US3870438A - Pump - Google Patents

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Publication number
US3870438A
US3870438A US361048A US36104873A US3870438A US 3870438 A US3870438 A US 3870438A US 361048 A US361048 A US 361048A US 36104873 A US36104873 A US 36104873A US 3870438 A US3870438 A US 3870438A
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US
United States
Prior art keywords
hollow shaft
housing
rotor
sleeve
combination according
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
US361048A
Other languages
English (en)
Inventor
Paul Dannenmann
Gunter Kratz
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.)
G Bauknecht GmbH
G Bauknecht Elektrotechnische Fabriken GmbH
Original Assignee
G Bauknecht GmbH
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 DE19722224213 external-priority patent/DE2224213B1/de
Priority claimed from DE19732323089 external-priority patent/DE2323089A1/de
Application filed by G Bauknecht GmbH filed Critical G Bauknecht GmbH
Application granted granted Critical
Publication of US3870438A publication Critical patent/US3870438A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0646—Units comprising pumps and their driving means the pump being electrically driven the hollow pump or motor shaft being the conduit for the working fluid

Definitions

  • a sealing sleeve in the housing seals between the stator and the rotor-impeller structure while fluid inlet and outlet ports in opposite ends of the housing communicate with opposite ends ofthe sleeve.
  • a hollow shaft carried by the housing at the inlet end extends into the rotor and rotatably supports the rotor while conveying fluid from the fluid inlet port of the housing to the inlet side of the impeller.
  • the outlet side of the impeller communicates with the fluid outlet port of the housing.
  • the present invention concerns a pump with a collimator stator sleeve motor pump unit which is coaxially arranged with regard to the pump rotor and has a common housing with the pump.
  • the rotor of the collimator stator sleeve motor pump unit is sealed relative to the stator by means of a collimator which is arranged between the rotor of the stator sleeve motor pump unit and the stator and has its ends resting in the interior of the housing by means of annular flanges.
  • the pump rotor and the rotor of the collimator stator sleeve motor pump unit are mounted on a hollow shaft which is arranged in the housing and which is in communication with the suction opening and the pressure opening of the housing which has a cover at least at one of its end faces.
  • the hollow shaft is designed as a separate structural element and is connected by supporting walls to the collimator which is arranged at a relatively great distance from the mantle of the hollow shaft.
  • the supporting walls are at both sides by means of a housing cover on each end face of the housing fixed with regard to the ends of the collimator and with regard to a central housing part.
  • an object of the present invention to provide a pump of the above described general character which will have a simplified construction and which will permit an economic problem-free mass production, while the pump will be easy to assemble and to disassemble whenever an exchange of parts becomes necessary.
  • FIG. 1 illustrates a pump according to the present invention, partly in axial section and partly in view.
  • FIG. 2 is a top view of the pump of FIG. 1.
  • FIG. 3 represents an axial section through a modified pump according to the invention.
  • FIGS. 4-6 respectively illustrate further embodiments of a pump according to the invention in an illustration similar to that of FIG. 3.
  • the pump according to the present invention is characterized primarily in that the hollow shaft is designed as knock-outspindle which is inserted into a holding flange at an end face of the housing and which by means of at least one collar is resting against a supporting surface of the holding flange and is secured against axial displacement.
  • the pump according to the invention is furthermore characterized in that a first flange of the collimator is located between that end face of the rotor which is adjacent to the holding flange and that end face of the housing which is adjacent thereto and rests against an inner radial abutment surface of the holding flange.
