CA1215097A - Brush mechanism for a homopolar generator - Google Patents
Brush mechanism for a homopolar generatorInfo
- Publication number
- CA1215097A CA1215097A CA000428867A CA428867A CA1215097A CA 1215097 A CA1215097 A CA 1215097A CA 000428867 A CA000428867 A CA 000428867A CA 428867 A CA428867 A CA 428867A CA 1215097 A CA1215097 A CA 1215097A
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- brush
- rotor
- slip ring
- strap
- current
- Prior art date
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Abstract
BRUSH MECHANISM FOR A HOMOPOLAR GENERATOR
ABSTRACT OF THE DISCLOSURE
A high-energy, high-current homopolar generator pulsed power supply system that is compact and field portable.
The power supply system includes a homopolar generator (HPG), an auxiliary supply and drive system, both mounted on a skid frame, and a control system coupled to the HPG
and drive system. The homopolar generator has a split rotor with insulation between the halves and a recess in the periphery. A stator ring and field coil, for producing a magnetic field through which the rotor halves make two simultaneous voltage-generating passes, are disposed within the recess in the rotor. Air-actuated brush mechanisms inside and outside the recess contact surfaces of the rotor and collect discharge current. The auxiliary supply and drive system includes a motoring system comprising hydraulic motors for driving the HPG to speed, a bearing lubrication system, a generator for energizing the field coil, and a brush actuator air supply system, all of which are driven by a prime mover. The control system comprises a logic controller for executing a prescribed sequence of steps including turning on the prime mover, initiating motoring of the HPG, energizing the field coil, and ini-tiating the discharge of electrical current.
ABSTRACT OF THE DISCLOSURE
A high-energy, high-current homopolar generator pulsed power supply system that is compact and field portable.
The power supply system includes a homopolar generator (HPG), an auxiliary supply and drive system, both mounted on a skid frame, and a control system coupled to the HPG
and drive system. The homopolar generator has a split rotor with insulation between the halves and a recess in the periphery. A stator ring and field coil, for producing a magnetic field through which the rotor halves make two simultaneous voltage-generating passes, are disposed within the recess in the rotor. Air-actuated brush mechanisms inside and outside the recess contact surfaces of the rotor and collect discharge current. The auxiliary supply and drive system includes a motoring system comprising hydraulic motors for driving the HPG to speed, a bearing lubrication system, a generator for energizing the field coil, and a brush actuator air supply system, all of which are driven by a prime mover. The control system comprises a logic controller for executing a prescribed sequence of steps including turning on the prime mover, initiating motoring of the HPG, energizing the field coil, and ini-tiating the discharge of electrical current.
Description
12~50~7 BAr~CROUND OF INVENTION
This invention was made at the Center for Electron mechanics of the University of Texas at Austin with support from the Department of the Army The present invention relates to pulsed power supply systems; and more particularly it relates to high-energy (multi-MJ), high current MA), pulsed power supply systems using inertial energy storage with homopolar conversion.
Inertial energy storage with homopolar conversion is known to be useful as a pulsed power supply. Such a home-polar generator HUG is shown, for example, in US. Patent No. 4,246,507. however, HUG power supplies have tended to be large, rather bulky, fixed laboratory installations.
An HUG, because it models electrically as a capacitor, admits to application as a power supply for electromagnetic (EM) propulsion systems for accelerating projectiles. Such EM propulsion systems include rail guns and launchers. In such applications, particularly rail guns, the power supply must be compact, and desirably is field portable. Prior HUG
power supplies due to their relatively large physical dimensions are not satisfactory.
Allis SUMMARY OF THE INVENTION
The present invention provides a compact pulsed power supply system utilizing a homopolar venerator. By reason of its compactness, the power supply is field portable The power supply system provides a high-energy (multi-MY), high-current mealtime) pulsed electrical output. The power supply is suitable for powering rail guns and the like The power supply utilizes a homopolar generator (HUG) comprising a rotor split into halves insulated from one another and having a recess formed in the periphery.
A stators and a field coil, for producing a magnetic field are disposed within the recess in the rotor. Further included in the HUG is means for collecting electrical discharge current from the rotor. An auxiliary supply and drive system it further included in the power supply. The auxiliary system comprises a prime mover for providing operating power, and includes a means for motoring the HUG
to speed. A control system coupled to the HUG and the auxiliary supply system controls the operation of the HUG
to obtain pulsed electrical power therefrom.
The control system includes a logic controller for executing a prescribed sequence of steps including turning on the prime mover, initiating motoring of the HUG, ever-giving the field coil, and initiating discharge of electric eel current.
The motoring means for the HUG includes a hydraulic motor coupled to the rotor. A hydraulic circuit, include in a hydraulic supply pump driven by the prime mover, ~2c controls the operation of the motor To permit tree-wheeling of the motor during discharge of the HUG, thy hydraulic circuit includes a relief valve bypassing the output of ho supply pump.
The HUG may also include a bearing system to facile-late rotation ox the wrier The auxiliary supply and drive system may further include a bearing lubrication system.
The current collecting means in the HUG may be brush mechanisms pneumatically actuated into contact with the rotor The auxiliary supply and drive system may further include a pneumatic control circuit for controlling the bra so mechanisms.
With particular reference to the subject matter claimed herein, the invention in one broad aspect pertains to a brush mechanism for a rotating electrical machine having a slip ring surface from which electrical current can be collected, comprising a brush for contacting a slip ring surface to collect current, and a brush strap having the brush attached to one end, for supporting the brush with respect to the slip ring surface, the brush strap comprising a plurality of laminations.
Another aspect of the invention pertains to a homopolar generator, comprising a stators for producing a magnetic field, a rotor having a slip ring surface defined thereon, for rotation within the stators magnetic field to generate an electrical potential, and a brush for contacting the rotor slip ring surface to collect current therefrom. Means are provided for repeatedly actuating the brush into contact with the rotor ~S~97 slip ring, and there is a brush strap having the brush attached thereto, for transferring current and for lifting the brush clear of the rotor slip ring after actuation. The brush strap comprises a plurality of laminations.
A still further aspect of the invention comprehends a homopolar generator, comprising a support structure with a stators assembly inwardly disposed within the support structure for producing a stators magnetic field. A shaft is mounted in the support structure and a rotor is carried on the shaft, the rotor including two mating rotor halves together defining a recess in the peripheral surface of the rotor, for fitting around the stators assembly to enclose the same. An inner brush mechanism is disposed within the recess in the rotor, for contacting a surface of the rotor defined by the recess to collect discharge current, and an outer brush mechanism is disposedwithln the support structure, for contacting the peripheral. surface of the rotor adjacent the recess to collect discharge current.
The invention also comprehends a brush assembly for a rotating electrical machine including a stators having a field coil for producing a magnetic field, a rotor for rotation within the stators magnetic field to produce electrical current, and a slip ring surface on the rotor. The assembly includes a brush pad comprising a plurality of adjacent brush pad blocks, for making contact with the rotor slip ring surface, and a brush strap connected to the brush pad, for biasing the brush pad blocks toward a retracted position away from the rotor slip ring surface. An actuator is provided for causing -PA-S`V97 deflection of the brush strap to simultaneously place the brush pad blocks in contact with the slip ring surface, the actuator including an elongated core structure having a passage there through for fluid communication, and an inflatable diaphragm comprising a synthetic rubber body molded around the core and bonded only to the top and sides thereof, whereby a diaphragm cavity is defined. Means are provided for introducing pressurized gas through the passage in the core and into the diaphragm cavity, to expand the diaphragm against the back of the brush strap and force the brush pad blocks into contact with rotor slip ring surface.
Various other aspects of the invention will become apparent from the more detailed disclosure which follows in conjunction with the appended claims.
~2'~5Q~7 BRIEF DESCRIPTION OF TOE DRYNESS
A written description setting forth the best mode presently known for carrying out the present invention and of the manner of implementing and using tip is pro-voided by the following detailed description of an thus-trative HUG power supply embodiment shown in the attached drawings wherein:
Figure 1 is a schematic diagram illustration of the HUG power supply;
Figure 2 is a graph of current and voltage versus time for the HUG power supply output upon charging of a specified load;
Figure 3 is a cross-sectional view of the single rotor HUG used in the HUG power supply;
Figure 4 is a cross-sectional view of the rotor assembly of the HUG power supply, including illustration of rotor hydraulic fitting;
Figure 5 is a plan view of the support structure for the rotor assembly;
Figure 6 is a side view of the support structure shown in Figure 5;
Figure 7 is a cross-sectional illustration of the thrust bearing assembly shown in Figure 3;
Figure 8 is a cross-sectional view of the stators assembly of the PUG power supply;
Figure 9 is a sectioned end view of three of the inner brush mechanisms used in the HUG power supply;
5{J I
Figure 10 is sectioned side view of one of the inner brush mechanism in the PI power supply;
Figure 11 it a sectioned end view of two of the outer brush mechanisms used in the PUG power supply;
Figure 12 is a sectioned side view of one of the outer brush mechanisms used in the HUG power supply;
Figure 13 is an illustration of the conductor cross-ovens for electrically connecting the two rotor halves in series;
Figure 14 it a schematic diagram of the air supply for the pneumatic brush mechanisms shown in Figures 9-12;
Figure 15 is a schematic diagram of the bearing lubrication system;
Figure 16 is a schematic diagram of the motoring system for bringing the PUG to speed;
Figure 17 is an illustration of the auxiliary and drive package for the HUG;
Figure 18 is a diagram of the control system; and Figure 19 is a flow chart of the control sequence for the HUG power supply (Figures aye & lob).
so DETAILED DESCRIPTION OF
ON ILLUSTRATIVE EMBODIMENT
A. HUG Power Supply General Configuration In Figure 10 there is presented a diagrammatic thus-traction of a homopolar generator (HUG) power supply system 10 providing in a compact, field-portable package, a high-energy mealtime, high-current (multi-MA) pulsed power supply.
HUG power supply system 10 comprises a homopolar generator (HUG) 12 in a single rotor configuration.
Output pulsed power from HUG 12 is available at terminals I HUG power supply 10 further includes auxiliary supply and drive package 15 for driving HUG 12 to speed and for supplying the required auxiliaries to HUG 12. An incitory-mentation and control system 18 provides control for the various components of the system 10 and disarms HUG 12 if a fault occurs The drive package 16 and HUG 12 are preferably mounted on a skid 13~ The control system is preferably provided in a standalone cabinet and connected by cable to the HUG and drive package.
By HUG Power Supply Operating Parameter As a sinqle-rotor machine and for an operating outer slip ring speed of 220 m/s (6,200 rum the electrical characteristics of HUG 12 are as summarized in Table I.
~12:~.5~
TALE I
stored Energy 6.2 Jo Rotational Speed 654 Rudy Capacitance 4,960 Internal Resistance 7.5 Internal Inductance OWE H
Voltage 50 V
Magnetic Flux Density 2 T
yield Coil 70,000 A-t lo Armature Current 750,00U A
Referring now to Figure 2, calculated curves of current and voltage versus time for HUG 12 when used to charge a load consisting of-a 5.4 micro henry, 27 micro-ohm inductive coil are shown C. Homopolar Generator Description 1. General Referring to Figure 3, HUG 12 is shown in cross-section. HUG 12 includes several major subassemblies, including: rotor-shaft assembly 20; stators 22; support structure 24; bearing systems 26, 28; inner brush mock-anises 30; outer brush mechanisms 32; and field coil 34.
Also shown is motor 36 for driving HUG 12 up to speed.
