US2527878A - Cooling system for dynamoelectric machines - Google Patents

Cooling system for dynamoelectric machines Download PDF

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Publication number
US2527878A
US2527878A US48862A US4886248A US2527878A US 2527878 A US2527878 A US 2527878A US 48862 A US48862 A US 48862A US 4886248 A US4886248 A US 4886248A US 2527878 A US2527878 A US 2527878A
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United States
Prior art keywords
liquid
rotor
ducts
shaft
bore
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Expired - Lifetime
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US48862A
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English (en)
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Carl J Fechheimer
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Individual
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Priority to US48862A priority Critical patent/US2527878A/en
Priority to CH273211D priority patent/CH273211A/de
Priority to FR980956D priority patent/FR980956A/fr
Priority to BE487476D priority patent/BE487476A/xx
Priority to GB773/49D priority patent/GB661051A/en
Application granted granted Critical
Publication of US2527878A publication Critical patent/US2527878A/en
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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • H02K9/193—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil with provision for replenishing the cooling medium; with means for preventing leakage of the cooling medium

Definitions

  • the invention relates to improvements in liquid cooled dynamoelectric machines, particularly machines operating at high speed such as turbo generators.
  • the invention is in certain aspects an improvement of the inventions disclosed in my prior Patents 2,285,960 of June 9, 1942, and 2,381,122 of August 7, 1945.
  • the presentapplication relates particularly to improved means for controlling the flow of cooling liquid through the rotor of a dynamoelectric machine, and particularly to means for preventing circumferential flow of liquid due to tangential inertia forces, and including means for regulating the circulation of the liquid flow between an outside storage tank for the cooling liquid and the cooling liquid ducts in the machine.
  • the invention provides means for preventing leakage of cooling liquid at the entrance to and discharge from the rotor, without requiring rubbing seals at these locations.
  • the invention further provides priming means for the liquid circulating system effective to initiate the flow of liquid through the'machine upon starting.
  • Means are also provided for regulating the flow of cooling liquid from an elevated storage tank through the rotor to a collecting sump.
  • An object of the present invention is to provide means for automatically initiating the flow of cooling liquid through the machine upon starting thereof.
  • Another object is to provide means for regulating the flow of cooling liquid through the machine.
  • Another object is to provide the rotating part of the machine with self contained means to compensate for the tangential inertia forces which normally would inhibit a regulable flow of cooling liquid through the rotor of the machine.
  • Another object is to obviate the necessity of troublesome stuffing boxes or rubbing seals, for confining the liquid within a predetermined path through the machine.
  • Another object is to provide a simple, efficient and self regulating system of cooling liquid circulation for the rotor of high speed dynamoelectric machines.
  • Another object is to provide means which eliminate the possibility of gas or'vapor traps within the cooling ducts.
  • Another object is to provide means for recirculating and cooling of the cooling medium.
  • Another object is to provide in the rotating part of a machine cooling ducts which are easily manufactured.
  • Fig. l is a longitudinal section of the entering end for the cooling liquid of a high speed dynamoelectric machine's rotor.
  • Fig. 2 is a view similar to Fig. 1, of the exit end for the liquid from the rotor.
  • Fig. 3 is a transverse section along the line 33 of Fig. 1.
  • Fig. 4 is a transverse section along the line 44 of Fig. 2.
  • Fig. 5 is a bottom view of Fig. 4.
  • Fig. 6 is a modification of the structure shown in Fig. 1.
  • Fig. '7 is a section along the line 1-1 of Fig. 6.
  • Fig. 8 is a diagrammatic showing of a liquid circulating system for the rotor
  • Fig. 9 is a view of a fragment of Fig. 6 but on an enlarged scale.
  • the rotor I0 is provided with an integral shaft extension H, which has a central bore l2 extending from the outer end of the shaft to a point approximately coplanar with the transverse right hand end plane l3 of the rotor ID.