  • the illustrated pumps substantially comprise a cylindrical housing 1 with two end walls 2 and 3 and a housing mantle 4, one end wall 2 being formed by an axially firmly clamped-in but detachable housing cover.
  • the circumference of the housing cover 2 as well as the circumference of the mantle 4 of housing 1 are each provided with two diametrically oppositely located protruding plates 5, 6.
  • the plates 5' of the housing cover 2 passages are provided, and in the plates 6 of the housing mantle 4 threaded bores are provided for a clamping screw 7.
  • FIGS. 1 In the embodiments illustrated in FIGS.
  • the circumference of the housing cover 2 as well as the circumference of the oppositely located end wall 3 have distributed thereover at least two passages 5 and 6 each which are passed through by a clamping screw 7.
  • the housing cover 2 is firmly clamped against the housing mantle 4.
  • an annular shoulder 8 is located on the inner side of the housing cover 2 which shoulder extends over a corresponding axially protruding annular collar 9 of the housing mantle 4 and centers the same in such a way that the housing cover 2 is precisely aligned with regard to the remaining housing portion.
  • a collimator motor 10 Arranged in housing 1 and coaxial therewith is a collimator motor 10 the stator 11 of which is connected to the inner circumferential surface of the housing mantle 4 in the central portion of its length. for instance, by a press fit.
  • the windings or coils 12 of the stator At both sides of the laminated packet of the stator 11 there are provided the windings or coils 12 of the stator which extend approximately to the respective pertaining end wall of housing 1.
  • That end wall 3 of the housing which is located opposite the housing cover 2 has a holding flange 13'located in the axis of the pump. This flange 13 extends over the major portion of its length into the housing 1, while the flange 13 forms one piece with the end wall 3.
  • the end wall 3 and the holding flange 13 are formed as one single piece, a stable and simple construction is obtained.
  • the arrangement of the holding flange 13 over a major portion of its length in the interior of the housing 1 permits a construction which saves space in axial direction.
  • Inserted into the bore 14 of the holding flange 13 is a sleeveshaped hollow shaft 15 with a plug section 16 the outer circumferential surface of which engages the bore 14 with press fit and thus is secured against axial displacement.
  • the hollow shaft 15 forms a knock-out spindle and a conveying pipe.
  • the plug section 16 of the hollow shaft 15 merges with a section 17 which is provided with the outer thread and which has only a slightly smaller outer diameter than the section 16 so that the hollow shaft 15 can from the interior of the housing be inserted into the holding flange 13 in such a way that the section 17 with its outer thread protrudes beyond the outer side of the end wall 3 and the holding flange 13.
  • an annular grooveshaped cut 18 on the outer circumference of the hollow shaft 15. The outer diameter of the cut 18 is only slightly smaller than the outer diameter of the plug section 16.
  • the cut 18 is adjacent an annular collar 19 which protrudes beyond the outer diameter of the ho]- low shaft 15 and forms a single piece therewith. As a result thereof, a stable construction is obtained.
  • the outer diameter of the annular collar 19 equals approximately the outer diameter of the holding flange l3 and thus furnishes a particularly large supporting surface.
  • the hollow shaft 15 forms a bearing section 20 which freely extends into the interior of the housing 1 and the outer diameter of which is only slightly less than the outer diameter of the plug section 16 or, as is the case with the embodiment of FIG. 6, equals the outer diameter of the plug section 16.
  • a bearing bushing 21 which extends approximately over the entire length of the bearing section 20. This bearing bushing 21 is pressed into the rotor 22 of the collimator motor which rotor 22 may be formed, for instance, by lamellae or in a laminated manner.
  • That end face of rotor 22 which faces away from the plug section 16 is located approximately in the plane of the inner end face of the hollow shaft 15, which inner end face is formed by the free end of the bearing section 20.
  • a spacer and connecting ring 23 which in axial section is angle-shaped and which extends into the inner bore of the rotor 2.