The rotor is the primary element of the machine; it stores the energy inertial and converts it to electric eel energy upon demand. lost of the fabrication labor involved in building this machine is applied to the stators assembly, which includes the field coils, brush mechanisms, I
~51:)~7 conductor, ferromagnetic twitter, and the support try-sure mounting the stators assembly relative to the rotor assembly The brush mechanisms are subjected to exterior dinarily difficult duty. The brushes must contact the rotor at its full diameter and thus at maximum surface speed. They must conduct extremely high currents at low voltage drop or maximum efficiency and minimum brush heating, They must operate in a relatively high magnetic field and thus are subjected to high J x forces during discharge. The outer brushes are the making switch for the machine and must simultaneously contact the rotor while remaining completely clear of the rotor before being actuated. Finally, the brush mechanisms must minimize and reject heating due to friction, interface voltage drop, and joule losses in order to minimize brush wear. Require-mints for the rotor assembly are that it be sufficiently stiff to allow operation at speeds up to 8,500 rum without encountering a critical frequency while being lightweight and compact. Because HUG power supply 10 is to be field portable, rolling element bearings, with minimal hydraulic power requirements are preferred. These bearings mutt be stiff; they are sub jetted to impact loads during a disk charge and might have to operate in stray magnetic fields that could cause electrical pitting.
Auxiliaries for HUG 12 include motoring supplies, lubrication systems, field-coil power supplies, and brush actuation.
The total weight of HUG 12 is approximately 3,500 lobs, and the machine fits into a 0.86 m diameter, O.g1 m long cylinder, a volume of O . 53 my
This invention was made at the Center for Electron mechanics of the University of Texas at Austin with support from the Department of the Army The present invention relates to pulsed power supply systems; and more particularly it relates to high-energy (multi-MJ), high current MA), pulsed power supply systems using inertial energy storage with homopolar conversion.
Inertial energy storage with homopolar conversion is known to be useful as a pulsed power supply. Such a home-polar generator HUG is shown, for example, in US. Patent No. 4,246,507. however, HUG power supplies have tended to be large, rather bulky, fixed laboratory installations.
An HUG, because it models electrically as a capacitor, admits to application as a power supply for electromagnetic (EM) propulsion systems for accelerating projectiles. Such EM propulsion systems include rail guns and launchers. In such applications, particularly rail guns, the power supply must be compact, and desirably is field portable. Prior HUG
power supplies due to their relatively large physical dimensions are not satisfactory.
Allis SUMMARY OF THE INVENTION
The present invention provides a compact pulsed power supply system utilizing a homopolar venerator. By reason of its compactness, the power supply is field portable The power supply system provides a high-energy (multi-MY), high-current mealtime) pulsed electrical output. The power supply is suitable for powering rail guns and the like The power supply utilizes a homopolar generator (HUG) comprising a rotor split into halves insulated from one another and having a recess formed in the periphery.
A stators and a field coil, for producing a magnetic field are disposed within the recess in the rotor. Further included in the HUG is means for collecting electrical discharge current from the rotor. An auxiliary supply and drive system it further included in the power supply. The auxiliary system comprises a prime mover for providing operating power, and includes a means for motoring the HUG
to speed. A control system coupled to the HUG and the auxiliary supply system controls the operation of the HUG
to obtain pulsed electrical power therefrom.
The control system includes a logic controller for executing a prescribed sequence of steps including turning on the prime mover, initiating motoring of the HUG, ever-giving the field coil, and initiating discharge of electric eel current.
The motoring means for the HUG includes a hydraulic motor coupled to the rotor. A hydraulic circuit, include in a hydraulic supply pump driven by the prime mover, ~2c controls the operation of the motor To permit tree-wheeling of the motor during discharge of the HUG, thy hydraulic circuit includes a relief valve bypassing the output of ho supply pump.
The HUG may also include a bearing system to facile-late rotation ox the wrier The auxiliary supply and drive system may further include a bearing lubrication system.
The current collecting means in the HUG may be brush mechanisms pneumatically actuated into contact with the rotor The auxiliary supply and drive system may further include a pneumatic control circuit for controlling the bra so mechanisms.
With particular reference to the subject matter claimed herein, the invention in one broad aspect pertains to a brush mechanism for a rotating electrical machine having a slip ring surface from which electrical current can be collected, comprising a brush for contacting a slip ring surface to collect current, and a brush strap having the brush attached to one end, for supporting the brush with respect to the slip ring surface, the brush strap comprising a plurality of laminations.
Another aspect of the invention pertains to a homopolar generator, comprising a stators for producing a magnetic field, a rotor having a slip ring surface defined thereon, for rotation within the stators magnetic field to generate an electrical potential, and a brush for contacting the rotor slip ring surface to collect current therefrom. Means are provided for repeatedly actuating the brush into contact with the rotor ~S~97 slip ring, and there is a brush strap having the brush attached thereto, for transferring current and for lifting the brush clear of the rotor slip ring after actuation. The brush strap comprises a plurality of laminations.
A still further aspect of the invention comprehends a homopolar generator, comprising a support structure with a stators assembly inwardly disposed within the support structure for producing a stators magnetic field. A shaft is mounted in the support structure and a rotor is carried on the shaft, the rotor including two mating rotor halves together defining a recess in the peripheral surface of the rotor, for fitting around the stators assembly to enclose the same. An inner brush mechanism is disposed within the recess in the rotor, for contacting a surface of the rotor defined by the recess to collect discharge current, and an outer brush mechanism is disposedwithln the support structure, for contacting the peripheral. surface of the rotor adjacent the recess to collect discharge current.
The invention also comprehends a brush assembly for a rotating electrical machine including a stators having a field coil for producing a magnetic field, a rotor for rotation within the stators magnetic field to produce electrical current, and a slip ring surface on the rotor. The assembly includes a brush pad comprising a plurality of adjacent brush pad blocks, for making contact with the rotor slip ring surface, and a brush strap connected to the brush pad, for biasing the brush pad blocks toward a retracted position away from the rotor slip ring surface. An actuator is provided for causing -PA-S`V97 deflection of the brush strap to simultaneously place the brush pad blocks in contact with the slip ring surface, the actuator including an elongated core structure having a passage there through for fluid communication, and an inflatable diaphragm comprising a synthetic rubber body molded around the core and bonded only to the top and sides thereof, whereby a diaphragm cavity is defined. Means are provided for introducing pressurized gas through the passage in the core and into the diaphragm cavity, to expand the diaphragm against the back of the brush strap and force the brush pad blocks into contact with rotor slip ring surface.
Various other aspects of the invention will become apparent from the more detailed disclosure which follows in conjunction with the appended claims.
~2'~5Q~7 BRIEF DESCRIPTION OF TOE DRYNESS
A written description setting forth the best mode presently known for carrying out the present invention and of the manner of implementing and using tip is pro-voided by the following detailed description of an thus-trative HUG power supply embodiment shown in the attached drawings wherein:
Figure 1 is a schematic diagram illustration of the HUG power supply;
Figure 2 is a graph of current and voltage versus time for the HUG power supply output upon charging of a specified load;
Figure 3 is a cross-sectional view of the single rotor HUG used in the HUG power supply;
Figure 4 is a cross-sectional view of the rotor assembly of the HUG power supply, including illustration of rotor hydraulic fitting;
Figure 5 is a plan view of the support structure for the rotor assembly;
Figure 6 is a side view of the support structure shown in Figure 5;
Figure 7 is a cross-sectional illustration of the thrust bearing assembly shown in Figure 3;
Figure 8 is a cross-sectional view of the stators assembly of the PUG power supply;
Figure 9 is a sectioned end view of three of the inner brush mechanisms used in the HUG power supply;
5{J I
Figure 10 is sectioned side view of one of the inner brush mechanism in the PI power supply;
Figure 11 it a sectioned end view of two of the outer brush mechanisms used in the PUG power supply;
Figure 12 is a sectioned side view of one of the outer brush mechanisms used in the HUG power supply;
Figure 13 is an illustration of the conductor cross-ovens for electrically connecting the two rotor halves in series;
Figure 14 it a schematic diagram of the air supply for the pneumatic brush mechanisms shown in Figures 9-12;
Figure 15 is a schematic diagram of the bearing lubrication system;
Figure 16 is a schematic diagram of the motoring system for bringing the PUG to speed;
Figure 17 is an illustration of the auxiliary and drive package for the HUG;
Figure 18 is a diagram of the control system; and Figure 19 is a flow chart of the control sequence for the HUG power supply (Figures aye & lob).
so DETAILED DESCRIPTION OF
ON ILLUSTRATIVE EMBODIMENT
A. HUG Power Supply General Configuration In Figure 10 there is presented a diagrammatic thus-traction of a homopolar generator (HUG) power supply system 10 providing in a compact, field-portable package, a high-energy mealtime, high-current (multi-MA) pulsed power supply.
HUG power supply system 10 comprises a homopolar generator (HUG) 12 in a single rotor configuration.
Output pulsed power from HUG 12 is available at terminals I HUG power supply 10 further includes auxiliary supply and drive package 15 for driving HUG 12 to speed and for supplying the required auxiliaries to HUG 12. An incitory-mentation and control system 18 provides control for the various components of the system 10 and disarms HUG 12 if a fault occurs The drive package 16 and HUG 12 are preferably mounted on a skid 13~ The control system is preferably provided in a standalone cabinet and connected by cable to the HUG and drive package.
By HUG Power Supply Operating Parameter As a sinqle-rotor machine and for an operating outer slip ring speed of 220 m/s (6,200 rum the electrical characteristics of HUG 12 are as summarized in Table I.
~12:~.5~
TALE I
stored Energy 6.2 Jo Rotational Speed 654 Rudy Capacitance 4,960 Internal Resistance 7.5 Internal Inductance OWE H
Voltage 50 V
Magnetic Flux Density 2 T
yield Coil 70,000 A-t lo Armature Current 750,00U A
Referring now to Figure 2, calculated curves of current and voltage versus time for HUG 12 when used to charge a load consisting of-a 5.4 micro henry, 27 micro-ohm inductive coil are shown C. Homopolar Generator Description 1. General Referring to Figure 3, HUG 12 is shown in cross-section. HUG 12 includes several major subassemblies, including: rotor-shaft assembly 20; stators 22; support structure 24; bearing systems 26, 28; inner brush mock-anises 30; outer brush mechanisms 32; and field coil 34.
Also shown is motor 36 for driving HUG 12 up to speed.
The rotor is the primary element of the machine; it stores the energy inertial and converts it to electric eel energy upon demand. lost of the fabrication labor involved in building this machine is applied to the stators assembly, which includes the field coils, brush mechanisms, I
~51:)~7 conductor, ferromagnetic twitter, and the support try-sure mounting the stators assembly relative to the rotor assembly The brush mechanisms are subjected to exterior dinarily difficult duty. The brushes must contact the rotor at its full diameter and thus at maximum surface speed. They must conduct extremely high currents at low voltage drop or maximum efficiency and minimum brush heating, They must operate in a relatively high magnetic field and thus are subjected to high J x forces during discharge. The outer brushes are the making switch for the machine and must simultaneously contact the rotor while remaining completely clear of the rotor before being actuated. Finally, the brush mechanisms must minimize and reject heating due to friction, interface voltage drop, and joule losses in order to minimize brush wear. Require-mints for the rotor assembly are that it be sufficiently stiff to allow operation at speeds up to 8,500 rum without encountering a critical frequency while being lightweight and compact. Because HUG power supply 10 is to be field portable, rolling element bearings, with minimal hydraulic power requirements are preferred. These bearings mutt be stiff; they are sub jetted to impact loads during a disk charge and might have to operate in stray magnetic fields that could cause electrical pitting.
Auxiliaries for HUG 12 include motoring supplies, lubrication systems, field-coil power supplies, and brush actuation.
