US3790309A - Unitary pump-motor assembly - Google Patents

Unitary pump-motor assembly Download PDF

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Publication number
US3790309A
US3790309A US00175225A US3790309DA US3790309A US 3790309 A US3790309 A US 3790309A US 00175225 A US00175225 A US 00175225A US 3790309D A US3790309D A US 3790309DA US 3790309 A US3790309 A US 3790309A
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US
United States
Prior art keywords
pump
motor
fluid
assembly according
housing
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
Application number
US00175225A
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English (en)
Inventor
H Volz
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.)
Allweiler GmbH
Original Assignee
Allweiler AG
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 claimed from DE19702044295 external-priority patent/DE2044295A1/de
Priority claimed from DE19702044335 external-priority patent/DE2044335C3/de
Application filed by Allweiler AG filed Critical Allweiler AG
Application granted granted Critical
Publication of US3790309A publication Critical patent/US3790309A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F04C2/165—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type having more than two rotary pistons with parallel axes
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • H02K5/132—Submersible electric motors

Definitions

  • ABSTRACT A houslng encloslng a motor and a pump havmg a 1561 CM 33131;; 3.51? 11151 1121112135 ZIIE QEJKLFZ 21501518; UNITED STATES PATENTS a secondary flow of liquid forced through the motor 3,146,605 9/1964 Rachfal et a1 417/366 helical passages o imilar arrangements to there- 3,618,337 11/1971 Mount 417/366 x after Sweep the heat generating Surfaces of the moton 3,514,225 5/1970 Tune Monden 417/410 X 2,460,371 2/1949 Szwargulski 417/369 13 Claims, 4 Drawing Figures 1 25 1 27 '2 H /7 37 I4 1 4 11 I Z PATENTED FEB 1974 sum 1 OF 3 INVENTOR.
  • This invention relates generally to a seal-free pump and electric motor assembly, with the motor arranged in the suction or pressure chamber of the device and completely immersed in the fluid flow.
  • the electric motor is arranged in the flow of the liquid fluid, with the total volume of liquid delivered by the pump being passed through the electric motor in order to dissipate the heatgenerated in the stator windings and in the rotor of the motor.
  • This mode of construction has the disadvantage that the insulation on the stator windings is subject to heavy erosion. Moreover, it causes a considerable loss in pressure as the entire volume of liquid passes through the motor and, in order to intensify the cooling, the cross section of the fluid flow area must be kept relatively small, so that there are no areas that are not affected by the fluid flow,
  • the motor is located out of the direct path of the flow of liquid.
  • the stator windings are cooled by means of a secondary flow obtained by providing a plurality of choke passages connecting the pressure chamber with the suction chamber.
  • This secondary flow obtained by choking causes a reduction in the efficiency of the pump which is particularlysignificant when the output of the motor is high, as in this case a large secondary flow is required to dissipate the heat.
  • Pumps of the type provided with helical displacement elements can also have the motor separated from the pump.
  • the pump and the motor are structurally adapted for each other and form technically a functional unit, although there is a structural separation between the pump and the motor.
  • the pump is designed as an independent part, having a special pressure chamber connected to the motor by an aperture; and the helical shafts are mounted in the pump housing independent of the motor mounting and are provided with means for equalizing axial thrust.
  • the motor shaft is secured to the pump shaft.
  • the motor shaft is journalled in one pump bearing at one end and, at the other,-is supported by a bearing arranged in the motor cove plate.
  • the auxiliary arrangement is provided in such a manner that the secondary flow of liquid is just sufficient to dissipate the heat produced by the motor.
  • the device requires little power, since it has to overcome only the internal resistance of the'motor, which is much less than when the whole flow is passed through the motor.
  • the auxiliary arrangement can' be of one or more configurations.
  • the arrangement consists of one or more helical grooves formed in the rotor or in the internal surface of the stator.
  • An arrangement of this kind is particularly suitable when the liquids passing through the pump are of high viscosity.
  • the helical grooves act as a simple helical pump producing a secondary flow through the motor according to the direction of rotation and the direction of the pitch.
  • the auxiliary fluid flow arrangement consists of at least one conduit arranged in the rotor, .the distance between the conduit and the rotor. increasing along the length of the rotor.
  • the conduit acts as a sling wheel with the liquid emerging from that side of the rotor where the distance between the conduitand the axis is the greatest.
