surrounded by a volute formed by an outwardly spiralling vane and terminating in a peripheral outlet connected through a transfer duct to the peripheral inlet of the succeeding intermediate ditfusing layer.
  • the transfer duct progresses relatively gradually in an axial direction as it progresses substantially farther in a circumferential direction so that it resembles a ramp.
  • Each difiusing layer includes a series of inwardly spiralling vanes defining, in the direction of flow, first a diffusing fer duct wall.
  • the outwardly spiralling vanes of the pumping layers and the inwardly spiralling vanes of the dilfusing layers not only define boundaries of flow passages but also serve as structural members which lend strength to the assembly to withstand the pressures developed.
  • the volute housing arrangement permits a wide range of operating conditions, much like the vaneless diffuser, before encountering a surging point.
  • FIGURE 1 is a partly broken perspective view of a single sandwich incorporating a pumping layer and a diffusing layer and with the impeller for the sandwich exploded;
  • FIGURE 2 is a view of a casing having a series of assembled sandwiches shown in outline form therewithin, and with parts of several sandwiches schematically shown to illustrate the flow path of the fluid;
  • FIGURE 3 is a section of the hub portion of a series of sandwiches in assembled relation
  • FIGURE 4 is a plan view of the pumping layer
  • FIGURE 5 is a plan view of the diffusing layer.
  • FIGURE 1 shows an assembled sandwich 10 with the impeller 11 exploded therefrom.
  • Each sandwich 10 forms one stage of the multi-stage pump as indicated in FIGURE 2, and each is substantially the same in form although successive sandwiches in the direction of flow will normally have progressively less depth, i.e., thickness, depending upon the particular fluid to be handled and the extent to which it is compressible.
  • Each sandwich essentially includes an upstream pumping layer 12 and an underlying and downstream diffusing layer 14 (FIGS. 1 and 2) with the communication between the pumping layer and diffusing layer being through means of the ramp-shaped transfer zone generally designated 16 adjacent the periphery of the sandwich.
  • the communication from the diffusing layer of one sandwich to the pumping layer of the next successive sandwich is through the central opening in the back wall of the diffusing layer.
  • the boundaries between the layers are defined by the disc-shaped plates or walls 18 and 20.
  • the back wall 18 of the pumping layer is substantially flat and is imperforate except for a slightly off center opening 22 which accommodates the hub of the impeller in the manner to be later explained, and a somewhat arcuateshaped opening 24 extending for a short distance along the outer margin of the layer and underlying the trans-
  • An outwardly spiralling vane 26 is disposed with its leading end adjacent the inner edge of the opening 24 for the transfer zone, and gradually progresses circumferentially and radially outwardly to a termination point at the periphery of the layer about three fourths of the way around the circle of the layer.
  • Vane 26 forms the volute providing a generally expanding cross-sectional area between the periphery of the impeller (indicated in FIG. 4 by the broken lines) and the vane. Flow into each pumping layer is through the eye of the impeller. The outlet of each pumping layer coincides with the entrance 28 to the transfer zone 16.
  • the diffusing layers which alternate with the pumping layers, are here so termed because their principal function from a performance standpoint is to provide space for continued diffusion of the fluid before entrance into the next pumping layer.
  • the lead-in function performed by these layers in gradually directing the fluid into the successive pumping layers while avoiding abrupt changes in cross section or obstacles to flow is perhaps equally important.
  • the wall (FIGS. 1, 3, 5) between a diffusing layer and the succeeding pumping layer is more or less disc shaped, and is flat except for the flanged edge on the central outlet opening 30, and the sloping lower ramp wall 32 of the transfer zone.
  • the inlet to the diffusing layer coincides with the outlet of the transfer duct and is generally indicated by the numeral 34 in FIGURE 5.
  • a series of three vanes 36, 38 and 40 are arranged to spiral inwardly to the outlet from circumferentially spaced locations around the periphery of the diffusing layer.
  • the number of vanes used will normally be determined by the diameter of the pump. These vanes stand on edge and are sandwiched between the two walls 18 and 20 when the layers are assembled.
  • the vanes form diffusing passages with the periphery of the layer, and lead-in passages to the outlet for the rest of their length.
  • the first diffusing passage of expanding cross-sectional area is defined between the vane 36 and the periphery of the layer and begins at the outlet of the transfer duct. This first diffusing passage ends where the leading end of the vane 38 is reached.
  • vane 38 is disposed with its leading end spaced radially outwardly from the vane 36 slightly more than half ofithe distance toward the periphery of the layer, and the vanes 36 and 38 run substantially parallel to each other for the remainder of the distance to the outlet of the diffusing layer.
