US3765480A - Device for cooling rotors - Google Patents

Device for cooling rotors Download PDF

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US3765480A
US3765480A US00135606A US3765480DA US3765480A US 3765480 A US3765480 A US 3765480A US 00135606 A US00135606 A US 00135606A US 3765480D A US3765480D A US 3765480DA US 3765480 A US3765480 A US 3765480A
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Prior art keywords
rotor
cavities
working medium
heat
condensation
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US00135606A
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English (en)
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P Fries
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Siemens AG
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Siemens AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0208—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes using moving tubes
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/22—Arrangements for cooling or ventilating by solid heat conducting material embedded in, or arranged in contact with, the stator or rotor, e.g. heat bridges
    • H02K9/225—Heat pipes

Definitions

  • a cooling device for cooling a rotor comprises a condensation chamber on a front surface of the rotor and a plurality of cavities containing an evaporable working medium provided in the area of the heating zones at the periphery of the rotor and ending directly in the condensation chamber.
  • the invention relates to a device for cooling rotors. More particularly, the invention relates to a device for cooling rotors with a heat tube containing an evaporable working medium and wherein the centrifugal acceleration may be utilized for recycling the condensate into the evaporation zone. Cavities containing the working. medium are provided within the area of the heating zones, at the periphery of the rotors.
  • the aforedescribed type of arrangement is well suited, for example, for cooling electrical mechinery. Difficulties are encountered in large rotors particularly in rotors having larger diameters, especially when the heat due to energy losses occurs in heating zones located at the periphery of the rotor where the heat accumulates to high values. In this case, the dissipation of heat via the rotation shaft entails a high heat resistance, to which the flow of heat in the rotor is exposed. Moreover, the heat-transferring wall of the heat tube may become too small for heat transformation alone. Therefore, arotor equipped with the known cooling device does not always insure a dissipation of heat losses which is adequate, for example, for the operational reliability of an electrical machine.
  • a device for cooling turbine blades is known, for example, from the known publication, where the blade rotor is designed as a heat tube and cavities are provided in the turbine blades.
  • the cavities are connected to the tubular heater via a tube having a small cross section.
  • the centrifugal force causes the wall of the heat tube to be lined with the working medium and the working medium is forced into the cavities of the turbine blades.
  • the working medium is primarily evaporated in the cavities of the turbine blades.
  • the heat transfer from the turbine blades to theheat tube occurs via a flow of gas bubbles of the working medium and through a natural convection of the heated working medium in the connecting tubes.
  • the transfer of heat via gas bubbles and the heated working medium must be carried out against the flow of the cold working medium, in these connecting tubes.
  • the travel path of the heat is therefore also subjected to a great heat resistance. Also, when the heat losses are greater, the heat transfer area of the heat tube becomes too small. Hence, the indicated problems cannot be solved by the known arrangements.
  • the cavities end directly in a condensation chamber located at a front surface of the rotor.
  • the cavities may be provided in the form of channels. It is preferable to interconnect the cavities in the rotor by means of channels.
  • a rotor or a number of such rotors comprising one or more spaced rotor parts affixed to a shaft which functions as an axis of rotation, may be provided with cavities whereby the cavities of adjacent rotor components or of the rotors may be connected through tubular connections, or each cavity or several interlinked cavities may be directly connected to a condensation chamber located at the front surface of the rotor or rotor part or component.
  • Each front surface of a rotor may be provided with a condensation chamber.
  • each condensation chamber has a heat exchanger whose heat exchange area is larger than the area on the front surface of the rotor covered by the condensation chamber.
  • Each condensation chamber may at least cover almost one front surface of the rotor.
  • the heat exchanger is preferably provided as a folded surface.
  • the folded surface may be designed as a bellows having essentially circular concentrically positioned folds.
  • the opening angle of the bellows folds may be made a maximum through the heat exchanger surface, at a predetermined rotor speed, with respect to the entire flow of heat.
  • a number of condensation chambers may be provided, and may be interconnected in the form of a cascade in order to enlarge the heat exchange area.