  • the auxiliary fluid arrangement consists of a rotor and stator, both of coni- I cal configuration.
  • the fluid flow is produced by the liquid moving from the smaller to the larger diameter under centrifugal forceln order to improve the delivery action, one or more helical grooves may be arranged in the conical rotor of the conical stator.
  • theprovision for the auxiliary fluid flow may also consist of axial or radial pump impellers fitted to the motor shaft. This is particularly suitable when the pump unit is used for low-viscosity liquids. Since large motors usually carry balancing discs on their shafts, the invention also provides for the impellers to be formed on these discs.
  • the pump using a helical displacement element, to arrange the pump .and the motor in a common housing.
  • the motor being located in the pressure chamber, and the drive and impeller shafts leading directly into the pressure chamber.
  • the motor shaft and the drive shaft comprising a rigid shaft, one end of which is mounted in the drive-shaft bore in the pump housing and the other end in the motor cover plate.
  • This arrangement produces a simplified and economical construction, since the pump bearing at the motor end is eliminated.
  • the design also has the advantage that the mounting is statically determinate, which results in a very smooth operation. The latter is particularly significant as these pump units are frequently used to operate hydraulic elevators in residential buildings.
  • the units can be made considerably shorter, as the absence of a bearing at the motor end does away with the need for a pump cover at the motor end. r
  • the bearing in the cover plate at the motor end is in the form of a fixed bearing arranged in an area separate from the pressure chamber and not under pressure, and when the passage of the shaft from the pressure chamber to the chamber not under pressure is such that the axial forces acting upon the shaft are equalized, the pump itself requires no means for equalizing the axial thrust or for locating the drive shaft.
  • the cover plate at the motor end is a relatively simple part, so that the production costs can be minimized.
  • an apparatus for pumping a fluid which comprises a housing provided with a pressure and a suction chamber and in which a fluid inlet in the housing hasa passageway to the suction'chamber.
  • a fluid outlet is located in the housing with a passageway extending to the pressure chamber.
  • a pump is located within the suction chamber of the housing for transferring the fluid from the inlet to the outlet.
  • a motor is provided having a stator and rotor within the housing at a location essentially out of the path of the fluid passing from the fluid inlet to the fluid outlet. The pump and themotor are speced relative to each other and the outlet passageway is located, generally, therebetween.
  • the outlet passageway originates in the pressure chamber of thehousing as compared to the pre-pumping area or suction chamber.
  • a passageway for passing cooling fluids therethrough with the passageways encompassing most of the outside surfaces of the motor.
  • the apparatus includes auxiliary flow producing means disposed within the pressure chamber to the axial end of the motor which is closest to the fluid outlet with the flow producing means being effective to force and divert a comparatively small portion of the fluid which has passed the pump and is'within the pressure chamber into the cooling passageways and thereafter into the passageway of the outlet without returning the fluid to the pump or the suction chamber.
  • FIG. 2 is a cross sectional view through the pumpmotor unit, shown in FIG. 1, taken along the line A-A thereof;
  • FIGS. 3 and 4 show modifications of the pump-motor unit shown in FIG. 1.
  • FIGS. 1 and 2 there is shown a housing 1 enclosing an electric motor 2 and a pump 3.
  • the housing 1 is formed as one unitary member and contains a suction chamber 4 and a pressure chamber 5, and is closed on the suction end by a housing cover 6 and at the motor end by a cover 7.
  • the pump 3 comprises a helical drive shaft 8 and parallel arranged helical idler shafts 9,10, in meshing engagement with shaft 8.
  • the shafts 8,9 and 10 are coaxially surrounded by a pump housing sleeve ll fitted to the housing 1.
  • the motor 2 comprises a'stator 13 with windings l2 and a rotor 15 fitted to a motor shaft 14 extending centrally through housing 1. Also arranged'on the motor shaft, at'opposite ends of the motor windings 12 are balancing discs 16,17.
  • the drive shaft 8 and the motor shaft 14 are formed into one rigid shaft by a shrink-fit connection'18, one end ofthe shaft being journalled in a ball bearing 19 in cover 7 while the other end is mounted in opening 20in pump housing sleeve 11 for drive shaft 8.
  • the ball bearing 19 is secured in a space 21 provided in cover 7.