  • the spaces between the vanes are termed lead-in passages and they are of substantially constant cross-sectional area.
  • a second diffusion passage of expanding cross sectional area is formed between the outside surface of the second vane 38 and the periphery of the layer until the leading edge of vane 40 (at the periphery of the layer) is reached. At this point the second lead-in passage of substantially constant cross-sectional area is formed between the vanes 38 and 40 as they progress to the outlet of the diffusing layer.
  • a third diffusing passage is formed between the third vane 40 and the periphery of the diffusing layer until the point where the leading edge of vane 36 is reached.
  • the third lead-in passage of substantially constant cross-sectional area is formed between the vanes 36 and 40. It will thus be apparent that for well over 180 degrees of the circumferential progression of the fluid around the diffusing layer, part of the fluid is moving in expanding crosssectional area passages. The remaining fluid is channelled by the lead-in passages to the outlet of the diffusing layer.
  • Each sandwich is circumscribed by a ring 42 having the same depth as a single sandwich.
  • the width of each ring is indicated in FIGURE 3. While the ring is shown around both FIGURES 4 and 5 for comparison, a single ring is used in the assembly of the two layers.
  • the impeller 11 (FIGS. 1 and 3) for each pumping stage is mounted on the common shaft 44 and includes a hub 46 of generally spool-like shape, a flat, circular back plate 48 affixed securely to the hub, and a series of generally radially extending blades 50 which abut the hub at their inner ends, but terminate short of the periphery of the back plate at their outer ends to provide an annular space 52 at the periphery of the impeller between the back plate 48 and the front plate 54.
  • the front plate has the same outer diameter as the back plate but has a flanged central opening 56 which serves to provide, with the oppositely directed and slightly smaller flanged outlet 30 of the diffusing layer back wall 20, an overlapping seal as is best shown in FIGURE 3.
  • a somewhat better seal more like a labyrinth may be pro vided by the addition of a ring (not shown) diametrically larger than flanged rim 56 of the impeller front plate, and attached to the back of the wall 20 in concentric relation to the rim.
  • hub 46 is provided with a boss 58 on one end face and a correspondingly dimensioned recess 60 on its opposite end so that in assembled form upon the shaft 44 the hubs interfit with each other.
  • Each hub boss may be provided with a set screw for securing the hub to the shaft.
  • FIGURE 2 In the generally outline view of FIGURE 2 a series of sandwiches 10 are shown in assembled relation within the outer cylindrical casing 62 and upon the shaft 44 of motor 64. The order of assembly is first the upstream impeller is locked on the shaft, then the first sandwich, then another impeller, then the next sandwich, and so on. Each sandwich is aligned with the others with all transfer zones being aligned also. An adhesive sealing material is provided between the rim edges of the outer rings 42 and the downstream face peripheral margins of the walls 20 as each of the sandwiches is inserted. Each hub 46 is also locked to the motor shaft 44.
  • the sandwich closest to the motor 64 is the first stage sandwich and is fed centrally through the space between the motor and the upstream wall of the casing. The fluid discharge is out of the central opening 30 of the last stage sandwich as indicated.
  • clamps 66 are provided to bear against the downstream wall 20 of the last diffuser layer.
  • the general flow path of the fluid handled is indicated 'by the arrows in both the broken away parts of FIGURE 2 and in the sectioned portion of FIGURE 3.
  • the hub 46a at the inlet to the casing, and 46b at the outlet are rounded to promote smooth entering and leaving flow.
  • the last diffusing layer may be replaced by a take-01f which receives the discharge from the last pump tangentially rather than through the central outlet.
  • FIGURE 3 it will normally be found preferable when handling compressible fluids to provide sandwich depths which progressively decrease in the direction of fluid flow to accommodate the decreasing volumetric capacity required in successive stages.
  • the decrease is mainly provided by decreasing thickness impellers and pumping layers.
  • the impeller and motor shaft axis does not correspond with the axis of the casing 62.
  • the scroll development for each pumping stage is calculated according to one of the conventional formulas Then the diameter of a circumscribing circle is determined by adding the longest radius of the scroll to the aligned radius. A circle with that diameter corresponds to the inner diameter of the outer ring 42.
  • the center of the circumscribing ring 42 is offset relative to the center of the impeller tothe degree indicated in FIGURES 4 and 5 where the ring center is indicated by numeral 68.
  • the centers are offset from each other about 1 inch.
  • the scroll outline and circle do not 00- incide exactly, but the differences are of an order which may be neglected in the character of construction with which the invention is concerned.