  • the evaporation of the working medium is effected directly at the place of origin, in the heating zones of the rotor.
  • the working medium which evaporates in the cavities of the rotor flows out in the form of steam, directly into the condensation chambers at the front surfaces of the rotor.
  • no resistance is encountered in the flow path of the steam.
  • the condensate too, flows directly from the condensation chambers back into the evaporation chambers of the rotor, that is, along the outside of the connecting paths, because of the centrifugal force.
  • cavities cross-linked with channels will provide the rotor with separate flow paths for the steam and for the condensate. Moreover, such cross-linking may also insure the cooling of several rotors or rotor parts or components, without any additional expenditure. This type of cross-linking also helps to adjust or adapt the arrangement of the cavities in the rotor to special temperature profiles. For example, one of the cavities for the working medium in a poleshoe of an electrical machine may be guided to a location where particularly high losses occur.
  • the device of the invention may also be conceived, according to this description, as a system comprising various heat tubes connected within the rotor in parallel with respect to the heat flow and having common condensation chambers.
  • the size of the condensation surfaces and the heat transfer surfaces of the heat exchanger may be adjusted in the simplest ing heat due to energy losses.
  • the size of these surfaces is no larger determined, as in the known devices, by the diameter of the shaft, designed as a tubular heater.
  • adequate cooling may be obtained in any case with the device of the invention, whereby cascade type connected condensation chambers may be used for extremely high heating.
  • Shaft portions located outside the rotor may be hollow and may be included in a condensation chamber. If necessary, the shaft of the rotor, which is intended to function as the axis of rotation, may also be designed as a separate heat tube.
  • FIG. 1 is a view, partly in section, of an embodiment of the cooling device of the invention
  • FIG. 2 is a sectional view taken along the lines II-II of FIG. 1;
  • FIG. 3 is a schematic diagram explaining the theory of operation of the embodiment of the cooling device of FIGS. 1 and 2; 7
  • FIG. 4 is a view, partly in section, of another'embodiment of the cooling device of the invention.
  • FIG. 5 is a cross-sectional view through part of the cooling device of FIG. 4;
  • FIG. 6 is a view, partly in section, of another embodiment of the cooling device of the invention.
  • FIG. 7 is a sectional view of still another embodiment of the cooling device of the invention.
  • FIG. 8 is a sectional view of another embodiment of the cooling device of the invention.
  • FIG. 9 is a sectional view of another embodiment of the cooling device of the invention.
  • FIG. 10 is a schematic diagram, partly in section, of a flywheel Diesel generator cooled by the cooling device of the invention.
  • FIG. I shows a rotor 1, in section.
  • the rotor 1 comprises metal and may constitute the rotor of an electrical machine.
  • the bearings of the rotor 1, as well as other parts of the device such as, for example, the stator of the electrical machine, are not shown in the FIGS., in order to preserve the clarity of illustration.
  • the rotor 1 may be rotated about or around a shaft 2, which is positioned on a main inertia axis of the rotor I.
  • the shaft 2 has a diameter 5.
  • a heating zone la is assumed for the rotor 1, and is separated from the remaining part 1b of the rotor, as indicated by broken line 3.
  • the broken line 3 may be defined by points of the same temperature.
  • cavities 4 are provided in the heating zone 1a.
  • the cavities 4 end directly in condensation chambers 5 and 5 provided on both front surfaces of the rotor I.
  • the cavities 4 are channel-type bores having longitudinal axes essentially parallel to the axis of rotation of the rotor 1.
  • Each condensation chamber 5 and 5' covers a corresponding front surface of the rotor l and is provided with a heat exchanger 6 and 6, respectively, comprising a material having good thermal conductivity such as, for example, aluminum, whose heat exchange surface is larger than the corresponding front surface of the rotor 1.
  • a heat exchanger 6 and 6 comprising a material having good thermal conductivity such as, for example, aluminum, whose heat exchange surface is larger than the corresponding front surface of the rotor 1.