  • the pump idler shafts 9,10 are provided on the suction side with cylindrical shaft collars 28,29 which axially bear against inner face 31 of housing cover 6 and, at the opposite end face, provide a supporting surface for the suction end 30 of shaft 8. This absorbs the axial hydraulic forces acting from pressure chamber 5 to suction chamber 4, and the axial forces produced by the helical teeth and acting from suction chamber 4 to pressure chamber 5.
  • the shafts 9,10 are mounted radially in bores 32,33 in pump housing 11, see FIG. 2..In pressure chamber 5, the end faces of the shafts are in approximate alignment with end-face 34 of pump housing 11, and therefore take up no room in pressure chamber 5.
  • the latter has a fluid outlet opening 35 located between the motor and the pump. Thus the liquid flowing out of the pump does not pass through the motor.
  • the rotor is provided with an auxiliary fluid flow arrangement comprising a plurality of helical grooves 36, producing a secondary flow in the direction of arrows 37.
  • the said stator is held in housing 1 by means of narrow, axially extending, ribs 38.
  • the pump housing 11 can be formed integral with housing 1, and conversely the housing 1 can be composed of a plurality of individual parts.
  • the pump-motor assembly shown in FIG. 3 corresponds substantially to the device shown in FIG. 1, except for a modified auxiliary fluid flow arrangement.
  • rotor 39 is of conical construction and is surrounded by a complementary conical stator 40. Due to the variation in the peripheral velocities of the rotor, when the latter rotates, a secondary fluid flow is produced which flows around the motor as indicated by arrows 41.
  • the approach comprises wheels 42,43 secured to motor shaft 14 by means of balancing discs 16,17.
  • the circumference of the wheels is provided with little buckets or propeller-like parts which in the case of wheel 43 causes the liquid to be conveyed axially from the pump side to the motor side, as indicated by the appropriate arrow 44.
  • the buckets of the wheel 42, formed on the circumference of disc 16 are formed as radially extending straight ribs. The ribs cause the movement of the liquid to accelerate in a radial direction and thus is caused to flow around stator 2.
  • passages 45 are arranged in the rotor, but have no delivery function.
  • the pump wheels 42,43 may be omitted if, as is shown in one half of the rotor, at least one duct 46 is provided in the rotor, the distance between the duct 46 and rotor axis 47 increasing along the length of the rotor, thereby producing-a flow through the motor.
  • Apparatus for pumping a fluid comprising:
  • a pump within the suction chamber of said housing for transferring the fluid from the fluid inlet to the fluid outlet;
  • said pump and motor being spaced relative to each other and the outlet passageway being located generally therebetween;
  • a pump-motor assembly according to claim 1, wherein said motor includes a drive shaft and said fluid flow means comprises a radial or axial pump wheel arranged on said drive shaft.
  • a pump-motor assembly according to claim 4 and a balancing disc interposed between said drive shaft and said pump wheel.
  • a pump-motor assembly according to claim 1, wherein said fluid flow means comprises a longitudinally extending passage in said motor whose distance from the motor axis increases in one axial direction.
  • a pump-motor assembly according to claim 1, wherein said pump comprises helical fluid displacement elements, and said motor is located in or proximate to said pressure chamber; and a common drive shaft for said pump and motor.