  • Ring 23 may extend, for instance, to the corresponding end face of the bearing bushing 21 (see FIG. 1) or may rest against the adjacent end face of the bearing bushing 21 and may be fixed relative to the rotor (FIGS. 3-6) by means of slotted or splined pins 47 or the like.
  • a pump rotor 24 Connected to the outer end face of the ring 23 is a pump rotor 24 which is axially aligned with the rotor 22 and which is located between the inner end of the hollow shaft and the housing cover 2.
  • a disc-shaped pump wall 25 Connected to that end face of the pump rotor 24 which faces away from the inner end of the hollow shaft 15 is a disc-shaped pump wall 25 which may form a single piece with the rotor blades 26 extending from the rotor shaft and the connecting ring 23.
  • Located opposite to the pump wheel wall 25 is a counter surface 27 which is composed of annular segment-shaped surface sections and is formed by corresponding ribs 28 which form one piece with the housing cover 2 and protrude inwardly beyond the inner side of the housing cover 2.
  • the rotor 22 and the pump rotor 24 are between the inner collar 19 of hollow shaft 15 and the counter surface 27 secured with a predetermined axial play against too great an axial displacement when the pump rotor 24 is due to occurring forces pulled away from the collar 19.
  • the pump wheel wall 25 has its outer side provided with a truncated cone-shaped extension 48 which cooperates with a counter surface 49 of a deblocking device 50 which counter surface 49 is rotatable from the outside.
  • the pump rotor 24 is by means of teeth or knurling provided on the engaging surface carried along and rotated so that any accumulation of limestone or the like will break off and that during the start of the pump the direction of rotation of the pump rotor 24 can be observed.
  • the liquid which leaves the region of the pump rotor 24 in radial direction is also in this instance by ribs 28 deviated into the axial direction of the pump and is conveyed to the pressure conduit.
  • the chamber 29 of housing 1 which houses the rotor 22 is sealed relative to chamber 30 which receives the stator 11 with the coils 12 by means of a collimator or sleeve 31 which is coaxially arranged with regard to the pump axis.
  • the collimator or sleeve 31 has a cylindrical extremely thin mantle 32 which surrounds the rotor 22 and the pump rotor 24 and may, for instance, engage the inner surface of the stator 11.
  • the collimator or sleeve 31 comprises at a first end a first annular discshaped flange 33 and has its other end provided with a second mantle-shaped flange 34.
  • the annular discshaped flange 33 which is formed by the radial inner range of a truncated cone-shaped end wall 35 of the collimator or sleeve 31 has its outer end face in engagement with the inner end face of the holding flange l3 and has its inner surface resting in centering manner against the outer circumference of the hollow shaft 15 and the plug section 16 (FIGS. l-4) or against a radial supporting surface of the holding flange 13 (FIGS. 5 and 6).
  • the liquid-filled chamber 29 is relative to the air-filled chamber 30 sealed by at least one annular disc-shaped seal 36. According to the embodiment of FIGS.
  • the seal 36 engages that end face of the first flange 33 which faces away from the holding flange 13 and has an outer diameter which corresponds to that of the holding flange 13.
  • the flange 33 and the seal 36 are clamped between the inner collar 19 of the hollow shaft 15 and the inner end face of the holding flange 13 so that an effective seal is obtained.
  • the inner wall 35 and the clamped-in flange 33 of the collimator or sleeve 31 have with all embodiments a thickness which is considerably greater than the thickness of the mantle 32.
  • the second flange 34 of the collimator or sleeve 31 has an inner diameter which equals the inner diameter of the mantle 32 of the collimator 31 while the outer diameter of the flange 34 is greater than that of the mantle 32 so that also the flange 34 has a thickness which is' considerably greater than that of the mantle 32. That end face 37 of the flange 34 which faces away from the other end of the collimator or sleeve 31 rests against an annular disc-shaped seal 38 which is inserted in an annular shoulder on the inner side of the housing cover 2 and the outer diameter of which approximately equals the outer diameter of the flange 34. An annular extension 39 of the housing cover 2 extends over the outer circumference of the annular seal 38.