  • Any heat exchanger which is adapted to the problem may be used as the heat exchanger for the condensation chambers 5 and 5'. It was found to be particularly favorable to use a folded surface or bellows-type structure as each of the heat exchangers 6 and 6.
  • the shape of the cross-section and the surface of the folds or creases may be selected as desired for this type of folded surface.
  • the folded surface may be meandershaped, wave-shaped or bellows-shaped.
  • FIG. 1 shows the heat exchangers 6 and 6' in form of bellows.
  • the folds of the bellows 6a, 6b and 6c and 6a, 6b and 6c are circular and positioned concentrically with the axis of rotation of the rotor 1.
  • the diameter of the outer limit of the larger bellows fold is R.
  • the openthrough the heat exchangers 6 and 6' which are hereinafter discussed in greater detail.
  • each of the heat exchangers 6 and 6 may be wetted with an air current or with a liquid coolant such as, for example, water.
  • the folds of the condensation areas of the heat exchanger 6 are mutualy supported by expanding rings 9, which are provided with inlet openings 9a for the coolant.
  • the expanding rings 9 may also assist in converting a laminar coolant flow into a turbulent current. This improves the heat exchanger.
  • the condensation chambers 5 and 5 and the cavities 4 of the rotor l which function as evaporation chambers, contain a working medium having a high evaporation heat and whose steam pressure is below the pressure limits, resistance or stability of the rotor when said rotor is at a permissible heating temperature.
  • the working medium must also have chemical stability in order to prevent the formation of a gas pocket or cushion, for example, in the condensation chambers 5 and 5.
  • the evaporation chambers 4 and the condensation chambers 5 and 5' thus define a hermetically sealed system, wherein the working medium circulates or cycles as a heat transfer medium, under the influence of the centrifugal force.
  • the return flow of the condensate occurs also at the peripheries of the condensation chambers 5 and 5 and the rotor l.
  • the condensate flowing back into the cavities 4 is depicted in FIG. 1 by arrows l1 and 11'.
  • a separation of the steam flow and 10' and the returning or recycling condensate l1 and 11 occurs in the aforedescribed device due to cent'rifuga] force.
  • the cooling device of the embodiment of FIG. 1 offers the advantages hereinbefore explained in detail.
  • FIG. 2 shows a section through the rotor of FIG. 1.
  • FIG. 2 shows that, in the illustrated example, the evaporation chambers or cavities 4 are distributed in rotational symmetry, relative to the axis of,rotation of the flow Q, via the heat exchange areas or surfaces of the heat exchangers 6 and 6'.
  • Nusselt calculates the condensation coefficient, the thickness of the developing condensation film'and the heat flow during the condensation of flowing steam at a vertically positioned wall of constant width, under the influence of centrifugal force. The calculation is derived from the Navier-Stokes movement equations 'for a viscous liquid, which are modified under limiting con ditions and whose integration leads to the indicated quantities.
  • FIG. 3 shows that the folding surface 60, 6b and 6c of the heat exchanger 6 is reduced to a frustum housing area 12.
  • This approximation makes sense, since, during rotation, the steam and the condensate are pressed against the surfaces 13a, 13b and 130 of the bellow folds 6a, 6b and 6c subjected to centrifugal force.
  • a condensate skin or coating forms at these surfaces.
  • a statistically distributed drop condensation may develop at the surfaces 14a and 14b of the bellows folds of FIG.
  • the conical housing surface 12 of FIG. 3 is a combination of the bellows surfaces.
  • the centrifugal acceleration b increases with the radius r, and thereby also its tangential acceleration component b,-, along a housing line of said conical housing surface.
  • the condensate is subjected to increasing forces in wall direction, which try to drive the condensate to the outside.
  • an increasing radius r causes an increase in the circumference of the conical housing surface 12.
  • the constant ground acceleration g which enters into Nusselts theory must be replaced by the variable conical housing circumference, via the variable tangential acceleration component h and via the constant wall width of the perpendicularly positioned wall, according to Nusselts theory.