  • fluid handled by the device flows in a continuing circular motion as it moves axially in a substantially shorter distance from inlet to outlet.
  • the rotary motion is imparted to the fluid first by the upstream impeller.
  • the fluid passes around the volute and then through the transfer duct to the diffusion layer.
  • the transfer duct provides a passage which progresses to a substantial degree in a circumferential direction as compared to the slight progression in the axial direction.
  • the fluid is led gradually and smoothly from the pumping layer to the diffusion layer.
  • There the smooth circular flow continues as guided by the vanes to the inlet of the next impeller.
  • a pump according to the described construction combines the features of inexpensive construction, substantial strength, compactness, and reasonable efficiency.
  • the sheet metal approach results in substantially reduced cost as compared to cast, machined and polished parts.
  • the sandwich, and layers with vanes, construction provides adequate strength to the assembly, and results in compactness with little waste space. Except for the final downstream wall of the assembly, the pressure difference on opposite sides of the transverse walls are only those differences between stages, and the cylindrical casing construction provides maximum strength in the radial direction.
  • the efficiency results from taking advantage of the scroll configuration and providing an arrangement in which the angular momentum of the fluid is preserved, both in the layers, and in the transfer zone between layers.
  • a multi-stage pumping device comprising: a right cylindrical outer casing; at least one fluid conducting stage in said casing, each stage including means defining an upstream pumping chamber and a downstream diffusing chamber;
  • each pumping chamber including a fluid impeller c0- operatively mounted for rotation in said pumping chamber, a central fluid inlet disposed to conduct fluid to said impeller and a vane spiralling radially outward about a portion of the periphery of said impeller and forming a volute between said vane and said outer casing, said vane terminating in a generally tangentially directed pumping chamber outlet adjacent the periphery of said impeller;
  • each diffusing chamber having a series of inwardly spiralling vanes disposed to provide first passage of expanding cross section area between one of said vanes and the outer casing of said chamber and then forming passages of uniform cross-sectional area between adjacent vanes, said vanes terminating in an outlet from said diffusing chamber which forms a cooperative intake for the next stage.
  • a multi-stage pumping device comprising:
  • each such stage including means defining an upstream pumping chamber and a downstream diffusing chamber;
  • each pumping chamber including a fluid impeller cooperatively mounted for rotation in said pumping chamber, a central fluid inlet disposed to conduct fluid to said impeller and a vane spiralling radially outwardly about a portion of the periphery of said impeller and forming a volute between said vane and said outer casing, said vane terminating in a generally tangentially directed pumping chamber outlet adjacent the periphery of said impeller;
  • each diffusing chamber having a series of inwardly spiralling vanes disposed to provide first passage of expanding cross-sectional area between one of said vanes and the outer casing of said chambers and then forming passages of uniform cross-sectional area between said vanes, said vanes terminating in an outlet from said diffusion chamber which forms a cooperative intake for the next stage.
  • a multi-stage pump comprising:
  • each pumping chamber including a fluid impeller cooperatively mounted for rotation in said pumping chamber, a central fluid inlet disposed to conduct fluid to said impeller and a vane spiralling radially outward about a portion of the periphery of the said impeller and forming a volute between said vane and said outer casing, said vane terminating in a tangentially directed pumping chamber outlet adjacent the periphery of the said impeller;
  • each diffusing chamber having a series of inwardly spiralling vanes providing first passage of expanding cross-sectional area between one of said vanes and the outer casing of said chamber and then forming passages of uniform cross-sectional area between adjacent said vanes, said vanes terminating in a central outlet from said diffusing chamber which forms a central intake for the next stage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US407764A 1964-10-30 1964-10-30 Multi-stage pump Expired - Lifetime US3289923A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US407764A US3289923A (en) 1964-10-30 1964-10-30 Multi-stage pump
GB39786/65A GB1126342A (en) 1964-10-30 1965-09-17 Multi-stage pumps and compressors
CH1430765A CH447460A (fr) 1964-10-30 1965-10-18 Pompe ou compresseur
SE13666/65A SE312074B (fr) 1964-10-30 1965-10-22
NL6513964A NL6513964A (fr) 1964-10-30 1965-10-28
DE19651528642 DE1528642A1 (de) 1964-10-30 1965-10-29 Mehrstufige Pumpe oder mehrstufiger Kompressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US407764A US3289923A (en) 1964-10-30 1964-10-30 Multi-stage pump