  • the flange 34 engages the annular extension 39 in such a way that the flange is centered relative to the housing cover 2, if desired, through the intervention of sealing material.
  • the annular seal 38 is pressed against the flange 34 so that also in this instance an effective seal is obtained.
  • An axial displacement of the hollow shaft 15 can with the pump according to the invention be prevented at any rate by mounting the hollow shaft 15 with press fit in the holding flange 13.
  • the housing 1 is heated up in region of the holding flange 13, and the hollow shaft 15 is inserted so that the holding flange 13, after the latter has cooled off, will firmly embrace the hollow shaft 15.
  • pumps of this type are employed as circulating pumps for heated liquids, as, for instance, in heating installations so that the pump while in operation often absorbs considerable temperatures of the conveying medium.
  • the press fit will loosen and thus a harmful axial displacement of the hollow shaft and of the parts carried thereby would be possible relative to the housing 1.
  • the hollow shaft 15 is advantageously secured against .axial displacement by a positive connection with the holding flange 13. This positive connection is illustrated in the various embodiments in different ways.
  • a nut 41 forming a collar is screwed onto a part 40 of the outer threaded section 17 of the hollow shaft 15.
  • This nut 41 rests against the outside of the pertaining housing end wall 3 and holding flange 13 respectively and can be tightened against the outer annular radial end face of the holding flange 13.
  • the hollow shaft 15 is clamped fast, and also the first flange 33 with the annular seal 36 is clamped between the inner collar 19 and the holding flange 13.
  • the outer thread 42 of the outer threaded section 17 which thread 42 protrudes beyond the outer end face of nut 41 forms a connecting flange which is coaxial with the pump axis for connecting to the connecting flange a pipe line.
  • a corresponding nut 41 is screwed onto the outer threaded section 17 of hollow shaft 15.
  • This nut 41 engages the outside of the pertaining housing end wall 3 and can be tightened against the outer annular end face of the holding flange 13 so that it likewise forms an axially clamping outer collar.
  • the inner collar 19 of the hollow shaft 15 is pulled against its inner engaging surface on the holding flange 13 and thereby clamps fast the first inner flange 33 of the collimator.
  • the annular seal 36 located the annular seal 36 which likewise, when tightening the nut 41, is pressed in and thus prevents liquid from escaping from chamber 29 into the air-filled chamber 30.
  • That section of the holding flange 13 which protrudes from the end wall 3 has its outer side provided with an outer thread 42 which serves for connecting the connecting conduit by means of a box nut or the like.
  • the housing cover 2 At the oppositely located housing side, the housing cover 2, in all embodiments, has a similarly designed connection 43 with an outer thread 44 for connecting a conduit thereto.
  • the hollow shaft 15 with annular seal 36 and assembled collimator or sleeve 31 is from the inner side of the housing inserted into the holding flange l3 whereupon the nut 41 is assembled and tightened so that the hollow shaft 15 will then be firmly connected, the rotor 22 being connected to the pump rotor 24.
  • the housing cover 2 to be mounted and to fasten the same by means of the clamping screws 7.
  • FIG. 4 The pump according to the invention as illustrated in FIG. 4 has an outer collar 51 which forms one piece with the hollow shaft 15.
  • the outer collar 51 is pressed against the outer end face of the holding flange 13 by means of a screw connection similar to a box nut.
  • the hollow shaft 15 is secured in its position relative to the housing of the pump without the necessity of a separate axial clamping element.
  • the hollow shaft 15 does no longer have a radially outwardly protruding collar corresponding to the collar 19. Therefore, the collimator is not clamped-in but merely engages the outer end side of the holding flange 13, while the sealing force is generated upon the annular seal 36 in the direction toward the holding flange 13 by the clamping screws 7.