  • a pump-motor assembly according to claim 10 and a bearing for supporting said common drive shaft arranged spaced from said pressure chamber in a housing location effective to equalize the axial forces acting upon the motor shaft and the pump shaft portions.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00175225A 1970-09-08 1971-08-26 Unitary pump-motor assembly Expired - Lifetime US3790309A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19702044295 DE2044295A1 (de) 1970-09-08 1970-09-08 Stopfbuchsloses Pumpenaggregat
DE19702044335 DE2044335C3 (de) 1970-09-08 Stopfbuchsenloses Motorpumpenaggregat

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US3790309A true US3790309A (en) 1974-02-05

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US00175225A Expired - Lifetime US3790309A (en) 1970-09-08 1971-08-26 Unitary pump-motor assembly

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CH (1) CH525392A (de)

Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3922114A (en) * 1974-07-19 1975-11-25 Dunham Bush Inc Hermetic rotary helical screw compressor with improved oil management
US4198191A (en) * 1978-04-07 1980-04-15 General Electric Company Vaporization cooled dielectric fluid pump
US4207033A (en) * 1976-12-06 1980-06-10 Trw Inc. Pump and motor assembly for use in regulating a flow of fuel from a source of fuel to an operating chamber of an engine of a vehicle
US4547135A (en) * 1982-12-11 1985-10-15 ALLWEILER AG Aktiengesellschaft Motor-pump unit
US4747757A (en) * 1986-11-26 1988-05-31 Haentjens Walter D Submersible mixing pump
US5007808A (en) * 1989-12-15 1991-04-16 Carrier Corporation Slotted rotor lubrication system
US5044896A (en) * 1988-10-31 1991-09-03 Wilo-Werk Gmbh & Co. Pumpen - Und Apparatebau Split tube centrifugal pump
US5118466A (en) * 1990-03-12 1992-06-02 Westinghouse Electric Corp. Nuclear reactor coolant pump with internal self-cooling arrangement
DE4234429A1 (de) * 1992-10-13 1994-04-14 Rexroth Mannesmann Gmbh Motor-Pumpen-Einheit
US5873710A (en) * 1997-01-27 1999-02-23 Copeland Corporation Motor spacer for hermetic motor-compressor
US6183213B1 (en) 1999-03-17 2001-02-06 Visteon Global Technologies, Inc. Hydraulic gear pump power pack for a power steering system with separate flow paths for fluid noise reduction
US6257364B1 (en) 2000-01-20 2001-07-10 Ford Global Technologies, Inc. Submersible electro-hydraulic powerpack for underhood automotive steering applications
US6305919B1 (en) 1999-08-24 2001-10-23 Visteon Global Technologies, Inc. Hydraulic pump housing with an integral dampener chamber
US6309187B1 (en) 1999-03-17 2001-10-30 Visteon Global Technologies, Inc. Hydraulic gear pump power pack for a power steering system with an integral pressure wave attenuator for fluid noise reduction
WO2001094786A1 (en) * 2000-06-08 2001-12-13 Powercell Corporation Submersible electrolyte circulation system
US20020170778A1 (en) * 2001-05-18 2002-11-21 Lg Electronics Inc. Oil supply apparatus for hermetic compressor
US6499966B1 (en) * 1998-08-06 2002-12-31 Automative Motion Technology, Ltd. Motor driven pump
US6634870B2 (en) 2002-01-03 2003-10-21 Tecumseh Products Company Hermetic compressor having improved motor cooling
US20030202891A1 (en) * 2002-04-24 2003-10-30 Masao Nakano Refrigerant pump
US20040091373A1 (en) * 2001-03-13 2004-05-13 Terry Sean Roderick Pump
GB2401396A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump assembly
US20040228744A1 (en) * 2003-05-14 2004-11-18 Matsushita Elec. Ind. Co. Ltd. Refrigerant pump
US20040241016A1 (en) * 2003-05-08 2004-12-02 Beaven Robert William Pump assembly
US20050082941A1 (en) * 2003-10-17 2005-04-21 Toyota Jidosha Kabushiki Kaisha Turbocharger with rotating electric machine
US20050175479A1 (en) * 2004-02-06 2005-08-11 Sauer-Danfoss Inc. Electro-hydraulic power unit with a rotary cam hydraulic power unit
US20060140787A1 (en) * 2004-11-23 2006-06-29 Wolfgang Amrhein Hydraulic assembly
US20090285702A1 (en) * 2005-12-28 2009-11-19 Daikin Industries, Ltd. Compressor