  • the layer thickness of the condensate skin and the heat transfer factor a (x), during centrifugal condensation in a conical chamber may be calculated in analogy with Nusselts theory. Both quantities are dependent upon x and y.
  • the heat transfer factor a (x) of the condensate, the heat or thermal conductance coefficient of thematerial of the frustum wall, as well as the heat transfer factor a, on the outer surface of the cone, may help to define the median heat transfer factor along the conical condenser. From such, we may determine the heat flow Q through the areas which are coated by the condensate skin.
  • T is the saturation temperature of the steam
  • T is the coolant temperature at the outer wall of the frustum and T,,, is the temperature of the conical wall
  • w [cal/gr] is the evaporation heat
  • p gr/cm is the density of the condensate
  • 1 gr/cm is the dynamic viscosity of the condensate.
  • FIG. 4 shows an embodiment, where the evaporation chambers or cavities 4 in the rotor l are interconnected through cross-linking channels 4a, which end within the rotor.
  • the interlinking of the cavities 4 in the rotor 1 defines an additional branch system for the steam flow within the rotor l.
  • the position of the evaporation chambers 4 and of the cross-linking channels 4a depends upon the constructive factors such as, for example, an anisotropic temperature distribution in the rotor 1. In this embodiment, too, the evaporation chambers 4 andthe channels 4a may be in rotational symmetry.
  • the cross-linking increases the cross-section of the path of the steam flow and, as hereinbefore described, the cross-linking provides an almost complete separation of the steam flow paths 10 and 10' and the condensate paths 11 and 11 which flow back into the evaporation chambers 4.
  • FIG. 4 indicates that the cross-linking may continue into the area of the shaft 2.
  • FIG. 5 shows in section, a cross-section through the rotor l of FIG. 4.
  • Evaporation channels or cavities 4 are located in the area of the heating zone la.
  • the longitudinal axes of the cavities 4 need not be parallel to the axis of rotation of the rotor I but, as shown in FIG. 5, may also proceed in radial direction and the cavities may have cross-connections.
  • the arrangement of the cavities 4 must be selected so that in a given usage, an optimum heat transfer from the heating zone la will be insured. The optimum heat transfer may be additionally controlled by the volume of working medium present in the system.
  • the amount of working medium should be so selected in order to achieve an optimum heat transfer, that during operation, that is, during the rotation of the rotor l, a liquid level 16 is established in the cavities 4 and the cross-linked channels 4a, which is approximately within the range of the limit or boundary 3 of the heating zone la of the rotor 1.
  • the evaporation of the working medium is then effected at this liquid level and the steam flows off through the cavities which are not filled with liquid or through the channel portions into the condensation chambers 5 and 5'.
  • a possibly obstructing counterflow of steam and condensate in the same connecting line may be largely prevented.
  • the steam flow paths l0 and and the condensate flow paths Ill and 11 have their own systems.
  • the condensate collects at the deepest point of the channel or cavity system 4 and is then flown off again, during rotation, as shown in FIG. 5, to the periphery of the rotor l.
  • FIG. 6 illustrates an embodiment in which several rotors 17, 18, 19, 20 and 21 are affixed to the shaft 2.
  • the rotor 17 has two separate rotor parts 17a and 17b.
  • the device of FIG. 6 rotates around the axis of rotation 15 of the shaft 2.
  • Each of the rotors 17 to 21 and each of the rotor parts 17a and 17b is provided with cavities 4, which may be cross-linked with channels, as shown in FIGS. 1 to 5.
  • the cavities or channel systems 4 are not separately shown in the rotors of FIG. 6.
  • the channel systems or cavities 4 of each rotor are connected to a channel system of an adjacent rotor or directly to the condensation chambers 5 or 5', provided in the embodiment of FIG.
  • the condensation chambers 5 and 5' may also be provided on the front'surface of a rotor part or component, or a rotor within the system, for example,
  • This system is used, for example, for cooling gas turbine blades or vanes, so that the system of FIG. 6 does not have the disadvantages of the aforedescribed known cooling system, and is not limited with respect to the quantity of heat due to energy losses, which can be removed by the cooling system.