The total weight of HUG 12 is approximately 3,500 lobs, and the machine fits into a 0.86 m diameter, O.g1 m long cylinder, a volume of O . 53 my
2. Rotor Rotor 24 in HUG 12 of thy field portable power supply being described is suitably 68 I in diameter, 40 cm thick, and shaped for a constant area magnetic flux path.
Rotor 24 it preferably made of steel, and weigh about 1j500 lobs. Rotor 24 is supported radially by heavy-duty needle bearings and axially by angular contact ball bearings, which bearings are provided in bearing systems 26, 28.
The stators support structure 25 houses the stators 22, the inner brush mechanism 30 and the field coils 34 (Figure 3). Therefore to assemble the machine, the rotor 20 must be split into halves and fitted around the stators In addition, the ability to take the rotor halves apart at any time it needed to perform maintenance on either the field coils or the inner brush mechanism. Furthermore, the rotor halves must be insulated from each other to per-mix two voltage generating passes through the externally applied magnetic field.
As the rotor is brought Jo speed in an HUG, the inner diameter (ID) of the rotor expands due to centrifugal forces. The shaft of the machine also experiences eon-trifugal growth, but not as much as the rotor ID. Cons-until a relative growth is present between the shaft and rotor ID at operating speeds; this growth increases with the square of machine speed. Therefore, an initial inter-furriness button the shaft and rotor is required in order to Anton contact at operating conditions.
heretofore, in most HUG machines, this initial inter-furriness is obtained by a thermal shrink fit of the shaft into the rotor. For shrunk fitting, the swat diameter is machined larger than the ID of the rotor to obtain the necessary interference. The shape is chilled reducing it diameter, while the rotor is heated; then the shaft it inserted into the rotor bore. When the ma trials return to room temperature (i.e., when there is no longer a thermal gradient), the interference between the rotor bore lo and shaft is established. However, in HUG 12, the rotor cannot be assembled solely by this method, since once the shrink fix is completed, the rotor cannot readily be separated from the shaft.
In view of these rotor assembly restrictions, the thermal gradient technique is used to fit one rotor half into place while using a hydraulic technique to fit the other rotor half into place. The thermal shrink fit is intended to be permanent, while the hydraulic fit can be disassembled. A drawing of the rotor assembly appears in Figure 4.
At the design speed of 220 m/s (6~242 rip the relative diametral growth between rotor bore and shaft is 0.0060 in Using a 100 percent factor of safety, the required initial interference is 0.0120 in. This is a conservative design that allows the machine to be run at speeds in excess of the design goals if desired. (At 300 so approximately 3,000 psi interference pressure will still be present between the shaft and rotor bore) lS~9'Y
The 0.012-in. interference produces an interference pressure of approximately 44,000 psi at the contacting surfaces. The maximum combined stress resulting rum this pressure occurs at the inner diameter of the rotor and is 7B,250 psi. At the design speed of 2~0 m/s this stress increases to a maximum value of 81~750 Sue This is a clear advantage of the interference fit; the maximum stress remains fairly constant over the operating speed range of the machine. The mechanism for this phenomenon is such that, at zero speed, the stresses present are due entirely to the initial interference between the shaft and rotor bore. As the machine speed increases, the inter-furriness is decreased, lowering the stress level due to the interference pressure. Concurrently, the stresses due to centrifugal effects in the rotor increase with speed, keeping the total maximum stress level fairly constant.
This effect is particularly advantageous from a fatigue standpoint because the cyclic stresses are minimized.
In order to shrink the right side AYE of the rotor onto shaft 21 a temperature differential large enough to offset the inn interference is required. For a 4-in diameter shaft, assuming that 0.001-in. clearance is surf-fishnet for assembly, the required temperature differential between shaft and rotor is 542F. This differential can be obtained by chilling the shalt, by heating the rotor, or by a combination of both.
To hydraulically assemble the left side of 20B of the rotor, the shalt 21 and rotor surfaces are not separated thermally as in a shrink fit, but by hydraulic pressure Sue supplied by an external pup. Thy pressure it introduced to the await rotor interface through a port 38 and oil grow 40~ ~ig~-pres~ure oil seal 42, 44 on both side of toe oil groovy prevent leakage frown the ends of the rotor. Once the pressure it applied, the rotor bore expand, thy shaft diameter shrinks, and a hydraulic pusher 46 is used to push the rotor half 20B onto the tapered shaft 21. A port 48 and oil groove 50 provided on the shrink-fi~ side AYE of the rotor enable disassembly lo of this rotor lye it necessary. Since seal are not required for rotor disassembly, they are omitted on the shrin~-fi~ side The hydraulic pressure necessary Jo separate the shaft and rotor born it the same as the final interference pressure (44,000 pal). A hand-operated pump pressure Prvduc~ Industries Model No. OH-102-60) and high pressure fitting manufactured by Sno-Trik) may be used; this pumping system it rated at a working pressure ox 60,000 psi. In addition, the seal for the system comprise Parker Pulp Type B seals (material: 90 dormitory Molt thanT~-4615)~ and Parker Modular backup rings (material Palmetto z-4652).
The hydraulic pusher 46 it designed to force the rotor onto the shaft while the rotor and shaft surface are separate by the high pressure hydraulic system. The inner cylinder of the pusher attaches to the shaft; the outer cylinder, actuated by a low-pressure pump (South-western Controls twiddle No. SC-40-500-3, maximum pressure 5,000 psi), presses against the rotor face and provide :121~i~97 the force to push Abe rotor onto thy shaft. an ester ally applied pressure of 44,000 pi a thy ~haft-rotor int~rfa~e, the force required Jo push the rotor onto the shaft 77,500 lb tithe shaft an rotor interface ha a 1 per side taper). At the present hydraulic pusher dummy swoons the low-pressure pump will have to produce 3~800 pi to achieve the 77,500-lb force.
In order to have two voltage generating passes through the motion externally applied magnetic yield, the rotor halves must be insulated from one another. The scheme to accomplish this it illustrated in Figure JO
On the -shrink fit rotor half AYE, a ceramic material 52 will insulate between that rotor half and the shaft.
In addition, the ceramic will be used to insulate between rotor face. Because the ceramic will insulate between the shaft and rotor on one side, it will have Jo with-stand some demanding mechanical tresses Kit will undergo the full interns pressure) without sacrificing it required electrical properties.
The ceramic coating may be aluminum oxide, such a Allah available prom Norton Industrial Ceramics Division.
The coating it preferably applied by a flame-spraying technique such as that conducted by the F. W. Garter Co., 3805 Lamar, Houston, Texas. After application, the ceramic coating it impregnated with silicon resin such as General Electric SR182S the resin it allowed to sure and is then around to dimension.
~2~5(:~7
Rotor 24 it preferably made of steel, and weigh about 1j500 lobs. Rotor 24 is supported radially by heavy-duty needle bearings and axially by angular contact ball bearings, which bearings are provided in bearing systems 26, 28.
The stators support structure 25 houses the stators 22, the inner brush mechanism 30 and the field coils 34 (Figure 3). Therefore to assemble the machine, the rotor 20 must be split into halves and fitted around the stators In addition, the ability to take the rotor halves apart at any time it needed to perform maintenance on either the field coils or the inner brush mechanism. Furthermore, the rotor halves must be insulated from each other to per-mix two voltage generating passes through the externally applied magnetic field.
As the rotor is brought Jo speed in an HUG, the inner diameter (ID) of the rotor expands due to centrifugal forces. The shaft of the machine also experiences eon-trifugal growth, but not as much as the rotor ID. Cons-until a relative growth is present between the shaft and rotor ID at operating speeds; this growth increases with the square of machine speed. Therefore, an initial inter-furriness button the shaft and rotor is required in order to Anton contact at operating conditions.
heretofore, in most HUG machines, this initial inter-furriness is obtained by a thermal shrink fit of the shaft into the rotor. For shrunk fitting, the swat diameter is machined larger than the ID of the rotor to obtain the necessary interference. The shape is chilled reducing it diameter, while the rotor is heated; then the shaft it inserted into the rotor bore. When the ma trials return to room temperature (i.e., when there is no longer a thermal gradient), the interference between the rotor bore lo and shaft is established. However, in HUG 12, the rotor cannot be assembled solely by this method, since once the shrink fix is completed, the rotor cannot readily be separated from the shaft.
In view of these rotor assembly restrictions, the thermal gradient technique is used to fit one rotor half into place while using a hydraulic technique to fit the other rotor half into place. The thermal shrink fit is intended to be permanent, while the hydraulic fit can be disassembled. A drawing of the rotor assembly appears in Figure 4.
At the design speed of 220 m/s (6~242 rip the relative diametral growth between rotor bore and shaft is 0.0060 in Using a 100 percent factor of safety, the required initial interference is 0.0120 in. This is a conservative design that allows the machine to be run at speeds in excess of the design goals if desired. (At 300 so approximately 3,000 psi interference pressure will still be present between the shaft and rotor bore) lS~9'Y
The 0.012-in. interference produces an interference pressure of approximately 44,000 psi at the contacting surfaces. The maximum combined stress resulting rum this pressure occurs at the inner diameter of the rotor and is 7B,250 psi. At the design speed of 2~0 m/s this stress increases to a maximum value of 81~750 Sue This is a clear advantage of the interference fit; the maximum stress remains fairly constant over the operating speed range of the machine. The mechanism for this phenomenon is such that, at zero speed, the stresses present are due entirely to the initial interference between the shaft and rotor bore. As the machine speed increases, the inter-furriness is decreased, lowering the stress level due to the interference pressure. Concurrently, the stresses due to centrifugal effects in the rotor increase with speed, keeping the total maximum stress level fairly constant.
This effect is particularly advantageous from a fatigue standpoint because the cyclic stresses are minimized.
In order to shrink the right side AYE of the rotor onto shaft 21 a temperature differential large enough to offset the inn interference is required. For a 4-in diameter shaft, assuming that 0.001-in. clearance is surf-fishnet for assembly, the required temperature differential between shaft and rotor is 542F. This differential can be obtained by chilling the shalt, by heating the rotor, or by a combination of both.
To hydraulically assemble the left side of 20B of the rotor, the shalt 21 and rotor surfaces are not separated thermally as in a shrink fit, but by hydraulic pressure Sue supplied by an external pup. Thy pressure it introduced to the await rotor interface through a port 38 and oil grow 40~ ~ig~-pres~ure oil seal 42, 44 on both side of toe oil groovy prevent leakage frown the ends of the rotor. Once the pressure it applied, the rotor bore expand, thy shaft diameter shrinks, and a hydraulic pusher 46 is used to push the rotor half 20B onto the tapered shaft 21. A port 48 and oil groove 50 provided on the shrink-fi~ side AYE of the rotor enable disassembly lo of this rotor lye it necessary. Since seal are not required for rotor disassembly, they are omitted on the shrin~-fi~ side The hydraulic pressure necessary Jo separate the shaft and rotor born it the same as the final interference pressure (44,000 pal). A hand-operated pump pressure Prvduc~ Industries Model No. OH-102-60) and high pressure fitting manufactured by Sno-Trik) may be used; this pumping system it rated at a working pressure ox 60,000 psi. In addition, the seal for the system comprise Parker Pulp Type B seals (material: 90 dormitory Molt thanT~-4615)~ and Parker Modular backup rings (material Palmetto z-4652).
The hydraulic pusher 46 it designed to force the rotor onto the shaft while the rotor and shaft surface are separate by the high pressure hydraulic system. The inner cylinder of the pusher attaches to the shaft; the outer cylinder, actuated by a low-pressure pump (South-western Controls twiddle No. SC-40-500-3, maximum pressure 5,000 psi), presses against the rotor face and provide :121~i~97 the force to push Abe rotor onto thy shaft. an ester ally applied pressure of 44,000 pi a thy ~haft-rotor int~rfa~e, the force required Jo push the rotor onto the shaft 77,500 lb tithe shaft an rotor interface ha a 1 per side taper). At the present hydraulic pusher dummy swoons the low-pressure pump will have to produce 3~800 pi to achieve the 77,500-lb force.