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US3289923A true US3289923A (en) 1966-12-06

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Application Number Title Priority Date Filing Date
US407764A Expired - Lifetime US3289923A (en) 1964-10-30 1964-10-30 Multi-stage pump

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US (1) US3289923A (fr)
CH (1) CH447460A (fr)
DE (1) DE1528642A1 (fr)
GB (1) GB1126342A (fr)
NL (1) NL6513964A (fr)
SE (1) SE312074B (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3986791A (en) * 1974-04-01 1976-10-19 Sigma Lutin, Narodni Podnik Hydrodynamic multi-stage pump
US4637779A (en) * 1985-05-17 1987-01-20 Kamyr, Inc. Two stage medium consistency pulp pumping
WO1989012753A1 (fr) * 1987-06-29 1989-12-28 Denis Toth Turbocompresseur a etages multiples
US5040946A (en) * 1989-07-05 1991-08-20 Ebara Corporation Case, particularly for centrifugal radial pumps, and method for manufacturing thereof
FR2676511A1 (fr) * 1991-05-15 1992-11-20 Bosch Gmbh Robert Machine soufflante radiale comportant un rotor de soufflante tournant dans un carter en spirale comme air secondaire a la veine de gaz d'echappement d'un moteur a combustion interne, notamment d'automobile.
EP1193399A2 (fr) * 2000-09-28 2002-04-03 PAPST-MOTOREN GmbH & Co. KG Ventilateur radial, en particulier pour respirateur
US20100232951A1 (en) * 2009-03-10 2010-09-16 Grundfos Management A/S Multi-stage centrifugal pump assembly (bearing carrier)
US9574562B2 (en) 2013-08-07 2017-02-21 General Electric Company System and apparatus for pumping a multiphase fluid

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9303161U1 (de) * 1993-03-04 1994-07-14 Robert Bosch Gmbh, 70469 Stuttgart Elektromotorisch betriebenes Gebläse
DE102019001882A1 (de) * 2019-03-19 2020-09-24 KSB SE & Co. KGaA Mantelgehäusepumpe und Herstellungsverfahren für eine Mantelgehäusepumpe
CN114688046B (zh) * 2020-12-25 2023-03-03 广东美的白色家电技术创新中心有限公司 风机组件和吸尘器

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE131076C (fr) *
US1247064A (en) * 1914-09-11 1917-11-20 B F Sturtevant Co Multistage blower for pneumatic cleaners.
CH103721A (de) * 1923-02-23 1924-03-01 Oerlikon Maschf Kreiselgebläse.
US1522655A (en) * 1925-01-13 Ginia
GB228365A (en) * 1924-02-26 1925-02-05 British Electric Plant Company Improvements in or relating to centrifugal pumps
US2578617A (en) * 1946-11-15 1951-12-11 Worthington Pump & Mach Corp Multistage centrifugal compressor
DE906894C (de) * 1941-10-16 1956-08-09 Siemen & Hinsch Gmbh Leitrad fuer Kreiselpumpen
US2978989A (en) * 1957-01-10 1961-04-11 Tait Mfg Co The Pumps
US3226085A (en) * 1962-10-01 1965-12-28 Bachl Herbert Rotary turbine
US3243102A (en) * 1963-12-20 1966-03-29 Kenton D Mcmahan Centrifugal fluid pump