  • FIG. 7 A possibility for enlarging the heat dissipation surfaces is shown in FIG. 7.
  • the shaft portions 2a and 2b are designed as hollow or tubular shafts having chambers 22a and 22b, respectively, formed therein.
  • the chambers 22a and 22b in the truncated shafts 2a and 2b are connected via openings 23 and 23 to the condensation chambers 5 and 5.
  • Heat exchangers 24 and 24' are mounted on the truncated shafts 2a and 2b, respectively.
  • the chambers 22a and 22b of the shaft 2 are incorporated into the condensation chambers 5 and 5, thereby enlarging the heat transfer surface for the removed heat due to energy losses.
  • FIG. 7 Another peculiarity of the embodiment of FIG. 7 is that the truncated shafts 2a and 2b have an approximately constant surface temperature. This may sometimes result in an impermissibly high heating of the bearings, of which a bearing 25 is schematically shown in FIG. 7. If the impermissibly high heating of the bearing cannot be obviated by a suitable bearing construction, the bearing 25 must be thermally insulated, directly at its seat, against the shaft 2. To accomplish this, a sleeve 26 ofa material having poor thermal conductivity is inserted on the shaft 2'. The sleeve 26 should be arranged so that it projects sufficiently beyond both sides of the bearing 25. The sleeve 26 may also be located in an annular depression of the shaft 2'.
  • FIG. 8 Another possibility for expanding the heat transfer surface for the removal of dissipated heat or heat losses is shown in the embodiment of FIG. 8.
  • a condensation chamber 5a is positioned on the front surface of the rotor which is shown in section. Additional condensation chambers 5b and 5c are fixed to the shaft 2'.
  • the condensation chambers 5a, 5b and 5c are interconnected in the form of cascades via a pipeline system.
  • the heat exchangers 6A, 6B and 65C of the condensation chambers 5a, 5b and 50, respectively are separately wetted by a coolant flowing in the direction of arrows 7.
  • the steam may flow through connecting lines 27 and through the chamber 23 of the shaft 2, to the condensation chambers 5a, 5b and 5c.
  • the connecting lines 27 for the steam preferably branch off from surfaces of the heat exchangers 6A, 6B and 6C, which are not affected by any component of the centrifugal force, as hereinbefore discussed in connection with FIG. 3.
  • the condensate flows back into the evaporation chambers 4 in connecting lines 27b located at the periphery of the rotating system.
  • the individual condensation chambers 5 and 5 may be constructed differently, so that the cooling would be particularly enhanced.
  • the folded surface of the heat exchanger 6C of FIG. 8 has a wavy cross-section, deviating from the folded surfaces of the heat exchangers 6A and 6B.
  • Tubular systems may also be used as the condensation chambers, and it is particularly advantageous to cross-link the tubes of a system.
  • the shaft 2" may be designed as a separate heat tube.
  • the shaft 2" must then be provided with a bore 28 which extends through the rotor and which contains a heat exchange medium. It may be necessary in the embodiment of FIG. 9 to provide the bearings for the rotor with heat insulation, as described with reference to FIG. 7.
  • FIGS. 1 to 5 It has been hereinbefore mentioned in this connection that several separate systems, disclosed in FIGS. 1 to 5, may be situated in one rotor. At the same time, each of the systems must be provided with its own condensation chamber on a front surface of the rotor.
  • FIG. l shows, as an example, the cooling of the rotor of a flywheel Diesel generator by the cooling device of the invention.
  • a generatorshaft 29 is rotatably mounted in bearings 30 and 30, affixed to foundations 31 and 3l'respectively.
  • a rotor 32 is mounted on the generator shaft 29.
  • the shaft 29 drives an exciter machine 33.
  • Pole shoes 35 are mounted with windings 36 on a rotor ring 34.
  • the generator hasa stator 37 which is enclosed by a generator housing 38. To obtain the torque required for operation, the rotor 32 is provided with a flywheel 39.