  • the clamping screws 7 also press the other flange 34 of the collimator 31 against the there located annular disc-shaped seal 38.
  • the hollow shaft 15 is within the region of the seal 36 provided with a shoulder 52 located toward the rotor 22.
  • the annular seal 36 extends into the shoulder 52 and is pressed-in in this area by the clamping force of the screw connection within the region of the collar 51.
  • the bearing section 20 which receives the bearing bushing 21 of the rotor 22 may, for instance, be produced of a high greade stainless steel and may be connected by welding to the plug section 16 of the hollow shaft 15.
  • the section 16 need not be produced of high grade and thereby expensive steel.
  • the hollow shaft 15 is pressed into the holding flange 13.
  • the hollow shaft 15 is, according to FIG. 4, inserted from the outside into the holding flange 13 of the heated up housing, whereupon from the other side the annular seal 36 as well as the collimator or sleeve 31 and the rotor 22 and pump rotor 24 are assembled, and finally the housing cover 2 is mounted.
  • the pump can, without risking a displacement of the parts, be shipped and installed, in which instance during the installation the collar 51 is first clamped fast whereby also during operation, when the pump is heated, the hollow shaft 15 will be secured in its position.
  • an inner collar 19 is provided, similar to the pumps of FIGS. 1-3.
  • a seal by means of a sealing ring 36 can be effected between the collar 19 and the inner side of flange 33 of the collimator or sleeve 31.
  • an additional annular seal 36 is provided which increases the sealing effect.
  • spreading elements 54 are provided which similar to a rivet connection extend behind a shoulder 55 on the inner surface of the holding flange 13.
  • the spreading elements 54 are, after insertion of the hollow shaft 15, bent outwardly from the inside in their position of installation by means of a punch or the like. The simultaneous pressing-in of the hollow shaft 15 into the holding flange 13 will prevent a springing or deflection of the spreading elements 54.
  • the hollow shaft 15 will, even when a considerable heating up occurs, positively be secured in its position relative to the holding flange 13 in a manner similar to that of FIG. by spreading elements 57 which, however, axially protrude on the inner end face of the holding flange 13.
  • the spreading elements 57 are formed by tongueshaped segments of a ring which extends the inner surface of the holding flange 13.
  • the collar 19 of the hollow shaft has within its foot area a deflecting surface 58 which when inserting the hollow shaftlS into the plug shaft 13 engages the spreading elements 57 and bends the same inwardly.
  • the defleeting surface 58 forms a lateral confinement of a slot 59 in which the spreading elements 57, following the assembly, are located substantially free from play so that axial displacements of the hollow shaft 15 relative to the holding flange 13 will be avoided.
  • That part of the holding flange 13 which extends beyond the end face 3, and with the embodiment of FIG. 1 the outer part of the hollow shaft 15, is designed as suction connection, and the connection 53 is designed as pressure connection.
  • the pump rotor 24 is by a corresponding shape of its blades 26 so designed that in both directions of rotation it will feed toward the pressure connection 43.
  • a change in the pump characteristic can easily be obtained by exchanging the blades 26 or the pump rotor 24, if desired, together with the rotor 22.
  • the inner diameter of the connection 43 substantially equals the inner diameter of the ribs 28 merging therewith and pertaining to the housing cover 2 and is substantially equal to the inner diameter of the hollow shaft 15 which, when the hollow shaft 15 is made as one piece (FIGS. 1-4 and 6), is constant over the entire length of shaft 15.
  • the housing 1 may be produced of die-cast metal or gray cast iron, expediently of steel, and in particular that part which forms the bearing section 20 may be made of stainless steel, such as chromium steel, or the like.
  • the pump rotor 24 may consist of synthetic material.
  • the outside of the housing mentle 4 is provided with a terminal box 45 or a cable outlet for the electric connection of the pump.