  • the shaft is supported in a bearing 14 of suitable construction.
  • the rotor I0 is provided with radial slots 15, in which the conductors of an energizing Winding are imbedded in the usual manner.
  • the diameter of the bore l2 has a preferably tapered enlargement to form a pocket [6, which connects with a number of outwardly extending smaller bores 11, which terminate on the outer periphery of the shaft l l near the part where it merges into the main cylindrical body of the rotor 10.
  • a stationary conduit l8 of slightly smaller external diameter than the bore [2 has its inner end spaced axially from the pocket IS.
  • the outer end of the shaft II has an end section 20 of reduced diameter to the end surface of which is fastened a ring shaped packing H! which surrounds the tube l8 with a very small clearance.
  • the tube I8 is supportingly attached by welding or other means to a stationary bracket 2 i.
  • a catch-basin 22 Fastened to the support 2
  • a gasket ring 25 is interposed between the flange 23 and the bracket 2
  • the catch-basin is provided with an inwardly extending radial flange 26 and a similar flange 2!
  • the lower part of the catch-basin 22 is provided with a drain pipe 23 to conduct away liquid which may leak past the ring IS.
  • the small amount of liquid that may escape past the flange 2'1 is drained off through one or more pipes 29a, the rotating disc 28 accentuating this drainage.
  • conduit I8 At its outer end the conduit I8 is provided with an L-bend 30.
  • is fixedly mounted concentric with the conduit 58.
  • extends into the enlargement I6, while its outer end passes through the bend 39, and is connected to a suitable trap, an eudiometer, or other device from which the entrapped air may escape, or be collected.
  • a valve 32 is indicated in Fig. 1, which may or may not be required.
  • a gauge or U-tube (not shown) containing. mercury may also be connected to conduit 3
  • may be supported by small lugs (not shown) from the interior of the conduit l8.
  • the cylindrical inner surface of the bore l2 may be rifled for; purposes which will be explained hereinaf er.
  • the rotor 10 is provided with axial ducts 33 (Figs. 1, 2 and 3), which preferably are arranged in the teeth intermediate of the winding slots l and additional ducts 34 may be provided below the bottoms of the winding slots [5 and sealed against the latter by wedges or plates 35, which may be placed into said slots and welded to the rotor before the windings are inserted into the slots l5. Liquid connections between the bores I!
  • a casing or enclosure 38 which provides a generally toroidal coaxial space 37 around the shaft ll, said casing also providin a plurality of radial ducts 38, which extend from the toroidal space outwardly between the slots [5 to the ducts and 34 to form hydraulic connections between the ducts 33 and 34 and the toroidal space 31.
  • the enclosure 36 is welded or otherwise attached in a liquid tight manner to the shaft and to the rotor respectively. As shown in Fig. 3, the toroidal space 3'!
  • partitions 39 which preferably extend from the shaft H to the circumferential wall of the enclosure 36, so as to divide the toroidal space into a, number of compartments to more effectively direct the flow of liquid from the bores I! to the radial ducts 38.
  • the partitions 39 may be curved or may be set at an angle from the position shown in the drawing. They may extend between the two side walls or may be spaced therefrom. These radial partitions prevent or impede circumferential flow of the liquid with respect to the rotor in the space 31, which flow would arise from the tangential inertia forces known as Coriolis forces, and which would seriously impede radial flow of the liquid.
  • the outlet end of the rotor is shown in Figs. 2, 4 and 5.
  • the rotor H] is provided with a shaft extension 40. which is journalled in a bearing of suitable type 4!.
  • the rotor ducts 33 and 34 communicate with the toroidal interior of a casing 42, which in all respects is constructed similar to the casing 36 aforedescribed.
  • the shaft adjacent to the outlet end of the rotor I0 is provided with ducts corresponding "to the ducts ll at the inlet end of the rotor.
  • the ducts 45 terminate in an axial bore 47, the outer end of which may be closed by a disc shaped plug 48.
  • the shaft 45 is provided with a plurality of substantially radial ducts 49.
  • the outer end of the ducts 49 are provided with screw plugs 50, which in turn are provided with orifices 5
  • the plugs 50 are preferably made of a material which resists erosion due to the high velocity of the cooling liquid passing therethrough.
  • a stationary collecting chamber 52 Surrounding the shaft 40 about the ducts 49 is a stationary collecting chamber 52, which is mounted concentric with the shaft 48 on suitable supports 53.