US20100181128A1 (en) * 2009-01-21 2010-07-22 Michael George Field Cyclonic motor cooling for material handling vehicles
US20100239441A1 (en) * 2007-05-09 2010-09-23 Siemens Aktiengesellschaft Compressor system for underwater use in the offshore area
US8668467B2 (en) 2009-07-16 2014-03-11 Parker Hannifin Corporation Integrated fluid handling apparatus
US20150030491A1 (en) * 2012-02-28 2015-01-29 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
US20150200577A1 (en) * 2014-01-16 2015-07-16 Man Truck & Bus Ag Electric machine for a vehicle, in particular for a utility vehicle, and method for protection against ingress of water
US20160053770A1 (en) * 2014-08-22 2016-02-25 Nidec Corporation Dynamic pressure bearing pump
US10197058B2 (en) 2012-02-28 2019-02-05 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US20190063438A1 (en) * 2016-03-08 2019-02-28 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Screw compressor
US11015602B2 (en) 2012-02-28 2021-05-25 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
EP3967882A1 (de) * 2020-09-09 2022-03-16 METELLI S.p.A. Mehrschneckenpumpe für kühlkreisläufe
US11293390B2 (en) * 2020-05-25 2022-04-05 Hyundai Motor Company Fuel pump for a liquid fuel injection system of a motor vehicle
US20230184248A1 (en) * 2021-12-14 2023-06-15 Leistritz Pumpen Gmbh Screw spindle pump

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US1631592A (en) * 1926-09-01 1927-06-07 Hill Compressor & Pump Company Rotary pumping machine
US2225338A (en) * 1937-05-13 1940-12-17 Gen Electric Immersion pump arrangement
US2394517A (en) * 1943-02-16 1946-02-05 Singer Mfg Co Cooling means for dynamoelectric machines
US2460371A (en) * 1947-03-31 1949-02-01 Carter Carburetor Corp Motor cooling means
US2583583A (en) * 1948-10-20 1952-01-29 John R Mangan Compressor pump
US2924181A (en) * 1957-05-13 1960-02-09 Laval Steam Turbine Co Screw pumps or motors
GB834689A (en) * 1957-06-03 1960-05-11 Lucas Industries Ltd Rotary fuel pumps
US2969908A (en) * 1953-04-27 1961-01-31 Garrett Corp Impulse axial-flow compressor
CA687495A (en) * 1964-05-26 Fostoria Corporation Motor driven pumps
US3146605A (en) * 1961-06-02 1964-09-01 Carrier Corp Apparatus for cooling a refrigeration system motor
US3247580A (en) * 1962-05-09 1966-04-26 Laval Turbine Method of making screw pumps
US3263619A (en) * 1965-10-04 1966-08-02 Laval Turbine Motor-pump unit
US3514225A (en) * 1967-06-21 1970-05-26 Tokyo Shibaura Electric Co Motor driven compressors for refrigerating machines
US3597133A (en) * 1969-01-15 1971-08-03 Allweiler Ag Screw pump with thrust absorber
US3618337A (en) * 1970-06-22 1971-11-09 Carrier Corp Hermetic refrigeration compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA687495A (en) * 1964-05-26 Fostoria Corporation Motor driven pumps
US1631592A (en) * 1926-09-01 1927-06-07 Hill Compressor & Pump Company Rotary pumping machine
US2225338A (en) * 1937-05-13 1940-12-17 Gen Electric Immersion pump arrangement
US2394517A (en) * 1943-02-16 1946-02-05 Singer Mfg Co Cooling means for dynamoelectric machines
US2460371A (en) * 1947-03-31 1949-02-01 Carter Carburetor Corp Motor cooling means
US2583583A (en) * 1948-10-20 1952-01-29 John R Mangan Compressor pump
US2969908A (en) * 1953-04-27 1961-01-31 Garrett Corp Impulse axial-flow compressor
US2924181A (en) * 1957-05-13 1960-02-09 Laval Steam Turbine Co Screw pumps or motors
GB834689A (en) * 1957-06-03 1960-05-11 Lucas Industries Ltd Rotary fuel pumps
US3146605A (en) * 1961-06-02 1964-09-01 Carrier Corp Apparatus for cooling a refrigeration system motor
US3247580A (en) * 1962-05-09 1966-04-26 Laval Turbine Method of making screw pumps
US3263619A (en) * 1965-10-04 1966-08-02 Laval Turbine Motor-pump unit
US3514225A (en) * 1967-06-21 1970-05-26 Tokyo Shibaura Electric Co Motor driven compressors for refrigerating machines
US3597133A (en) * 1969-01-15 1971-08-03 Allweiler Ag Screw pump with thrust absorber