In order to have two voltage generating passes through the motion externally applied magnetic yield, the rotor halves must be insulated from one another. The scheme to accomplish this it illustrated in Figure JO
On the -shrink fit rotor half AYE, a ceramic material 52 will insulate between that rotor half and the shaft.
In addition, the ceramic will be used to insulate between rotor face. Because the ceramic will insulate between the shaft and rotor on one side, it will have Jo with-stand some demanding mechanical tresses Kit will undergo the full interns pressure) without sacrificing it required electrical properties.
The ceramic coating may be aluminum oxide, such a Allah available prom Norton Industrial Ceramics Division.
The coating it preferably applied by a flame-spraying technique such as that conducted by the F. W. Garter Co., 3805 Lamar, Houston, Texas. After application, the ceramic coating it impregnated with silicon resin such as General Electric SR182S the resin it allowed to sure and is then around to dimension.
~2~5(:~7
3. Support Structure and Bearings Systems The PUG 12 support structure 24 is shown in detail in Figures 5 and 6. The support structure provide alignment and structural integrity needed for the rotor. The sup-port structure also provides a mounting attachment for the stators assembly.
Support structure 24 is made entirely of aluminum and comprises a one-inch thick aluminum ring 54. Preferably, the ring 54 is shrunk fit onto the stators 22. A plurality of T-shaped crossbars 56 are welded to ring 54. Two conic eel end plates say 60 are bolted to the crossbars, and carry stainless steel bearing housings 62, 64.
Bearing system 28 (Figure 3) is a non-thrust bearing, whereas bearing system 26 in housing 62 it a thrust bear-in. Roth bearing systems have radial bearings of heavy-duty needle bearings which are suitably Torrington No.
HJ-445628 bearings. These bearings include both the inner and outer race and a cage to accurately guide the bearing rollers. In Figure 7, there is a cross-sectional view of the thrust bearing system 26, showing both the needle roller radial bearing 64 common to the non-thrust bearing system 28 and the duplex angular contact ball thrust bear-in 66~
Needle bearings are used because of their inherently high stiffness. because the rolling elements (the needles) are radially thin and are relatively long axially, they are much stiffer than comparable ball bearings. In add-lion, the fact that the rollers have line contact with each race (rather than point contact as in ball bearings) SUE
also adds kiwi their 'siphon. The calculated ~iffnes~
for each of the joy bearing. I 7.23 x 10~ lb/in at a reload provided by like rotor weight.
It us important hut the bearings in the HUG 12 machine be preluded to prevent skidding at high speed.
In the radial bearing this reload it provided by the weight of the rotor approximately 800 lb per Bering The radial bearing have a catalog-ra~ed maximum steed of 6,150 rum however overspending of rolling element bear-lo ins is an acceptable practice provided they receive adequate lubrication and cooling The radial bearings have a calculated h-10 life of 1,850 hour a continuous operation at 6,300 rip Referring to Figure 7, the thrust bearing system 26 it shown in pagan with shaft 21 inserted therein Additionally, figure 7 shows stainless steel bearing housing 62 bolted to conical end 58 of thy support struck lure I by bolts 68. Conical end 58 is further shown to inlay a steel mounting sleeve 70 pressed therein. Con-netted by bolt 72 it a bearing housing cap 74.
The angular contact ball bearing 66, suitably SO
No. 7411 B, art duplex mounted back-to-bacX on one end of the machine. Attaining sufficient stiffness from the annular contact bull bearings I is accomplished by pro-loading, To prowled these bearings, a shim can be placed between the outer races of the two back-to-back bearing.
Then by clamping the two bearings together on the shaft with a nut, the reload can be established. The amount of reload attained can be adjusted by the thickness of the slough hi between ho bearing. The tradeoff to be made forth thrust bearing it Tiffany versus luff Increasing the reload increase the stiffness while depressing the bearing Lowe. At an 8,000-lb reload (8.5 x 106 lb/in s~iffnesR~, the calculated L-10 life of the thrust bearing_ pair is 97 his. Thy rated speed limit of the bearing it approximately 5,100 rum; however, overspending is accept able when adequate lubrication and cooling are provided.
Lubrication and cooling is provided by an injection lo of oil into the bearing rolling element. Oil flow is provided through lubrication oil inlet 75 to oil injection passage 76 in bearing housing 62 and housing cap 74. At the end of each pa sage is a nozzle 78, which may suitably TM
be a 0.055-in-diameter fluid restructure (Lee Plug Jet Part No. 187002-005)~ A shown, there are two ox is provided for each wide of etch set of bearing roller elements Jo that the bearing will receive lubricant in case of a clogged restructure Also in bearing housing 62 and housing cap 74 are oil jump passages 80 leading to a lubrication oil sup outlet 82. Preferably, the lubrication oil will be passed through at a total flow rate ox 10 gal/min. Oil scavenging is at 25 gamin to prevent oil from pooling in the beaning housing and keep viscous friction losses to a m~nimumr There further shown in Figure 7 a clamping nut 84 on the end of shaft 21 and a drive coupling 86. Driving motor 36 figure 3) it partially shown coupled through mounting flange 88 and spacer 90 to housing caps 74 and d r ivy coup i no 8 6 .
I. Stutter Assumably The talon assembly for PUG 12 it shown it detail in Figure 8. the stators assumably my be regraded a including the ferromagnetic stutter ring 22, the field coil 34, and the aluminum T-bar3 56 figure S) for connecting the pharaoh magnetic stators rings to the support structure. Addition-ally, the stators assembly include inner brush ring 92 and outer brush ring 94. Connecting to the inner brush ring are current collecting conductors AYE and 968.
lo The ferromagnetic stators 22, preferably of A-36 steel, conducts the magnetic field from one rotor face to the other Since the inner brush mechanisms are air-actuated, as will be described, an air manifold 98 is provided through staSor ring 22 and in communication with brush air inlet 100. A noted in the ascription relating to the support structure 24 shown in Figures S and it, aluminum ring 54 is shrunk onto stout ring 22. Additionally, the aluminum ring 54 is pinned to the Starr by steels studs 102.
As shown in Figure 8J the T-bars 56 are bolted by stainless steel bolts 104 to the aluminum ring 54. The bolts 104 are modified so as Jo register with and have inserted in Tao end thereof the steel stud 102. To further enhance the connection of the T-bar 56 to aluminum ring 54, dowel pin 106 are inserted. through the T bar and into ring 54. Bolts 104 are preferably I inch in diameter, and dowel pins 106 are preferably 3~8 inch in diameter. It is also preferred that compensating conductor go be held firmly to the steel stators ring by, for example nylon fathead screws (not shown).
so Field coil 34 comprise two coil Hoyle AYE and 34~, preferably designed for 70,000 amp-turns a a magnetic air yap of 0.5 inch. Because of it interior location, field coil 34 mutt be as thin as possible radially. Accordingly, the coy pulsed rather Han steady state. Each field coil half ha 156 turns of 0.23 inch square solid copper conductor insulated with a heavy coat of armored polyp thermalized insulation.
The terminals 108 of the coil are plug-in-Multilam connectors located between the two coil halves AYE and 34B. Terminal access is through the center of the stators which minimize field dissymmetry. The coils can be run either in series or in parallel and require a 30-V, 417-amp power supply per coil at the 70,000 amp-turn level. In parallel the 30-V requirement is very nearly compatible with an Army 28-V generator.
The field coil is fabricate a follows. The square conductors art half-lap-wrapped with 0.OOS-inch thick, 1/2-inch wide fiberglass tape. Then the two conductors are wound separately onto the two halves of a vacuum impregnation mold. the terminals are then brazed into place, the two halve are bolter together, an the entire structure it vacuum impregnated with a low viscosity, 250F, elevated-temperature-cure epoxy.
JO Brush mechanisms Collection and transfer of current from the high-surface-speed slip rinse is accomplished in PUG 12 by the inner brush mechanism Sheehan in r issues 9 and 10 and the L5~97 outer brush mechanism shown in Figures 11 and 12. This is a demanding task, and because ox the A-I-R configure-lion of the machine additional constraints are placed on the inner brush mechanism in regard to radial height.
That is the radial height must be minimized because the brush and its actuator directly reduce the flux-cutting area of the rotor, which in turn reduces the generated machine voltage. In HUG 12, the outer brush mechanism is also subject to additional considerations since it is lo being used as the current mixing switch.
Referring first to Figures 9 and 10, the inner brush mechanism 30 is shown in position relative to the stators and the rotor In Figure 9, the brush mechanism is shown in an end view (along with two other brush mechanisms 31 and 33). In Figure 10, brush mechanism 30 is shown in a side view The inner brush mechanisms are shown in Figures 9 and 10 connected to the inner brush current collecting conduct ion ring 92 by fathead screws 110. The brush pads 112 which make contact to the rotor inner slip ring surface 19, are preferably 1/8 inch thick by 3/4 inch long by 7/16 inch wide sistered copper-graphite blocks. Each brush pad is attached by silver brazing to a brush strap 114 that carries the current to the brush ring.
The brush straps must conduct extremely high currents without becoming excessively hot. They must operate in a relatively high magnetic field and thus are subjected to high electromagnetic forces during a current pulse. The strap must provide sufficient elastic spring force to lift -lo-~2~51~9~
the brush clear of the slip ring. Finally and most important, the strap must provide a dynamically stable brush mount sufficiently soft radially Jo allow the brush to track the slip ring but 5uffi~iently stiff axially and circumferential to ensure that the brush return to exactly the same orientation on the rotor after each actuation As brush 112 wears away with use, it is desirable to compensate for this wear so that the brush is retracted the same distance from the rotor slip ring surface through-out its useful lifetime, ensuring consistent brush actual lion times and down forces Unfortunately for compact, high packing factor brush assemblies that require short brush straps, the bending stress in the solid copper strap is exceeded during brush actuation, causing the brush strap to yield in the "brush down position and resulting in a 108s of ability to retract the brush. Conventionally hardened copper (hardened by cold working or rolling) cannot be used to raise the yield strength of the brush strap since it will be annealed during the process of brazing the brush strap to the brush.
As a solution, brush straps 114 are laminated.
laminated brush strap is both dynamically stable and stiff in the axial and circumferential planes. This means that the brush will swing through the same arc and maze contact in the same location with each actuation. This it important because as the brush wears it makes better con-tact, but it must make contact in the same orientation with the slip ring during each cycle. The brush strap mutt radially soft because whatever mechanist is act-axing the brush must overcome the strap stiffness as well as provide adequate down forte of thy brush onto ho slip ring however, the strap must be thick enough to conduct the current without an excessive temperature rise. ~150 it must be strong enough to lift the brush clear of the slip ring; thus it should not yield during actuation.
These problems were resolved by laminating the brush strap. By maying the laminations different thicknesses and out of different types of copper (i.e., beryllium, ETA
110, or dispersion strengthened copper, which is not annealed during brazing 9 various combinations of stiff-news, cross-sectional area and strength can ye obtained.
A typical example is a strap made of two 0~031-inch-thick ETA 110 copper straps and one 0.031-inch-thick dispersion strengthened copper strap all 7/16 of an inch wide.
Laminated brush straps 114 will each conduct 3,000 amperes for 0.25 seconds with a 15F~temperature rise.
It take approximately S pounds to move the brush 1/16 of an inch, which provides a lift force of approximately 4.5 pounds. Each strap 114 is approximately one inch long.
The discharge currents in the brush straps 114 react with each other and wit the excitation magnetic field to lift the brushes off the slip ring during a discharge.