  • the diameter of the shaft 4f! inside of the collecting chamber 52 is preferably somewhat enlarged as at 54 to provide axial clearances 55 between the inner circular side walls 58 of the collecting chamber 52 and the shaft.
  • the enlargement of the shaft diameter also compensates for the weakening of the shaft due to the holes 39 and the bores for the plugs 59.
  • Concentric with the outer circumferential wall 5'! of the collectin chamber 52 is a cylindrical inner partition 58, which partition is provided with perforations 59. The perforations may be chamfered to facilitate the flow of liquid therethrough.
  • the partition 58 is welded to the side walls 56 of the collecting chamber 52.
  • the enlarged diameter of the shaft 54 has attached thereto a number of radial rings 60 of such outer diameter that they afford a small clearance from the partition 58. Attached to the partition 58 are inwardly extending rings 6! arranged intermediate of the rings 63.
  • An outlet pipe 62 (Figs. 4 and 5) is at tached to the outer collecting chamber 52 near its bottom and preferably tangential thereto, being so directed that the discharged liquid will tend to enter it.
  • Each of the side walls 56 of the collecting chamber may be further provided with a drain pipe 63, also preferably tangential thereto.
  • the entrance ends of the radial bores I1, 45 and 49, are preferably tapered or rounded so as to reduce the resistance to the flow of the entering liquid.
  • the casing may be modified to provide a plurality of sectional compartments, each interposed between one or more bores ll or 45, and one or a plurality of radial duct 38.
  • FIG. 8 the same illustrates a liquid circulating system which may be employed to supply cooling liquid to the machine.
  • the cooling liquid is stored in a sump 88 from which it is conveyed through a pipe 8! to a pump 82.
  • the pump forces the liquid through a pipe 83 into an elevated tank 84.
  • a heat exchanger 85 for cooling the liquid may be interposed in the pipe Bl or alternatively (not shown) in the pipe 83.
  • the pump may be driven by a motor M which is connected to a suitable power supply through a float switch 86, responsive to the liquid level in the tank 84.
  • a float switch an overflow pipe may be provided in the tank 84 to carry surplus liquid back to the sump 80.
  • a valve 87 in the pipe 83 may be employed to regulate the supply of liquid to the tank 84.
  • a pipe 88 connects the bottom of the tank 84 with the pipe 38 through a valve 90. If the pump 82 is above the level of the liquid in the sump 88, the pipe 88 is provided (as shown) with a branch connection which includes a valve 89 to afford when said Valve is open, a direct connection between the bottom of the tank 84 and the outlet of the pump 82.
  • the operation of the hydraulic system for the rotor is as follows: The sump 88 is first filled with cooling liquid and the tank 84 is partially filled. If the pump 82 is above the sump 88, the valve 89 is opened, so as to prime the pump. It may be advantageous to provide a check valve (not shown) in the pipe Bl between the pump 82 and the sump 88. After priming, valve 89 is closed and the motor M is started, and valve 81 is opened. This fills the tank 84. Thereafter valve 98 is opened, while the rotor I8 is simultaneously rotated slowly until all of its ducts and its hollow shafts are filled with liquid. A pressure gauge (not shown) which may be connected to the conduit 3!, will initially indicate a fluctuating pressure, but ultimately the pressure becomes constant when all of the passages are filled with liquid.
  • the head acting on the liquid in the machine is substantially the height of liquid in the tank 84, and most of the liquid passing through the machine is discharged into the sump 80, through the pipe 62, while a small amount is discharged through the pipes 29 and 63.
  • the liquid from the sump 30 is returned to the tank 84.
  • the rotor is accelerated to its normal speed by its prime mover.
  • the rate of flow of liquid increases rapidly with increasing speed of the rotor owing to the action of the radial outlet ducts 49.
  • valve 81 is opened so as to keep the tank 84 nearly filled.
  • the rate of flow at full speed of the rotor is determined mainly by the centrifugal head generated in the outlet ducts 48 and the cross sectional area of the orifices 5
  • the throttle '6 drop between the entrance pipe l8 and the bore 41 may be reduced by rounding or beveling the entrances of the various passages such as IT and 45, by shortening the conduit l8, and/ or by rifling the bore l2, the rifiing 95 being such as to cause the liquid to rotate at approximately the angular velocity of the rotor. If the rate of flow of liquid is limited by its entrance pressure, it may obviously be increased by raising the level of the liquid in the tank 84.