  • the inner annular collar 19 of the hollow shaft 15 may be provided with a radial bore 46 (FIG. 1) which connects the interior of the hollow shaft 15 with the inner chamber of the collimator 31 on that side of the rotor 22 which faces toward the suction side of the rotor 22 so that on this side of rotor 22 a pressure drop occurs, and the rotor 22 will not press at too high a pressure in the direction toward the counter surface 27.
  • a radial bore 46 FIG. 1
  • the pump according to the present invention which is also suited for delivering liquids at high temperatures, in addition to having small dimensions, is reversible and furthermore the centric construction has the advantage that it is self-ventilating and that the danger of soiling of the bearings is very small, and that it has excellent lubricating properties as well as a favorable withdrawal of heat from the motor.
  • the simple and easily to be surveyed construction is suited for the socalled building block principle so that a unitary construction is obtained for a number of rated outputs and pole numbers.
  • a pump impeller and a drive motor therefor in coaxial adjacent relation said motor comprising a stator and a tubular rotor, said impeller being drivingly connected to one end of said rotor, a common housing for said pump impeller and stator, a collimator sleeve extending axially along the inside of the stator and forming a fluid seal in the housing isolating the rotor and pump impeller from the stator, a fluid inlet in said housing leading into one end of said sleeve and a fluid outlet in said housing leading from the other end of said sleeve, a hollow shaft comprising a readily separable knock-out spindle interchangeably carried by said housing in centered accurate alignment therewith and secured against axial displacement extending axially into and rotatably supporting said rotor for quiet operation and being less susceptible to wear, said hollow shaft communicating with said fluid inlet and the discharge side of said pump impeller communicating with said fluid outlet, said housing having a generally radial shoulder there
  • said housing has a separable first end cover at the outlet end and having said fluid outlet herein, said housing having a cylindrical central portion surrounding said stator and a second end cover integral therewith at the inlet end of the housing and having said fluid inlet therein, a tubular portion formed on said second end cover in which said hollow shaft is mounted, said tubular portion having said radial shoulder thereon, and a collar on said hollow shaft engaging said radial flange of said sleeve element on the side opposite said radial shoul der.
  • tubular portion has a shoulder therein facing away from said rotor
  • hollow shaft has the axially outer end in the axial region of said shoulder and formed radially outwardly into clamping engagement with said shoulder.
  • said hollow shaft has an annular recess formed therein at the junction of said collar with said hollow shaft, said tubular portion having means protruding axially from the inner side of said radial shoulder and adapted to enter said recess and to be deformed therein to clamp said hollow shaft to said tubular portion.
  • a combination according to claim 2 in which said sleeve at the end opposite said radial flange has an axially facing annular surface, said first end cover having an axial surface engaging the axial surface on said sleeve and a projection on said first end cover engaging one radial side of the sleeve adjacent said annular surface.
  • a combination according to claim 9 which includes seal elements interposed between said end covers and the opposite ends of said sleeve and in pressure engagement with said radial flange and with said annular surface of said sleeve.
  • a combination according to claim 1 which includes a bearing bushing in the rotor engaging said hollow shaft, and a collar on said hollor shaft engaging the axial end of said bushing.
  • a combination according to claim 1 which includes means mounted in said housing and radially adjustable therein into locking engagement with said pump impeller.
US361048A 1972-05-18 1973-05-17 Pump Expired - Lifetime US3870438A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19722224213 DE2224213B1 (de) 1972-05-18 1972-05-18 Pumpe
DE19732323089 DE2323089A1 (de) 1973-05-08 1973-05-08 Pumpe