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE131076C (fr) *
US1522655A (en) * 1925-01-13 Ginia
US1247064A (en) * 1914-09-11 1917-11-20 B F Sturtevant Co Multistage blower for pneumatic cleaners.
CH103721A (de) * 1923-02-23 1924-03-01 Oerlikon Maschf Kreiselgebläse.
GB228365A (en) * 1924-02-26 1925-02-05 British Electric Plant Company Improvements in or relating to centrifugal pumps
DE906894C (de) * 1941-10-16 1956-08-09 Siemen & Hinsch Gmbh Leitrad fuer Kreiselpumpen
US2578617A (en) * 1946-11-15 1951-12-11 Worthington Pump & Mach Corp Multistage centrifugal compressor
US2978989A (en) * 1957-01-10 1961-04-11 Tait Mfg Co The Pumps
US3226085A (en) * 1962-10-01 1965-12-28 Bachl Herbert Rotary turbine
US3243102A (en) * 1963-12-20 1966-03-29 Kenton D Mcmahan Centrifugal fluid pump

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3986791A (en) * 1974-04-01 1976-10-19 Sigma Lutin, Narodni Podnik Hydrodynamic multi-stage pump
US4637779A (en) * 1985-05-17 1987-01-20 Kamyr, Inc. Two stage medium consistency pulp pumping
WO1989012753A1 (fr) * 1987-06-29 1989-12-28 Denis Toth Turbocompresseur a etages multiples
US4925368A (en) * 1987-06-29 1990-05-15 Can-Am Engineered Products, Inc. Turbo-compressor having air-cooled bearing
US5040946A (en) * 1989-07-05 1991-08-20 Ebara Corporation Case, particularly for centrifugal radial pumps, and method for manufacturing thereof
FR2676511A1 (fr) * 1991-05-15 1992-11-20 Bosch Gmbh Robert Machine soufflante radiale comportant un rotor de soufflante tournant dans un carter en spirale comme air secondaire a la veine de gaz d'echappement d'un moteur a combustion interne, notamment d'automobile.
US5286164A (en) * 1991-05-15 1994-02-15 Robert Bosch Gmbh Radial blower with blower wheel rotating in spiral housing
EP1193399A2 (fr) * 2000-09-28 2002-04-03 PAPST-MOTOREN GmbH & Co. KG Ventilateur radial, en particulier pour respirateur
EP1193399A3 (fr) * 2000-09-28 2003-04-23 PAPST-MOTOREN GmbH & Co. KG Ventilateur radial, en particulier pour respirateur
US20100232951A1 (en) * 2009-03-10 2010-09-16 Grundfos Management A/S Multi-stage centrifugal pump assembly (bearing carrier)
US8568093B2 (en) * 2009-03-10 2013-10-29 Grundfos Management A/S Multi-stage centrifugal pump assembly (bearing carrier)
US9574562B2 (en) 2013-08-07 2017-02-21 General Electric Company System and apparatus for pumping a multiphase fluid

Also Published As

Publication number Publication date
CH447460A (fr) 1967-11-30
NL6513964A (fr) 1966-05-02
DE1528642A1 (de) 1969-05-14
SE312074B (fr) 1969-06-30
GB1126342A (en) 1968-09-05

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AS Assignment

Owner name: CONNECTICUT NATIONAL BANK THE, A NATIONAL BANKING

Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001

Effective date: 19830329

Owner name: WOODS KATHLEEN D., AS TRUSTEE

Free format text: SECURITY INTEREST;ASSIGNOR:ALLIS-CHALMERS CORPORATION A DE CORP.;REEL/FRAME:004149/0001

Effective date: 19830329