Therefore current compensating straps 116 are provided to counteract these of cats. Straps 116 increase the brush down force as the current magnitude increases because the currents flowing in opposite directions repel each other.
This guarantees maximum gown force at peak current.
So Spacer 118 are alto shown on screws 110 between adjacent compensating straps.
Brush pads 12 are downwardly actuated to contact with thy lip ring of the rotor and a down force it applies to maintain brush contact. Actuation of each brush 112 it by a brush actuator 120. The actuator come proses an inflatable diaphragm that forces the brush down. As indicated, one actuator provides simultaneously a down force to a row of brushes ( F inure 1 0 ) The die-frog 122 is suitably synthetic rubber neoprene) molded around a metal brass) core 124, and bonded by a vulcan Nissan process to the top and sides thereof but not to the bottom.
The diaphragm t22 is secured by fathead screws 126 to a fiberglass dovetail mount 128. The mount engages a mating mount t30 carried on the end ox screws 110.
Pressurized gas at about 90 psi is introduced through a hole in the metal core and into the diaphragm cavity. This expands the diaphragm against the back of strap 114 and forces brush pad 112 into contact with the rotor slip ring. The pressurized gas is introduced via inlet tube t32.
Referring now to Figures 11 and 12, outer brush mechanism 32 and adjacent brush mechanism 35 are shown connected by screws 134 to conductor ring 94 and in position adjacent rotor outer slip ring surface 29. Each brush mechanism comprises a brush pad 136 for awaking contact with the rotor slip ring surface. The brush pads are preferably sistered copper-graphite blocks having ISSUE
dimension of I inch in thickness by 3/4 inch in length by 7/16 inch in width. Each brush pad is attached by silver brazing Jo a laminated brush strap 138. Brush straps 138 are a composite famine ion of two 1/32 inch thick annealed copper straps and one 1/32 inch thick disk pension strengthened copper strap.
To prevent discharge currents in brush straps 138 from reacting with each other and with the excitation magnetic field t current compensating straps 140 are provided. Straps 140 extend between adjacent screws 134, and spacers 142 are placed between the straps on each screw.
Deflection of brush straps 138 to place brush pads 136 in contact with the slip ring surface 29 is by await-atop devices 144 carried on the ends of screws 134. The actuator devices comprise a neoprene diaphragm t46 that inflates when pressurized, forcing the brush pads down.
As shown in Figure 12, each actuator provides a down force simultaneously to a row ox brush pads 1360 The diaphragm 146 is molded around a metal (brass) core 148. The metal core is further connected to a manifold 150 having Ann inlet 152 therein. Pressurized gas (air) at 90 psi it suitable for actuating brush actuator devices 144. Actual lion time is on the order of about three millisecond.
The down force applied is about 4-1/2 to 5 lobs.
To electrically connect the two rotor halve in series, which effectively doubles the HUG open-circuit voltage, conductor cross-over structure is required Referring to Figure 13, there is shown a portion of thy :iL2~1LS~97 exterior of HUG 12u pa view art oros~-sv~r bars 154 9 along with arrows inditing discharge current. Each cross over bar arrangement empower two copper Brie 5~8 inch thick by 1-3/8 inch wide It bar 154 are nested between the aluminum T-bars 56. The bars 154 are attached to conductors 94 and 96 (Figure 8) by silver brazing.
Terminals 156 are also shown in Figure 13 D. Auxiliary Supply an Drive System The auxiliary supply and drive system include the lo brush actuator air supply (Figure 14), the bearing Libra-cation system figure 15), and the motoring system (Figure US). These subsystems are shown in Figure 17 in an arrangement on a skid mount. All subsystem are powered by a prime mover, e.g., any motor, engine, or turbine capable of 200 ho a 1800 rum. Suitably, a squirrel-cage induction motor such as Lineguar3M445T is used. It is a drip proof motor with service factor of 1.15 and varnished windings requiring one 460v three-phase lingo Its full-I load speed it 1,780 rum, and its full-load torque is 600 f tubs .
1. Brush Air Supply Brushes 30, 32 figure 3) for HUG 12 are actuated by compressed air. The pneumatic control circuit shown it Figure 14 will supply the brush actuators with 90 pus compressed air The air volume of the inner brush mock anise 30 is approximately 100 in, roughly 1/2 gal. The 2 So I
volume of the outer brush mechanist 32 it approximately 190 in, roughly one gal, The total ye I idea to handle up to 150 pi, although normal operation it antic-pawed in thy vote of 90 psi.
A single stage two-cylinder air comparer pump 160 in Figure 14 it belt-driven from the prime Dover 162~ The compressor 160 (Spiders) is rated to t50 pi maximum pressure and delivers 5.70 aim fret air at 100 pal and 735 rum. At 1 no psi this corresponds to 6.25 gamin compressed air. This means the accumulators 172, 174 con be charged to 100 pi in under one minute. The compressor require up to 2 ho when not unloaded.
Once the accumulators have been charged the compressor will be unloaded (outlet vented to atmosphere) by a con-Tony run unloader control 164. The unloader Control Device 55X709 us rated to 250 psi maximum pressure at 20 efmO Control pressure are adjustable to 135 psi. The unloader also act a a check valve. Down line from the unloader is a SO pi air filter 166 to prevent compressor oil from entering the brush mechanisms. The air filter Speedair~M2Z328 go razed a 110 aim with 40-micron lit-traction.- After filtration, two 125 psi pressure Wrigley-tars 16B, 170 provide control of accumulator pressure.
The regulator SpeedaiTM lZ~38 it rated at 250 pi maximum pressure at 18 aim. Compressed air is stored in two 3-gal accumulator 172, 174. Brush air pressure control it accomplishes with your 300 psi normally closed, two-way solenoid valves 176, 17~t 180, 182. These valve have a l-in port, assuring quick pressurization and venting.
US
Thy valve are ~kkom~tic ~S430-~ semi direct lift solenoid equipped with manual opening h~ndwheel~.
I Bearing Lubrication System The rolling eleven Byron 26, 28 (Figure 3) used in the HUG 12 require oil jet for proper lubrication and cooling. Sufficient scavenging capacity it required to prevent accumulation of lubricant in the bearing and sup covet.
The lubricant preferred is æ parafinic ~ineral-based lo oil with foam suppressant having a viscosity of 100 SO
at 150-F. This lubricant will carry away a significant portion of bearing and seal drag heat output. Bearing losses are emoted at 7.7 ho total; seal losses are east-mated at 7.2 ho total. These losses are nearly linearly dependent on speed and represent worst-case figures A schematic of the bearing lubrication system it shown in Pure 15. The supply and scavenge pumps are belt-driven by the prime mover 162. The bearing oft supply pressure is provided by three 3.2-gpm Gyrate pumps A
noble H3H3 GerotoTMdouble pump 184 supplies pressure to the thrust duplex pair 183 and the thrust end radial bearing 185. Redundant rut assure lubricant flow to both bearings in case of failure of either pump. The oil pressure for the non-thrust-end radial bearing 1~1 is provided by one 3.2-gpm pump of a Double A H3H3Dl Gyrate triple pump 186. This pump is driven by a through shaft from pump 1 a through a flexible coupling. The other 3.2-gpm pump is used to scavenge the outer non-thrust-end US
jump 187~ Thy small 1-gpm pump it used to sieving thy inner hru~t-end sup 189.
Thy third pump 188 it by driven by thy prime Dover.
The Double ~5~5 Juror double pump scavenge both middle jump 191 192 with a keep of 5.0 gyp each.
Driven from the third pump through a flexibly coupling, the fourth pup 190 it a Double A ~12D1 Jury doubly pump. The 13-gpm pump scavenges the outer throned sup OWE The 1-gp~ pump scavenges the non-thrust~end lo inner sup 195.
overall supply flow is 9.6 gyp while overall scavenge flow it 28.2 gym. This result in a scavenge-to-supply ratio of 2,9.
Flow from the scavenge pumps it directed to a toggle reservoir 192 for deforming. From the res~rvoirD oil it pulled through an oil cooler 194 and filter 196 ho the supply pumps. The Perfex SUB I oil cooler it rated at 20 hp/100~ITD at 9.6 gym. The cooler has minimal pressure drop at this low flow. The yoke DEFY 330 oil filter it rated for 46 pi at JOY pi and provides 5-micron ration. Should the pressure drop of these components cause cavitation in the supply pumps, they can be moved to the scavenge to reservoir line. This location would be undesirably as tooling capacity will drop due to air entrapment in the oil cooler. However, the system should be able to maintain the machine at speed indefinitely . Motoring System wow hydraulic motor AYE, 36B figure 3), one on each end of the shaft, will be used to bring the A-I-R HUG 12 Sue to speed. VolvoMF11~-19 hydraulic motor are preferred to obtain a motoring time ox approximately 2 yin Jo reach 6,300 rip the design speed. The hydraulic ~lrcuit, shown schematically in Figure 16~ must supply each hydraulic motor with 32 gal of OWE psi hydraulic fluid per min.
In the schematic, new ANSI fluid power symbols are used to-identify the compo~ent5.
The hydraulic motor AYE, 36~ in Figure 1 it, have 1.16 in3/rev displacement, a maximum continuous operating lo pressure of 5,000 psi, and a listed maximum operating speed ox 7,500 rum. They have a constant output torque of 922 in-lb~ each and require 31~6 gamin each at 6,300 rip before mechanical and volumetric efficiencies are included.
Estate mechanical efficiency is 90 percent and estimated volumetr~e efficiency is 99 percent.
The hydraulic supply pump 198 is a ~ydromati~ AVOW 16~
DRY variable displacement, flange-mounted, bent axis, axial piston pump. It has displacement of 164 crave, Max-mum speed of 2,000 rum, adjustable constant pressure con-trot, and mechanical stroke limiter. It has a theoretical output of 77.t gym at 1, 780 rum, which becomes 74.8 go with 3 percent displacement losses. Thus thy hydraulic circuit ha a 15 percent martin of safety including menu-lecturers losses, for motoring to 6,300 rum.
A separate cooling and filtering circuit will cool the hydraulic fluid during motoring and idling. The cooling pump 200 it 40 gym flange-mounted gear pump.
The HydrecBM2025 fixed displacement pump it rated for 1, 800 rum and 750 psi although system pressure it limited it 100 pal by on nine relief valve 202. This Rowley valve protect ho oil cooler 204 and filter 206 Roy o'er pressures during syrup The Circle Siam in-line relies Allah 202 it rated for 40 gym an 1,200 pi Mom The rocking prowar it adjustable from 85 pi to 120 psi. The Pere~MS~-6~ oil cooler 2~4 way sized to disk-pate the heat generated from the hydraulic braking valve at 75 hp/100 vindicated temperature difference). It ha an estimated pressure drop of 40 psi, a maximum operating lo pressure of 150 psi, and a maximum flow of 72 gyp The GreseTMF401 filter 206 provide 10-micron filtration. The filter it rated for 75 gym at 200 psi and ha a 15 psi bypass spring.
After motoring to speed the pilot-operated relief valve 20~, ~10 will be opened to the reservoir by two-way solenoid valve 212, 214. This will allow freewheeling of the hydraulic motors and will bypass the main supply pump output to the reservoir during discharge or idling condo-lions. The Victor Fluid Powe~FMVR323105 pilvt-operated relief valves 208, 21~ operate as a 6,000 psi relief valve until vented my the wow solenoid valve. The valve rated at 10,000 psi maximum pressure at 50 gym flow The Circle Sea~MSV460 two-way solenoid valves 212, 214 ore rated at 6,000 psi maxim pressure. They have a I of 0.64 which assures very low vent pressure. These valve are normally open so that in the event of loss of power the relief v21ves will fail open.