  • the flywheel 39 is a so-called lateral flywheel, which is pulled up in radial directions on the driving side, by the rotor ring 34 in order to provide the shortest possible structural length.
  • the lateral flywheel 39 is very well suited for the installation of a cooling device for the pole shoes 35, in accordance with the invention.
  • the lateral flywheel 29 is sealed by a heat exchanger 6, which in the example of FIG. 10 has a folded surface of wave-shape.
  • Another heat exchanger such as, for example, a star-shaped, hollow rib arrangement, may be provided instead of the folded surface. Due to the size of the flywheel 39, a condensation chamber is provided in any event. The heat transfer surfaces of the heat exchanger 6 are sufficiently large for the removal of high heat due to energy losses.
  • the pole shoes 35 are provided with a cross-linked system of channels, as disclosed with reference to FIGS. 4 and 5.
  • the channel system of the pole shoes 35 is not separately shown in FIG. 10.
  • the channel system of the pole shoes 35 is directly connected, via tubes 40a and 40b to the condensation chamber 5.
  • the condensation chamber 5 and the channel system contain an easily evaporable working medium.
  • the channel system, as an evaporation chamber, and the condensation chamber 5 constitute an hermetically sealed system, wherein the working medium circulates as a heat carrier medium under the influence of centrifugal force, in the aforedescribed manner, and wherein the heat due to energy losses are transferred from the pole shoes 35 to the heat exchanger 6.
  • the steam flow paths l0 and condensate return flow path 11 end separately in the tubes 40a and 40b.
  • the outside surface of the folded surface heat exchanger 6 is wetted by a coolant 7.
  • expanding rings may be provided for the folds of the heat exchanger, as disclosed in FIG. 1.
  • expanding rings have openings for the flow of the coolant.
  • the expanding rings protect the condensation surfaces against radial bulging due to centrifugal force.
  • the expanding rings are not shown in FIG. 10.
  • FIG. 10 shows what simple means may be utilized, in accordance with the invention, to provide cooling for a rotor l or 32, along its periphery.
  • An economical, low output is required for removing even extremely high dissipation losses and the operational reliability of electrical machinery may be considerably improved thereby.
  • a cooling device for cooling a rotor rotatable about its axis and having two front faces comprising means defining a'plurality of cavities disposed at the periphery of said rotor, each of said cavities having at least a portion thereof extending substantially parallel to the axis of said rotor, a condensation chamber on a front face of said rotor, each of said cavities communicating with said chamber, said chamber and said cavities defining a hermetically sealed enclosure in which an evaporable working medium is disposed, said condensation chamber being defined at least in part by folded heat exchange surface having an area which is greater than the area of the front face of the rotor on which said condensation chamber is disposed, said heat exchange surface being defined by a plurality of substantially circular and concentrically positioned folds, the outside of said heat exchange surface being exposed to a heat exchanger medium to cool the working medium in said hermetically sealed enclosure, the inside of said heat exchange surface providing a condensation zone for said working medium, whereby centrifugal force is utilized for providing return flow of the con
  • a cooling device as claimed in claim 1 further comprising a plurality of channels cross-linked in a network with the cavities in a manner whereby a level for a liquid is adjusted during operation to the volume of working medium in the network, the level being substantially within the limit of the heating zones of the rotor.