  • the collecting chamber 52 and the catch basin 22 are preferably split. and the two halves bolted together in a suitable manner for easy assembly.
  • a rotating machine element provided with means for passing a liquid therethrough and including a shaft having an axial liquid discharge bore, a discharge orifice in said shaft in communication with said discharge bore and arranged to convert the static head of a liquid in said bore into a velocity head, of an inner hollow cylinder having a perforate wall surrounding said shaft and extending axially in both directions from said orifice,
  • an outer solid walled stationary hollow cylinder axially coextensive with said inner cylinder and provided with solid end walls arranged to afford a clearance for said shaft, said outer cylinder being adapted to intercept liquid passing through said inner cylinder, at least one circular disc fixed to said shaft on either side of the plane of rotation of said orifice, cooperating circular discs axially alternating with said first named discs and fixed to the inside of said inner cylinder, and a liquid discharge conduit connected to the interspace between said cylinders.
  • a rotating machine element provided with means for passing a liquid therethrough and including a shaft having an axial liquid discharge bore, a discharge orifice in said shaft in communication with said discharge bore and arranged to convert the static head of a liquid in said bore into a velocity head, of an inner hollow cylinder having a perforate wall surrounding said shaft and extending axially in both directions from said orifice, an outer solid walled stationary hollow cylinder axially coextensive with said inner cylinder and provided with solid end walls arranged to afford a clearance for said shaft, said outer cylinder being adapted to intercept liquid passing through said inner cylinder, at least one circular disc fixed to said shaft on either side of the plane of rotation of said orifice, cooperating circular discs axially alternating with said first named discs and fixed to the inside of said inner cylinder, a liquid discharge conduit connected to the interspace between said cylinders, and a liquid discharge outlet connected to the interspace between said shaft and said first cylinder.
  • a rotor having a plurality of ducts longitudinally therethrough, shaft portions extending from the rotor ends and severally provided with a co-axial bore and with generally radial bores coacting for admission of cooling liquid to and for discharge of the liquid from the rotor ducts, and casings fixed on the rotor and the several shaft extensions, the casing having partitions forming compartments severally connecting the radial shaft bores with groups of rotor ducts and in liquid-tight relation.
  • a rotor having a plurality of ducts longitudinally therethrough, shaft portions extending from the rotor ends and severally provided with a co-axial bore and with radial bores coacting for admission of cooling liquid to and for discharge of the liquid from the rotor ducts, casings fixed on the rotor and the shaft extensions for severally connecting the radial shaft bores with groups of rotor ducts 3 and in liquid-tight relation, and collecting chambers related with the ends of the shaft portions for receiving liquid discharged from the shaft portion bores and for discharging liquid therefrom.
  • a rotating machine element comprising a body having a plurality of ducts therethrough, shaft portions extending from the ends of the body, each shaft portion having an axial passage and each shaft portion having passages extending radially from the axial passage, and casings severally fixed on the body ends and the shaft portions and extending about the shaft portions, the casings having partitions providing a plurality of compartments severally connecting one radial passage With a group of ducts for the flow of cooling liquid therethrough.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Motor Or Generator Cooling System (AREA)
US48862A 1948-09-11 1948-09-11 Cooling system for dynamoelectric machines Expired - Lifetime US2527878A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US48862A US2527878A (en) 1948-09-11 1948-09-11 Cooling system for dynamoelectric machines
CH273211D CH273211A (de) 1948-09-11 1949-02-07 Einrichtung an Maschinen mit einem von mehreren Kanälen längsdurchsetzten rotierenden Teil.
FR980956D FR980956A (fr) 1948-09-11 1949-02-15 Machine rotative avec rotor à canaux longitudinaux de circulation d'un liquide
BE487476D BE487476A (en(2012)) 1948-09-11 1949-02-22
GB773/49D GB661051A (en) 1948-09-11 1949-03-22 Improvements in liquid cooled rotors for dynamo-electric machines