Publications (1)

Publication Number Publication Date
US3870438A true US3870438A (en) 1975-03-11

Family

ID=25763269

Family Applications (1)

Application Number Title Priority Date Filing Date
US361048A Expired - Lifetime US3870438A (en) 1972-05-18 1973-05-17 Pump

Country Status (12)

Country Link
US (1) US3870438A (ja)
AT (1) AT327007B (ja)
CH (1) CH568485A5 (ja)
DK (1) DK134079C (ja)
FI (1) FI53033C (ja)
FR (1) FR2191038B1 (ja)
GB (1) GB1393353A (ja)
IT (1) IT992552B (ja)
NL (1) NL7307026A (ja)
PL (1) PL85755B1 (ja)
SE (1) SE379833B (ja)
YU (1) YU127173A (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040091373A1 (en) * 2001-03-13 2004-05-13 Terry Sean Roderick Pump
WO2007064605A2 (en) 2005-11-30 2007-06-07 Dresser-Rand Company End closure device for a turbomachine casing
RU174399U1 (ru) * 2015-12-11 2017-10-11 Ангел Йорданов СТЕФАНОВ Энергоэффективный вентилятор с малой мощностью
WO2018204104A1 (en) * 2017-05-02 2018-11-08 Moog Inc. Electric motor for use in pressurized fluid environment

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009034158B4 (de) 2009-07-20 2023-11-16 Flender Gmbh Kapselung einer elektrischen Maschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2312848A (en) * 1941-01-07 1943-03-02 Albert R Pezzillo Motor driven pump unit
US2485408A (en) * 1948-05-14 1949-10-18 Republic Industries Motor pump unit
US2535695A (en) * 1950-06-07 1950-12-26 Jr Albert R Pezzillo Motor pump unit
US2537310A (en) * 1945-12-13 1951-01-09 Lapp Emil Fluid pump with built-in induction motor
US3164096A (en) * 1962-09-24 1965-01-05 W Dan Bergman Ab Pumps with incorporated motor
US3719436A (en) * 1970-09-22 1973-03-06 Gorman Rupp Co Axial flow pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2312848A (en) * 1941-01-07 1943-03-02 Albert R Pezzillo Motor driven pump unit
US2537310A (en) * 1945-12-13 1951-01-09 Lapp Emil Fluid pump with built-in induction motor
US2485408A (en) * 1948-05-14 1949-10-18 Republic Industries Motor pump unit
US2535695A (en) * 1950-06-07 1950-12-26 Jr Albert R Pezzillo Motor pump unit
US3164096A (en) * 1962-09-24 1965-01-05 W Dan Bergman Ab Pumps with incorporated motor
US3719436A (en) * 1970-09-22 1973-03-06 Gorman Rupp Co Axial flow pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
WO2007064605A2 (en) 2005-11-30 2007-06-07 Dresser-Rand Company End closure device for a turbomachine casing
EP1960632A2 (en) * 2005-11-30 2008-08-27 Dresser-Rand Company End closure device for a turbomachine casing
EP1960632A4 (en) * 2005-11-30 2011-09-21 Dresser Rand Co END LOCKING DEVICE FOR A TURBO MACHINE HOUSING
RU174399U1 (ru) * 2015-12-11 2017-10-11 Ангел Йорданов СТЕФАНОВ Энергоэффективный вентилятор с малой мощностью
WO2018204104A1 (en) * 2017-05-02 2018-11-08 Moog Inc. Electric motor for use in pressurized fluid environment
CN110603713A (zh) * 2017-05-02 2019-12-20 穆格公司 用于加压流体环境的电动马达
US10811927B2 (en) 2017-05-02 2020-10-20 Moog Inc. Electric motor for use in pressurized fluid environment
US11349368B2 (en) 2017-05-02 2022-05-31 Moog Inc. Electric motor for use in pressurized fluid environment
CN110603713B (zh) * 2017-05-02 2022-07-19 穆格公司 用于加压流体环境的电动马达

Also Published As

Publication number Publication date
FI53033C (ja) 1978-01-10
CH568485A5 (ja) 1975-10-31
ATA438473A (de) 1975-03-15
DK134079C (da) 1977-02-07
SE379833B (ja) 1975-10-20
YU127173A (en) 1982-06-30
IT992552B (it) 1975-09-30
AT327007B (de) 1976-01-12
PL85755B1 (ja) 1976-04-30
FI53033B (ja) 1977-09-30
NL7307026A (ja) 1973-11-20
FR2191038B1 (ja) 1974-07-05
GB1393353A (en) 1975-05-07
FR2191038A1 (ja) 1974-02-01
DK134079B (da) 1976-09-06

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