The hydraulic braking valves 216, 218 are 2,500 pus pilot-operated relief valves vented by normally open solenoid valve Swahili o the frill relief valve.
The Tickers CT5-10 ~ol~no~d-controlled relief valve combine both in one unit. These valves were selected for their low venter pressure drop of 25 psi at 35 gym.
higher pressure drop would adversely aft the hydraulic motors These valves will be open except during emergency shutdown situation. When closed, these braking valves will stop the rotor in less than 3 mix from 6,300 rum.
The hydraulic fluid reservoir 220 has two deforming lo plates and a capacity of 10 gal. It will be constructed from welded aluminum pipe and sheet stock. The high-pressure feed hose 222 will be 1.00-in ID, 1.91-in ODE
sprawler double-armored hydraulic hose. It is rated at 5,000 psi working pressure and 20,000 psi minimum burst pressure. the return hove 224 will be 1.25-in-ID, 1.91-in ODE 4-spiral-wire, double-armored hydraulic hose. It is rated at 3,000 psi working pressure and 12,000 psi minimum burst pressure. The cooling circuit hose 226 will be 1.38-in ID, 1.75-in ODE single-wire braid hydraulic hose.
it it rated at 500 psi worming pressure and 2,000 pus minimum burst pressure. The hydraulic medium chosen for the system is Rondo Oil HD32. It is a high-grade mineral-based hydraulic fluid with a viscosity of 152 SUE at 150-F, the projected operating temperature.
Support structure 24 is made entirely of aluminum and comprises a one-inch thick aluminum ring 54. Preferably, the ring 54 is shrunk fit onto the stators 22. A plurality of T-shaped crossbars 56 are welded to ring 54. Two conic eel end plates say 60 are bolted to the crossbars, and carry stainless steel bearing housings 62, 64.
Bearing system 28 (Figure 3) is a non-thrust bearing, whereas bearing system 26 in housing 62 it a thrust bear-in. Roth bearing systems have radial bearings of heavy-duty needle bearings which are suitably Torrington No.
HJ-445628 bearings. These bearings include both the inner and outer race and a cage to accurately guide the bearing rollers. In Figure 7, there is a cross-sectional view of the thrust bearing system 26, showing both the needle roller radial bearing 64 common to the non-thrust bearing system 28 and the duplex angular contact ball thrust bear-in 66~
Needle bearings are used because of their inherently high stiffness. because the rolling elements (the needles) are radially thin and are relatively long axially, they are much stiffer than comparable ball bearings. In add-lion, the fact that the rollers have line contact with each race (rather than point contact as in ball bearings) SUE
also adds kiwi their 'siphon. The calculated ~iffnes~
for each of the joy bearing. I 7.23 x 10~ lb/in at a reload provided by like rotor weight.
It us important hut the bearings in the HUG 12 machine be preluded to prevent skidding at high speed.
In the radial bearing this reload it provided by the weight of the rotor approximately 800 lb per Bering The radial bearing have a catalog-ra~ed maximum steed of 6,150 rum however overspending of rolling element bear-lo ins is an acceptable practice provided they receive adequate lubrication and cooling The radial bearings have a calculated h-10 life of 1,850 hour a continuous operation at 6,300 rip Referring to Figure 7, the thrust bearing system 26 it shown in pagan with shaft 21 inserted therein Additionally, figure 7 shows stainless steel bearing housing 62 bolted to conical end 58 of thy support struck lure I by bolts 68. Conical end 58 is further shown to inlay a steel mounting sleeve 70 pressed therein. Con-netted by bolt 72 it a bearing housing cap 74.
The angular contact ball bearing 66, suitably SO
No. 7411 B, art duplex mounted back-to-bacX on one end of the machine. Attaining sufficient stiffness from the annular contact bull bearings I is accomplished by pro-loading, To prowled these bearings, a shim can be placed between the outer races of the two back-to-back bearing.
Then by clamping the two bearings together on the shaft with a nut, the reload can be established. The amount of reload attained can be adjusted by the thickness of the slough hi between ho bearing. The tradeoff to be made forth thrust bearing it Tiffany versus luff Increasing the reload increase the stiffness while depressing the bearing Lowe. At an 8,000-lb reload (8.5 x 106 lb/in s~iffnesR~, the calculated L-10 life of the thrust bearing_ pair is 97 his. Thy rated speed limit of the bearing it approximately 5,100 rum; however, overspending is accept able when adequate lubrication and cooling are provided.
Lubrication and cooling is provided by an injection lo of oil into the bearing rolling element. Oil flow is provided through lubrication oil inlet 75 to oil injection passage 76 in bearing housing 62 and housing cap 74. At the end of each pa sage is a nozzle 78, which may suitably TM
be a 0.055-in-diameter fluid restructure (Lee Plug Jet Part No. 187002-005)~ A shown, there are two ox is provided for each wide of etch set of bearing roller elements Jo that the bearing will receive lubricant in case of a clogged restructure Also in bearing housing 62 and housing cap 74 are oil jump passages 80 leading to a lubrication oil sup outlet 82. Preferably, the lubrication oil will be passed through at a total flow rate ox 10 gal/min. Oil scavenging is at 25 gamin to prevent oil from pooling in the beaning housing and keep viscous friction losses to a m~nimumr There further shown in Figure 7 a clamping nut 84 on the end of shaft 21 and a drive coupling 86. Driving motor 36 figure 3) it partially shown coupled through mounting flange 88 and spacer 90 to housing caps 74 and d r ivy coup i no 8 6 .
I. Stutter Assumably The talon assembly for PUG 12 it shown it detail in Figure 8. the stators assumably my be regraded a including the ferromagnetic stutter ring 22, the field coil 34, and the aluminum T-bar3 56 figure S) for connecting the pharaoh magnetic stators rings to the support structure. Addition-ally, the stators assembly include inner brush ring 92 and outer brush ring 94. Connecting to the inner brush ring are current collecting conductors AYE and 968.
lo The ferromagnetic stators 22, preferably of A-36 steel, conducts the magnetic field from one rotor face to the other Since the inner brush mechanisms are air-actuated, as will be described, an air manifold 98 is provided through staSor ring 22 and in communication with brush air inlet 100. A noted in the ascription relating to the support structure 24 shown in Figures S and it, aluminum ring 54 is shrunk onto stout ring 22. Additionally, the aluminum ring 54 is pinned to the Starr by steels studs 102.
As shown in Figure 8J the T-bars 56 are bolted by stainless steel bolts 104 to the aluminum ring 54. The bolts 104 are modified so as Jo register with and have inserted in Tao end thereof the steel stud 102. To further enhance the connection of the T-bar 56 to aluminum ring 54, dowel pin 106 are inserted. through the T bar and into ring 54. Bolts 104 are preferably I inch in diameter, and dowel pins 106 are preferably 3~8 inch in diameter. It is also preferred that compensating conductor go be held firmly to the steel stators ring by, for example nylon fathead screws (not shown).
so Field coil 34 comprise two coil Hoyle AYE and 34~, preferably designed for 70,000 amp-turns a a magnetic air yap of 0.5 inch. Because of it interior location, field coil 34 mutt be as thin as possible radially. Accordingly, the coy pulsed rather Han steady state. Each field coil half ha 156 turns of 0.23 inch square solid copper conductor insulated with a heavy coat of armored polyp thermalized insulation.
The terminals 108 of the coil are plug-in-Multilam connectors located between the two coil halves AYE and 34B. Terminal access is through the center of the stators which minimize field dissymmetry. The coils can be run either in series or in parallel and require a 30-V, 417-amp power supply per coil at the 70,000 amp-turn level. In parallel the 30-V requirement is very nearly compatible with an Army 28-V generator.
The field coil is fabricate a follows. The square conductors art half-lap-wrapped with 0.OOS-inch thick, 1/2-inch wide fiberglass tape. Then the two conductors are wound separately onto the two halves of a vacuum impregnation mold. the terminals are then brazed into place, the two halve are bolter together, an the entire structure it vacuum impregnated with a low viscosity, 250F, elevated-temperature-cure epoxy.
JO Brush mechanisms Collection and transfer of current from the high-surface-speed slip rinse is accomplished in PUG 12 by the inner brush mechanism Sheehan in r issues 9 and 10 and the L5~97 outer brush mechanism shown in Figures 11 and 12. This is a demanding task, and because ox the A-I-R configure-lion of the machine additional constraints are placed on the inner brush mechanism in regard to radial height.
That is the radial height must be minimized because the brush and its actuator directly reduce the flux-cutting area of the rotor, which in turn reduces the generated machine voltage. In HUG 12, the outer brush mechanism is also subject to additional considerations since it is lo being used as the current mixing switch.
Referring first to Figures 9 and 10, the inner brush mechanism 30 is shown in position relative to the stators and the rotor In Figure 9, the brush mechanism is shown in an end view (along with two other brush mechanisms 31 and 33). In Figure 10, brush mechanism 30 is shown in a side view The inner brush mechanisms are shown in Figures 9 and 10 connected to the inner brush current collecting conduct ion ring 92 by fathead screws 110. The brush pads 112 which make contact to the rotor inner slip ring surface 19, are preferably 1/8 inch thick by 3/4 inch long by 7/16 inch wide sistered copper-graphite blocks. Each brush pad is attached by silver brazing to a brush strap 114 that carries the current to the brush ring.
The brush straps must conduct extremely high currents without becoming excessively hot. They must operate in a relatively high magnetic field and thus are subjected to high electromagnetic forces during a current pulse. The strap must provide sufficient elastic spring force to lift -lo-~2~51~9~
the brush clear of the slip ring. Finally and most important, the strap must provide a dynamically stable brush mount sufficiently soft radially Jo allow the brush to track the slip ring but 5uffi~iently stiff axially and circumferential to ensure that the brush return to exactly the same orientation on the rotor after each actuation As brush 112 wears away with use, it is desirable to compensate for this wear so that the brush is retracted the same distance from the rotor slip ring surface through-out its useful lifetime, ensuring consistent brush actual lion times and down forces Unfortunately for compact, high packing factor brush assemblies that require short brush straps, the bending stress in the solid copper strap is exceeded during brush actuation, causing the brush strap to yield in the "brush down position and resulting in a 108s of ability to retract the brush. Conventionally hardened copper (hardened by cold working or rolling) cannot be used to raise the yield strength of the brush strap since it will be annealed during the process of brazing the brush strap to the brush.
As a solution, brush straps 114 are laminated.
laminated brush strap is both dynamically stable and stiff in the axial and circumferential planes. This means that the brush will swing through the same arc and maze contact in the same location with each actuation. This it important because as the brush wears it makes better con-tact, but it must make contact in the same orientation with the slip ring during each cycle. The brush strap mutt radially soft because whatever mechanist is act-axing the brush must overcome the strap stiffness as well as provide adequate down forte of thy brush onto ho slip ring however, the strap must be thick enough to conduct the current without an excessive temperature rise. ~150 it must be strong enough to lift the brush clear of the slip ring; thus it should not yield during actuation.
These problems were resolved by laminating the brush strap. By maying the laminations different thicknesses and out of different types of copper (i.e., beryllium, ETA
110, or dispersion strengthened copper, which is not annealed during brazing 9 various combinations of stiff-news, cross-sectional area and strength can ye obtained.
A typical example is a strap made of two 0~031-inch-thick ETA 110 copper straps and one 0.031-inch-thick dispersion strengthened copper strap all 7/16 of an inch wide.
Laminated brush straps 114 will each conduct 3,000 amperes for 0.25 seconds with a 15F~temperature rise.
It take approximately S pounds to move the brush 1/16 of an inch, which provides a lift force of approximately 4.5 pounds. Each strap 114 is approximately one inch long.