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US48862A US2527878A (en) 1948-09-11 1948-09-11 Cooling system for dynamoelectric machines

Publications (1)

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US2527878A true US2527878A (en) 1950-10-31

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US48862A Expired - Lifetime US2527878A (en) 1948-09-11 1948-09-11 Cooling system for dynamoelectric machines

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US (1) US2527878A (en(2012))
BE (1) BE487476A (en(2012))
CH (1) CH273211A (en(2012))
FR (1) FR980956A (en(2012))
GB (1) GB661051A (en(2012))

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1014215B (de) * 1952-03-10 1957-08-22 Licentia Gmbh Fluessigkeitsgekuehlte Laeuferwicklung fuer elektrische Maschinen
US3049633A (en) * 1960-08-22 1962-08-14 Gen Electric Liquid-cooled rotor for dynamoelectric machine
US3398304A (en) * 1964-02-28 1968-08-20 English Electric Co Ltd Rotating machinery
US3518466A (en) * 1968-08-22 1970-06-30 Gen Electric Dynamoelectric machine
US3535565A (en) * 1968-03-29 1970-10-20 Siemens Ag Large dynamoelectric machine with a water-cooled rotor
US3543063A (en) * 1967-01-03 1970-11-24 Asea Ab Directly cooled electrical machine
US3740596A (en) * 1971-09-21 1973-06-19 Westinghouse Electric Corp Liquid cooled rotor for dynamoelectric machines
US3742266A (en) * 1971-09-21 1973-06-26 Westinghouse Electric Corp Liquid cooled rotor for dynamoelectric machines
US3894253A (en) * 1973-10-25 1975-07-08 Gen Electric Very high current field winding for dynamoelectric machine rotor
US3968388A (en) * 1972-06-14 1976-07-06 Kraftwerk Union Aktiengesellschaft Electric machines, particularly turbogenerators, having liquid cooled rotors
US4350908A (en) * 1980-12-04 1982-09-21 Westinghouse Electric Corp. Cooling system for rotor of a dynamoelectric machine
US6078115A (en) * 1996-11-07 2000-06-20 Fanuc Ltd Air-cooled motor

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2970232A (en) * 1958-10-21 1961-01-31 Gen Electric Conductor-cooled generator
CH583378A5 (en(2012)) * 1975-04-08 1976-12-31 Bbc Brown Boveri & Cie
DE2518062A1 (de) * 1975-04-23 1976-11-04 Kraftwerk Union Ag Kuehlmittelkreislauf fuer den laeufer einer elektrischen maschine mit supraleitender erregerwicklung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1911790A (en) * 1930-07-17 1933-05-30 Blathy Otto Titus Rotary field magnet
US2381122A (en) * 1944-04-27 1945-08-07 Carl J Fechheimer Cooling means for dynamoelectric machines

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1911790A (en) * 1930-07-17 1933-05-30 Blathy Otto Titus Rotary field magnet
US2381122A (en) * 1944-04-27 1945-08-07 Carl J Fechheimer Cooling means for dynamoelectric machines

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1014215B (de) * 1952-03-10 1957-08-22 Licentia Gmbh Fluessigkeitsgekuehlte Laeuferwicklung fuer elektrische Maschinen
US3049633A (en) * 1960-08-22 1962-08-14 Gen Electric Liquid-cooled rotor for dynamoelectric machine
US3398304A (en) * 1964-02-28 1968-08-20 English Electric Co Ltd Rotating machinery
US3543063A (en) * 1967-01-03 1970-11-24 Asea Ab Directly cooled electrical machine
US3535565A (en) * 1968-03-29 1970-10-20 Siemens Ag Large dynamoelectric machine with a water-cooled rotor
US3518466A (en) * 1968-08-22 1970-06-30 Gen Electric Dynamoelectric machine
US3740596A (en) * 1971-09-21 1973-06-19 Westinghouse Electric Corp Liquid cooled rotor for dynamoelectric machines
US3742266A (en) * 1971-09-21 1973-06-26 Westinghouse Electric Corp Liquid cooled rotor for dynamoelectric machines
US3968388A (en) * 1972-06-14 1976-07-06 Kraftwerk Union Aktiengesellschaft Electric machines, particularly turbogenerators, having liquid cooled rotors
US3894253A (en) * 1973-10-25 1975-07-08 Gen Electric Very high current field winding for dynamoelectric machine rotor
US4350908A (en) * 1980-12-04 1982-09-21 Westinghouse Electric Corp. Cooling system for rotor of a dynamoelectric machine
US6078115A (en) * 1996-11-07 2000-06-20 Fanuc Ltd Air-cooled motor

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Publication number Publication date
FR980956A (fr) 1951-05-21
CH273211A (de) 1951-01-31
GB661051A (en) 1951-11-14
BE487476A (en(2012)) 1949-03-15

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