  • a cooling device including a second condensation chamber on the other front face of said rotor, each of said cavities communicating with said second condensation chamber, said second chamber being included in said hermetically sealed enclosure in which said evaporable working medium is disposed, said second condensation chamber being defined at least in part by a second folded heat exchange surface having an area which is greater than the area of the front face of the rotor on which said second condensation chamber is disposed, said second heat exchange surface being defined by a plurality of substantially circular and concentrically positioned folds, the outside of said second heat exchange surface being exposed to a heat exchange medium to cool the working medium in said hermetically sealed enclosure, the inside of said second heat exchange surface providing a condensation zone for said working medium, whereby contrifugal force is utilized for providing return flow of the condensed working medium from said second condensing chamber to said plurality of cavities at the periphery of said rotor where said working medium is evaporated.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00135606A 1970-04-24 1971-04-20 Device for cooling rotors Expired - Lifetime US3765480A (en)

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DE19702019956 DE2019956A1 (de) 1970-04-24 1970-04-24 Anordnung zur Kuehlung von Rotationskoerpern

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AT (1) AT306167B (de)
CA (1) CA918730A (de)
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US20030066381A1 (en) * 2001-09-17 2003-04-10 Eric Lewis Heat energy dissipation device for a flywheel energy storage system (fess), an fess with such a dissipation device and methods for dissipating heat energy
US20040007878A1 (en) * 2002-07-11 2004-01-15 Siemens Westinghouse Power Corporation Turbine power generator including supplemental parallel cooling and related methods
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US20050285403A1 (en) * 2003-03-28 2005-12-29 Tharp John E Hydro-electric farms
US20080023177A1 (en) * 2006-06-19 2008-01-31 Timothy Hassett Electric motor with heat pipes
US20100026109A1 (en) * 2006-06-19 2010-02-04 Thermal Motor Innovations, Llc Electric motor with heat pipes
US20100026108A1 (en) * 2006-06-19 2010-02-04 Thermal Motor Innovations, Llc Electric motor with heat pipes
US20100033042A1 (en) * 2008-08-06 2010-02-11 Thermal Motor Innovations , LLC Totally enclosed heat pipe cooled motor
US20100283335A1 (en) * 2009-05-05 2010-11-11 General Electric Company Generator coil cooling baffles
US20120217756A1 (en) * 2009-11-02 2012-08-30 Siemens Aktiengesellschaft Wind power generator with internal cooling circuit
US9416877B2 (en) 2009-06-12 2016-08-16 Alfa Laval Corporate Ab Cooling device for spindle sealing and/or bearing means
US11038390B2 (en) 2017-07-27 2021-06-15 Rolls-Royce Plc Electrical machine apparatus having a conduit with a particular arrangement for an inlet and outlet
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US4217513A (en) * 1976-11-10 1980-08-12 Fujitsu Fanuc Limited Direct current motor
FR2371807A1 (fr) * 1976-11-23 1978-06-16 Electric Power Res Inst Ecran de protection contre le rayonnement thermique d'une generatrice supraconductrice
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US7569955B2 (en) 2006-06-19 2009-08-04 Thermal Motor Innovations, Llc Electric motor with heat pipes
US8134260B2 (en) 2006-06-19 2012-03-13 Hpev, Inc. Electric motor with heat pipes
US8148858B2 (en) 2008-08-06 2012-04-03 Hpev, Inc. Totally enclosed heat pipe cooled motor
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US7893576B2 (en) 2009-05-05 2011-02-22 General Electric Company Generator coil cooling baffles
US20100283335A1 (en) * 2009-05-05 2010-11-11 General Electric Company Generator coil cooling baffles
US9416877B2 (en) 2009-06-12 2016-08-16 Alfa Laval Corporate Ab Cooling device for spindle sealing and/or bearing means
US20120217756A1 (en) * 2009-11-02 2012-08-30 Siemens Aktiengesellschaft Wind power generator with internal cooling circuit
US9287747B2 (en) * 2009-11-02 2016-03-15 Siemens Aktiengesellschaft Wind power generator with internal cooling circuit
US11038390B2 (en) 2017-07-27 2021-06-15 Rolls-Royce Plc Electrical machine apparatus having a conduit with a particular arrangement for an inlet and outlet
US20230353016A1 (en) * 2020-03-26 2023-11-02 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Rotary machine

Also Published As

Publication number Publication date
AT306167B (de) 1973-03-26
CA918730A (en) 1973-01-09
SE361794B (de) 1973-11-12
CH528170A (de) 1972-09-15
JPS5214452B1 (de) 1977-04-21
DE2019956A1 (de) 1971-11-04

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