US3618337A (en) * 1970-06-22 1971-11-09 Carrier Corp Hermetic refrigeration compressor

Cited By (59)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2529317A1 (de) * 1974-07-19 1976-04-01 Dunham Bush Inc Schraubenkompressor
US3922114A (en) * 1974-07-19 1975-11-25 Dunham Bush Inc Hermetic rotary helical screw compressor with improved oil management
US4207033A (en) * 1976-12-06 1980-06-10 Trw Inc. Pump and motor assembly for use in regulating a flow of fuel from a source of fuel to an operating chamber of an engine of a vehicle
US4198191A (en) * 1978-04-07 1980-04-15 General Electric Company Vaporization cooled dielectric fluid pump
US4547135A (en) * 1982-12-11 1985-10-15 ALLWEILER AG Aktiengesellschaft Motor-pump unit
US4747757A (en) * 1986-11-26 1988-05-31 Haentjens Walter D Submersible mixing pump
US5044896A (en) * 1988-10-31 1991-09-03 Wilo-Werk Gmbh & Co. Pumpen - Und Apparatebau Split tube centrifugal pump
US5007808A (en) * 1989-12-15 1991-04-16 Carrier Corporation Slotted rotor lubrication system
US5118466A (en) * 1990-03-12 1992-06-02 Westinghouse Electric Corp. Nuclear reactor coolant pump with internal self-cooling arrangement
DE4234429A1 (de) * 1992-10-13 1994-04-14 Rexroth Mannesmann Gmbh Motor-Pumpen-Einheit
US5873710A (en) * 1997-01-27 1999-02-23 Copeland Corporation Motor spacer for hermetic motor-compressor
US6499966B1 (en) * 1998-08-06 2002-12-31 Automative Motion Technology, Ltd. Motor driven pump
US6309187B1 (en) 1999-03-17 2001-10-30 Visteon Global Technologies, Inc. Hydraulic gear pump power pack for a power steering system with an integral pressure wave attenuator for fluid noise reduction
US6183213B1 (en) 1999-03-17 2001-02-06 Visteon Global Technologies, Inc. Hydraulic gear pump power pack for a power steering system with separate flow paths for fluid noise reduction
US6305919B1 (en) 1999-08-24 2001-10-23 Visteon Global Technologies, Inc. Hydraulic pump housing with an integral dampener chamber
US6257364B1 (en) 2000-01-20 2001-07-10 Ford Global Technologies, Inc. Submersible electro-hydraulic powerpack for underhood automotive steering applications
WO2001094786A1 (en) * 2000-06-08 2001-12-13 Powercell Corporation Submersible electrolyte circulation system
US20040091373A1 (en) * 2001-03-13 2004-05-13 Terry Sean Roderick Pump
US7347674B2 (en) * 2001-03-13 2008-03-25 Davey Products Pty Ltd Pump
US6866123B2 (en) * 2001-05-18 2005-03-15 Lg Electronics Inc. Oil supply apparatus for hermetic compressor
US20020170778A1 (en) * 2001-05-18 2002-11-21 Lg Electronics Inc. Oil supply apparatus for hermetic compressor
US6634870B2 (en) 2002-01-03 2003-10-21 Tecumseh Products Company Hermetic compressor having improved motor cooling
US20030202891A1 (en) * 2002-04-24 2003-10-30 Masao Nakano Refrigerant pump
US7040875B2 (en) * 2002-04-24 2006-05-09 Matsushita Electric Industrial Co., Ltd. Refrigerant pump with rotors in bearing
US20040241016A1 (en) * 2003-05-08 2004-12-02 Beaven Robert William Pump assembly
GB2401396A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump assembly
US7052230B2 (en) 2003-05-08 2006-05-30 Automotive Motion Technology Limited Pump assembly
US20040228744A1 (en) * 2003-05-14 2004-11-18 Matsushita Elec. Ind. Co. Ltd. Refrigerant pump
US6943468B2 (en) * 2003-10-17 2005-09-13 Toyota Jidosha Kabushiki Kaisha Turbocharger with rotating electric machine
US20050280325A1 (en) * 2003-10-17 2005-12-22 Toyota Jidosha Kabushiki Kaisha Turbocharger with rotating electric machine
US7071585B2 (en) 2003-10-17 2006-07-04 Toyota Jidosha Kabushiki Kaisha Turbocharger with rotating electric machine
US20050082941A1 (en) * 2003-10-17 2005-04-21 Toyota Jidosha Kabushiki Kaisha Turbocharger with rotating electric machine
US20050175479A1 (en) * 2004-02-06 2005-08-11 Sauer-Danfoss Inc. Electro-hydraulic power unit with a rotary cam hydraulic power unit
US7182583B2 (en) * 2004-02-06 2007-02-27 Sauer-Danfoss Inc. Electro-hydraulic power unit with a rotary cam hydraulic power unit
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