The discharge currents in the brush straps 114 react with each other and wit the excitation magnetic field to lift the brushes off the slip ring during a discharge.
Therefore current compensating straps 116 are provided to counteract these of cats. Straps 116 increase the brush down force as the current magnitude increases because the currents flowing in opposite directions repel each other.
This guarantees maximum gown force at peak current.
So Spacer 118 are alto shown on screws 110 between adjacent compensating straps.
Brush pads 12 are downwardly actuated to contact with thy lip ring of the rotor and a down force it applies to maintain brush contact. Actuation of each brush 112 it by a brush actuator 120. The actuator come proses an inflatable diaphragm that forces the brush down. As indicated, one actuator provides simultaneously a down force to a row of brushes ( F inure 1 0 ) The die-frog 122 is suitably synthetic rubber neoprene) molded around a metal brass) core 124, and bonded by a vulcan Nissan process to the top and sides thereof but not to the bottom.
The diaphragm t22 is secured by fathead screws 126 to a fiberglass dovetail mount 128. The mount engages a mating mount t30 carried on the end ox screws 110.
Pressurized gas at about 90 psi is introduced through a hole in the metal core and into the diaphragm cavity. This expands the diaphragm against the back of strap 114 and forces brush pad 112 into contact with the rotor slip ring. The pressurized gas is introduced via inlet tube t32.
Referring now to Figures 11 and 12, outer brush mechanism 32 and adjacent brush mechanism 35 are shown connected by screws 134 to conductor ring 94 and in position adjacent rotor outer slip ring surface 29. Each brush mechanism comprises a brush pad 136 for awaking contact with the rotor slip ring surface. The brush pads are preferably sistered copper-graphite blocks having ISSUE
dimension of I inch in thickness by 3/4 inch in length by 7/16 inch in width. Each brush pad is attached by silver brazing Jo a laminated brush strap 138. Brush straps 138 are a composite famine ion of two 1/32 inch thick annealed copper straps and one 1/32 inch thick disk pension strengthened copper strap.
To prevent discharge currents in brush straps 138 from reacting with each other and with the excitation magnetic field t current compensating straps 140 are provided. Straps 140 extend between adjacent screws 134, and spacers 142 are placed between the straps on each screw.
Deflection of brush straps 138 to place brush pads 136 in contact with the slip ring surface 29 is by await-atop devices 144 carried on the ends of screws 134. The actuator devices comprise a neoprene diaphragm t46 that inflates when pressurized, forcing the brush pads down.
As shown in Figure 12, each actuator provides a down force simultaneously to a row ox brush pads 1360 The diaphragm 146 is molded around a metal (brass) core 148. The metal core is further connected to a manifold 150 having Ann inlet 152 therein. Pressurized gas (air) at 90 psi it suitable for actuating brush actuator devices 144. Actual lion time is on the order of about three millisecond.
The down force applied is about 4-1/2 to 5 lobs.
To electrically connect the two rotor halve in series, which effectively doubles the HUG open-circuit voltage, conductor cross-over structure is required Referring to Figure 13, there is shown a portion of thy :iL2~1LS~97 exterior of HUG 12u pa view art oros~-sv~r bars 154 9 along with arrows inditing discharge current. Each cross over bar arrangement empower two copper Brie 5~8 inch thick by 1-3/8 inch wide It bar 154 are nested between the aluminum T-bars 56. The bars 154 are attached to conductors 94 and 96 (Figure 8) by silver brazing.
Terminals 156 are also shown in Figure 13 D. Auxiliary Supply an Drive System The auxiliary supply and drive system include the lo brush actuator air supply (Figure 14), the bearing Libra-cation system figure 15), and the motoring system (Figure US). These subsystems are shown in Figure 17 in an arrangement on a skid mount. All subsystem are powered by a prime mover, e.g., any motor, engine, or turbine capable of 200 ho a 1800 rum. Suitably, a squirrel-cage induction motor such as Lineguar3M445T is used. It is a drip proof motor with service factor of 1.15 and varnished windings requiring one 460v three-phase lingo Its full-I load speed it 1,780 rum, and its full-load torque is 600 f tubs .
1. Brush Air Supply Brushes 30, 32 figure 3) for HUG 12 are actuated by compressed air. The pneumatic control circuit shown it Figure 14 will supply the brush actuators with 90 pus compressed air The air volume of the inner brush mock anise 30 is approximately 100 in, roughly 1/2 gal. The 2 So I
volume of the outer brush mechanist 32 it approximately 190 in, roughly one gal, The total ye I idea to handle up to 150 pi, although normal operation it antic-pawed in thy vote of 90 psi.
A single stage two-cylinder air comparer pump 160 in Figure 14 it belt-driven from the prime Dover 162~ The compressor 160 (Spiders) is rated to t50 pi maximum pressure and delivers 5.70 aim fret air at 100 pal and 735 rum. At 1 no psi this corresponds to 6.25 gamin compressed air. This means the accumulators 172, 174 con be charged to 100 pi in under one minute. The compressor require up to 2 ho when not unloaded.
Once the accumulators have been charged the compressor will be unloaded (outlet vented to atmosphere) by a con-Tony run unloader control 164. The unloader Control Device 55X709 us rated to 250 psi maximum pressure at 20 efmO Control pressure are adjustable to 135 psi. The unloader also act a a check valve. Down line from the unloader is a SO pi air filter 166 to prevent compressor oil from entering the brush mechanisms. The air filter Speedair~M2Z328 go razed a 110 aim with 40-micron lit-traction.- After filtration, two 125 psi pressure Wrigley-tars 16B, 170 provide control of accumulator pressure.
The regulator SpeedaiTM lZ~38 it rated at 250 pi maximum pressure at 18 aim. Compressed air is stored in two 3-gal accumulator 172, 174. Brush air pressure control it accomplishes with your 300 psi normally closed, two-way solenoid valves 176, 17~t 180, 182. These valve have a l-in port, assuring quick pressurization and venting.
US
Thy valve are ~kkom~tic ~S430-~ semi direct lift solenoid equipped with manual opening h~ndwheel~.
I Bearing Lubrication System The rolling eleven Byron 26, 28 (Figure 3) used in the HUG 12 require oil jet for proper lubrication and cooling. Sufficient scavenging capacity it required to prevent accumulation of lubricant in the bearing and sup covet.
The lubricant preferred is æ parafinic ~ineral-based lo oil with foam suppressant having a viscosity of 100 SO
at 150-F. This lubricant will carry away a significant portion of bearing and seal drag heat output. Bearing losses are emoted at 7.7 ho total; seal losses are east-mated at 7.2 ho total. These losses are nearly linearly dependent on speed and represent worst-case figures A schematic of the bearing lubrication system it shown in Pure 15. The supply and scavenge pumps are belt-driven by the prime mover 162. The bearing oft supply pressure is provided by three 3.2-gpm Gyrate pumps A
noble H3H3 GerotoTMdouble pump 184 supplies pressure to the thrust duplex pair 183 and the thrust end radial bearing 185. Redundant rut assure lubricant flow to both bearings in case of failure of either pump. The oil pressure for the non-thrust-end radial bearing 1~1 is provided by one 3.2-gpm pump of a Double A H3H3Dl Gyrate triple pump 186. This pump is driven by a through shaft from pump 1 a through a flexible coupling. The other 3.2-gpm pump is used to scavenge the outer non-thrust-end US
jump 187~ Thy small 1-gpm pump it used to sieving thy inner hru~t-end sup 189.
Thy third pump 188 it by driven by thy prime Dover.
The Double ~5~5 Juror double pump scavenge both middle jump 191 192 with a keep of 5.0 gyp each.
Driven from the third pump through a flexibly coupling, the fourth pup 190 it a Double A ~12D1 Jury doubly pump. The 13-gpm pump scavenges the outer throned sup OWE The 1-gp~ pump scavenges the non-thrust~end lo inner sup 195.
overall supply flow is 9.6 gyp while overall scavenge flow it 28.2 gym. This result in a scavenge-to-supply ratio of 2,9.
Flow from the scavenge pumps it directed to a toggle reservoir 192 for deforming. From the res~rvoirD oil it pulled through an oil cooler 194 and filter 196 ho the supply pumps. The Perfex SUB I oil cooler it rated at 20 hp/100~ITD at 9.6 gym. The cooler has minimal pressure drop at this low flow. The yoke DEFY 330 oil filter it rated for 46 pi at JOY pi and provides 5-micron ration. Should the pressure drop of these components cause cavitation in the supply pumps, they can be moved to the scavenge to reservoir line. This location would be undesirably as tooling capacity will drop due to air entrapment in the oil cooler. However, the system should be able to maintain the machine at speed indefinitely . Motoring System wow hydraulic motor AYE, 36B figure 3), one on each end of the shaft, will be used to bring the A-I-R HUG 12 Sue to speed. VolvoMF11~-19 hydraulic motor are preferred to obtain a motoring time ox approximately 2 yin Jo reach 6,300 rip the design speed. The hydraulic ~lrcuit, shown schematically in Figure 16~ must supply each hydraulic motor with 32 gal of OWE psi hydraulic fluid per min.
In the schematic, new ANSI fluid power symbols are used to-identify the compo~ent5.
The hydraulic motor AYE, 36~ in Figure 1 it, have 1.16 in3/rev displacement, a maximum continuous operating lo pressure of 5,000 psi, and a listed maximum operating speed ox 7,500 rum. They have a constant output torque of 922 in-lb~ each and require 31~6 gamin each at 6,300 rip before mechanical and volumetric efficiencies are included.
Estate mechanical efficiency is 90 percent and estimated volumetr~e efficiency is 99 percent.
The hydraulic supply pump 198 is a ~ydromati~ AVOW 16~
DRY variable displacement, flange-mounted, bent axis, axial piston pump. It has displacement of 164 crave, Max-mum speed of 2,000 rum, adjustable constant pressure con-trot, and mechanical stroke limiter. It has a theoretical output of 77.t gym at 1, 780 rum, which becomes 74.8 go with 3 percent displacement losses. Thus thy hydraulic circuit ha a 15 percent martin of safety including menu-lecturers losses, for motoring to 6,300 rum.
A separate cooling and filtering circuit will cool the hydraulic fluid during motoring and idling. The cooling pump 200 it 40 gym flange-mounted gear pump.
The HydrecBM2025 fixed displacement pump it rated for 1, 800 rum and 750 psi although system pressure it limited it 100 pal by on nine relief valve 202. This Rowley valve protect ho oil cooler 204 and filter 206 Roy o'er pressures during syrup The Circle Siam in-line relies Allah 202 it rated for 40 gym an 1,200 pi Mom The rocking prowar it adjustable from 85 pi to 120 psi. The Pere~MS~-6~ oil cooler 2~4 way sized to disk-pate the heat generated from the hydraulic braking valve at 75 hp/100 vindicated temperature difference). It ha an estimated pressure drop of 40 psi, a maximum operating lo pressure of 150 psi, and a maximum flow of 72 gyp The GreseTMF401 filter 206 provide 10-micron filtration. The filter it rated for 75 gym at 200 psi and ha a 15 psi bypass spring.
After motoring to speed the pilot-operated relief valve 20~, ~10 will be opened to the reservoir by two-way solenoid valve 212, 214. This will allow freewheeling of the hydraulic motors and will bypass the main supply pump output to the reservoir during discharge or idling condo-lions. The Victor Fluid Powe~FMVR323105 pilvt-operated relief valves 208, 21~ operate as a 6,000 psi relief valve until vented my the wow solenoid valve. The valve rated at 10,000 psi maximum pressure at 50 gym flow The Circle Sea~MSV460 two-way solenoid valves 212, 214 ore rated at 6,000 psi maxim pressure. They have a I of 0.64 which assures very low vent pressure. These valve are normally open so that in the event of loss of power the relief v21ves will fail open.
