Electrical generator or motor structure – Dynamoelectric – Rotary
Reexamination Certificate
2000-12-22
2002-05-21
Mullins, Burton S. (Department: 2834)
Electrical generator or motor structure
Dynamoelectric
Rotary
C310S061000, C310S065000
Reexamination Certificate
active
06392326
ABSTRACT:
BACKGROUND OF THE INVENTION
The invention relates to a structure and method for increasing the heat transfer rate particularly in the center and corners of endwinding cavities to increase overall cooling effectiveness in generator and rotor endwinding.
The power output rating of dynamoelectric machines, such as large turbo-generators, is often limited by the ability to provide additional current through the rotor field winding because of temperature limitations imposed on the electrical conductor insulation. Therefore, effective cooling of the rotor winding contributes directly to the output capability of the machine. This is especially true of the rotor end region, where direct, forced cooling is difficult and expensive due to the typical construction of these machines. As prevailing market trends require higher efficiency and higher reliability in lower cost, higher-power density generators, cooling the rotor end region becomes a limiting factor.
Turbo-generator rotors typically consist of concentric rectangular coils mounted in slots in a rotor. The end portions of the coils (commonly referred to as endwindings), which are beyond the support of the main rotor body, are typically supported against rotational forces by a retaining ring (see FIG.
1
). Support blocks are placed intermittently between the concentric coil endwindings to maintain relative position and to add mechanical stability for axial loads, such as thermal loads (see FIG.
2
). Additionally, the copper coils are constrained radially by the retaining ring on their outer radius, which counteracts centrifugal forces. The presence of the spaceblocks and retaining ring results in a number of coolant regions exposed to the copper coils. The primary coolant path is axial, between the spindle and the bottom of the endwindings. Also, discrete cavities are formed between coils by the bounding surfaces of the coils, blocks and the inner surface of the retaining ring structure. The endwindings are exposed to coolant that is driven by rotational forces from radially below the endwindings into these cavities (see FIG.
3
). This heat transfer tends to be low. This is because according to computed flow pathlines in a single rotating endwinding cavity from a computational fluid dynamic analysis, the coolant flow enters the cavity, traverses through a primary circulation and exits the cavity. Typically, the circulation results in low heat transfer coefficients especially near the center of the cavity. Thus, while this is a means for heat removal in the endwindings, it is relatively inefficient.
Various schemes have been used to route additional cooling gas through the rotor end region. All of these cooling schemes rely on either (1) making cooling passages directly in the copper conductors by machining grooves or forming channels in the conductors, and then pumping the gas to some other region of the machine, and/or (2) creating regions of relatively higher and lower pressures with the addition of baffles, flow channels and pumping elements to force the cooling gas to pass over the conductor surfaces.
Some systems penetrate the highly stressed rotor retaining ring with radial holes to allow cooling gas to be pumped directly alongside the rotor endwindings and discharged into the air gap, although such systems can have only limited usefulness due to the high mechanical stress and fatigue life considerations relating to the retaining ring.
If the conventional forced rotor end cooling schemes are used, considerable complexity and cost are added to rotor construction. For example, directly cooled conductors must be machined or fabricated to form the cooling passages. In addition, an exit manifold must be provided to discharge the gas somewhere in the rotor. The forced cooling schemes require the rotor end region to be divided into separate pressure zones, with the addition of numerous baffles, flow channels and pumping elements—which again add complexity and cost.
If none of these forced or direct cooling schemes are used, then the rotor endwindings are cooled passively. Passive cooling relies on the centrifugal and rotational forces of the rotor to circulate gas in the blind, dead-end cavities formed between concentric rotor windings. Passive cooling of rotor endwindings is sometimes also called “free convection” cooling.
Passive cooling provides the advantage of minimum complexity and cost, although heat removal capability is diminished when compared with the active systems of direct and forced cooling. Any cooling gas entering the cavities between concentric rotor windings must exit through the same opening since these cavities are otherwise enclosed—the four “side walls” of a typical cavity are formed by the concentric conductors and the insulating blocks that separate them, with the “bottom” (radially outward) wall formed by the retaining ring that supports the endwindings against rotation. Cooling gas enters from the annular space between the conductors and the rotor spindle. Heat removal is thus limited by the low circulation velocity of the gas in the cavity and the limited amount of the gas that can enter and leave these spaces.
In typical configurations, the cooling gas in the end region has not yet been fully accelerated to rotor speed, that is, the cooling gas is rotating at part rotor speed. As the fluid is driven into a cavity by means of the relative velocity impact between the rotor and the fluid, the heat transfer coefficient is typically highest near the spaceblock that is downstream relative to the flow direction—where the fluid enters with high momentum and where the fluid coolant is coldest. The heat transfer coefficient is also typically high around the cavity periphery. The center of the cavity receives the least cooling.
Increasing the heat removal capability of passive cooling systems will increase the current carrying capability of the rotor providing increased rating capability of the generator whole maintaining the advantage of low cost, simple and reliable construction.
U.S. Pat. No. 5,644,179, the disclosure of which is incorporated by reference describes a method for augmenting heat transfer by increasing the flow velocity of the large single flow circulation cell by introducing additional cooling flow directly into, and in the same direction as, the naturally occurring flow cell. This is shown in
FIGS. 4 and 5
. While this method increases the heat transfer in the cavity by augmenting the strength of the circulation cell, the center region of the rotor cavity was still left with low velocity and therefore low heat transfer. The same low heat transfer still persists in the corner regions.
BRIEF SUMMARY OF THE INVENTION
The above-mentioned needs are addressed by the present invention, in which enhanced cooling of generator rotors is achieved by the use of flow-through spaceblocks to promote better flow circulation in the normally starved cavity center and corners, thus increasing the flow heat transfer rate. The invention further relates to the use of coolant flow deflectors to enhance coolant flow into and from the cooling cavities.
Accordingly, as an embodiment of the invention, a gas cooled dynamoelectric machine is provided that comprises a rotor having axially extending coils, endwindings, and at least one spaceblock located between adjacent the endwindings so as to define first and second cavities adjacent the spaceblock between mutually adjacent endwindings. At least one of the spaceblocks has at least one passage defined therethrough to provide for cooling flow communication between the first and second cavities through the spaceblock. The number of passages in each spaceblock may be appropriately determined by the circumferential position of the spaceblock.
By providing a flow of cooling gas between the mutually adjacent cavities, the flow-through passage(s) improve the inherent gas flow patterns generated by the rotating endwindings. This results in increased heat removal capability while maintaining low cost, simplicity and reliable construction. In addition, the improved passive coolin
Jarczynski Emil Donald
Salamah Samir Armando
Turnbull Wayne Nigel Owen
Vandervort Christian Lee
Wetzel Todd Garrett
General Electric Company
Mullins Burton S.
Nixon & Vanderhye PC
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