The hydraulic braking valves 216, 218 are 2,500 pus pilot-operated relief valves vented by normally open solenoid valve Swahili o the frill relief valve.
The Tickers CT5-10 ~ol~no~d-controlled relief valve combine both in one unit. These valves were selected for their low venter pressure drop of 25 psi at 35 gym.
higher pressure drop would adversely aft the hydraulic motors These valves will be open except during emergency shutdown situation. When closed, these braking valves will stop the rotor in less than 3 mix from 6,300 rum.
The hydraulic fluid reservoir 220 has two deforming lo plates and a capacity of 10 gal. It will be constructed from welded aluminum pipe and sheet stock. The high-pressure feed hose 222 will be 1.00-in ID, 1.91-in ODE
sprawler double-armored hydraulic hose. It is rated at 5,000 psi working pressure and 20,000 psi minimum burst pressure. the return hove 224 will be 1.25-in-ID, 1.91-in ODE 4-spiral-wire, double-armored hydraulic hose. It is rated at 3,000 psi working pressure and 12,000 psi minimum burst pressure. The cooling circuit hose 226 will be 1.38-in ID, 1.75-in ODE single-wire braid hydraulic hose.
it it rated at 500 psi worming pressure and 2,000 pus minimum burst pressure. The hydraulic medium chosen for the system is Rondo Oil HD32. It is a high-grade mineral-based hydraulic fluid with a viscosity of 152 SUE at 150-F, the projected operating temperature.
4. Auxiliary System Mounting Arrangement Referring now to figure 17, the mounting arrangement of the supply subsystems on a skid frame 228 is diagramed The prime mover 162 is securely located between the rails ~ZJ~S~97 of fray 2280 To one en of ho prize mover I hydraulic supply pump 1980 flexible coupling 230 it owe inter-ensuing the prize mover and pup OWE Drive belt 232 sonnet thy prim over to Berlin oil supply double pup 184 an bearing oil scavenge double pump 18B. Bearing owl supply pump I driven by pump 18~. Similarly, bearing oil scavenge pump 190 it driven by pump 188. Reservoir 192 which receives flow from the scavenge pump it shown in the forward part of the skid frame. Thy owl from the lo reservoir it pulled through cooler 194 located aft of prime mover 162.
hydraulic cooling circuit pump 200 is mounted on the skid adjacent pump 188 and driven by prime mover The hydraulic owl filter 206 it mounted aft on the slid frame The hydraulic relief valves 208, 210 art shown in position in the forward portion of the skid frame, along with braking valve ~16, 218. Hydraulic fluid reservoir 220 is mounted just behind valves 216, 218 and adjacent the oil reservoir. The high pressure hydraulic feed hoses 222 are carried in the forward end of the skid frame as are the hydraulic return hose 224. A hydraulic air cooler 2~3 for prime mover 162 it mounted to the aft end of the skid.
Alto mounted on the skid it field golf generator 23~.
This generator, belt-driven from prime mover 162, energizes the PUG field coils. the air compressor 160 for the brush actuator Siam is mounted on the opposite side ox the skid from generator 23~, and is also belt-driven from the prime mover. HUG 12, though not shown, also mounted on the skid frame.
l~LS097 En Control System The control system 18 (Figure 1) junctions to control the various system of the HUG power supply, and to disarm ho machine if a fault occurs The PUG power supply it controlled by an operator through a control panel 240 shown in Figure 18. Thy control system further include a logic controller 242, an L~C-40 device, interconnected with the control panel and HUG 12. Instrumentation, including a signal analyzer 244, an integrator 246, and an oscillo~
lo graph 248 are also provided and receive control signal inputs from the logic controller. The instrumentation provides information useful to monitor machine performance.
For example, the following my be monitored: discharge current, rum, voltage, rotor runt, and bearing signature analysis.
The control panel 240 with which the operator inter-faces has four push buttons for controlling HUG 12 include in power on Sutton 250, shut down button 252, ready to motor button 254, and ready to discharge button 256.
digital tachometer 258 is provided, and there are a series of fault-indicating lights 260. The fault lights indicate the following:
Low Brush Pressure -- two pressure switches with a low point set at 90 Sue Lowe Bearing Oil Pressure -- one pressure switch set at a low point of 50 psi and a high point of 125 psi.
jot Bearing Oil -- a temperature switch set at 20GF~
Low Motoring Oil pressure -- a pro sure switch set at 2,500 pi.
owe Motoring Oil -- a temperature switch sot at 250~.
Rotor Vibration -- a vibration alarm switch set a 1-g lateral acceleration.
Long rotor Time -- LDC I controller provide a timer.
Low Alternator Voltage -- a millimeter with an adjustable sex point connected in series with a shunt across terminals of alternator jot Field Coil - a temperature switch set at 220'F.
Brush Dragging -- a millimeter with an 8-10-V set point connected across terminal of A-I-R PUG
No PUG Voltage -- same as Brush Dragging No HO Current -- a Rogues coil set to trip a latching relay.
Overfeed Pi set point on digital tachometer.
The operating control sequence carried out by logic controller 242 is set forth in the flow chart of Figure 19. Default mode indicated on the controller flow chart are:
LEVEL 1 - Stand by - Light up fault indicating on control panel - Hold until clear LEVEL 2 hydraulic motor braze. When stopped, go to Level 1 LEVEL 3 - Reduced field discharge LEVEL 4 - Full field discharge 5V9~
The foregoing description of the invention has been directed to a particular preferred embodiment for purposes of explanation and illustration It will be apparent however, to those skilled in this art that many modifica-lions and changes in both the illustrated apparatus and the methods taught may be made without departing from the invention. It is applicants' intention in the following claims to cover all equivalent modifications and variations as fall within the scope of the invention.
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hydraulic cooling circuit pump 200 is mounted on the skid adjacent pump 188 and driven by prime mover The hydraulic owl filter 206 it mounted aft on the slid frame The hydraulic relief valves 208, 210 art shown in position in the forward portion of the skid frame, along with braking valve ~16, 218. Hydraulic fluid reservoir 220 is mounted just behind valves 216, 218 and adjacent the oil reservoir. The high pressure hydraulic feed hoses 222 are carried in the forward end of the skid frame as are the hydraulic return hose 224. A hydraulic air cooler 2~3 for prime mover 162 it mounted to the aft end of the skid.
Alto mounted on the skid it field golf generator 23~.
This generator, belt-driven from prime mover 162, energizes the PUG field coils. the air compressor 160 for the brush actuator Siam is mounted on the opposite side ox the skid from generator 23~, and is also belt-driven from the prime mover. HUG 12, though not shown, also mounted on the skid frame.
l~LS097 En Control System The control system 18 (Figure 1) junctions to control the various system of the HUG power supply, and to disarm ho machine if a fault occurs The PUG power supply it controlled by an operator through a control panel 240 shown in Figure 18. Thy control system further include a logic controller 242, an L~C-40 device, interconnected with the control panel and HUG 12. Instrumentation, including a signal analyzer 244, an integrator 246, and an oscillo~
lo graph 248 are also provided and receive control signal inputs from the logic controller. The instrumentation provides information useful to monitor machine performance.
For example, the following my be monitored: discharge current, rum, voltage, rotor runt, and bearing signature analysis.
The control panel 240 with which the operator inter-faces has four push buttons for controlling HUG 12 include in power on Sutton 250, shut down button 252, ready to motor button 254, and ready to discharge button 256.
digital tachometer 258 is provided, and there are a series of fault-indicating lights 260. The fault lights indicate the following:
Low Brush Pressure -- two pressure switches with a low point set at 90 Sue Lowe Bearing Oil Pressure -- one pressure switch set at a low point of 50 psi and a high point of 125 psi.
jot Bearing Oil -- a temperature switch set at 20GF~
Low Motoring Oil pressure -- a pro sure switch set at 2,500 pi.
owe Motoring Oil -- a temperature switch sot at 250~.
Rotor Vibration -- a vibration alarm switch set a 1-g lateral acceleration.
Long rotor Time -- LDC I controller provide a timer.
Low Alternator Voltage -- a millimeter with an adjustable sex point connected in series with a shunt across terminals of alternator jot Field Coil - a temperature switch set at 220'F.
Brush Dragging -- a millimeter with an 8-10-V set point connected across terminal of A-I-R PUG
No PUG Voltage -- same as Brush Dragging No HO Current -- a Rogues coil set to trip a latching relay.
Overfeed Pi set point on digital tachometer.
The operating control sequence carried out by logic controller 242 is set forth in the flow chart of Figure 19. Default mode indicated on the controller flow chart are:
LEVEL 1 - Stand by - Light up fault indicating on control panel - Hold until clear LEVEL 2 hydraulic motor braze. When stopped, go to Level 1 LEVEL 3 - Reduced field discharge LEVEL 4 - Full field discharge 5V9~
The foregoing description of the invention has been directed to a particular preferred embodiment for purposes of explanation and illustration It will be apparent however, to those skilled in this art that many modifica-lions and changes in both the illustrated apparatus and the methods taught may be made without departing from the invention. It is applicants' intention in the following claims to cover all equivalent modifications and variations as fall within the scope of the invention.
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Claims (20)
1. A brush assembly for a rotating electrical machine including a stators having a field coil for producing a magnetic field, a rotor for rotation within the stators magnetic field to produce electrical current, and a slip ring surface on the rotor, comprising:
(a) a brush pad comprising a plurality of adjacent brush pad blocks, for making contact with the rotor slip ring surface;
(b) a brush strap connected to said brush pad, for biasing said brush pad blocks toward a retracted position away from the rotor slip ring surface;
(c) an actuator for causing deflection of said brush strap to simultaneously place the brush pad blocks in contact with the slip ring surface;
said actuator including -(i) an elongated core structure having a passage there through for fluid communication; and (ii) an inflatable diaphragm comprising a synthetic rubber body molded around the core and bonded only to the top and sides thereof, whereby a diaphragm cavity is defined;
and (d) means for introducing pressurized, gas through the passage in the core and into the diaphragm cavity, to expand the diaphragm against the back of the brush strap and force the brush pad blocks into contact with rotor slip ring surface.
(a) a brush pad comprising a plurality of adjacent brush pad blocks, for making contact with the rotor slip ring surface;
(b) a brush strap connected to said brush pad, for biasing said brush pad blocks toward a retracted position away from the rotor slip ring surface;
(c) an actuator for causing deflection of said brush strap to simultaneously place the brush pad blocks in contact with the slip ring surface;
said actuator including -(i) an elongated core structure having a passage there through for fluid communication; and (ii) an inflatable diaphragm comprising a synthetic rubber body molded around the core and bonded only to the top and sides thereof, whereby a diaphragm cavity is defined;
and (d) means for introducing pressurized, gas through the passage in the core and into the diaphragm cavity, to expand the diaphragm against the back of the brush strap and force the brush pad blocks into contact with rotor slip ring surface.
2. A homopolar generator, comprising:
a stator, for producing a magnetic field;
a rotor having a slip ring surface defined thereon, for rotation within the stator magnetic field to generate an electrical potential;
a brush for contacting the rotor slip ring surface to collect current therefrom;
means for repeatedly actuating the brush into contact with the rotor slip ring; and a brush strap having the brush attached thereto, for transferring current and for lifting the brush clear of the rotor slip ring after actuation, said brush strap comprising a plurality of laminations.
a stator, for producing a magnetic field;
a rotor having a slip ring surface defined thereon, for rotation within the stator magnetic field to generate an electrical potential;
a brush for contacting the rotor slip ring surface to collect current therefrom;
means for repeatedly actuating the brush into contact with the rotor slip ring; and a brush strap having the brush attached thereto, for transferring current and for lifting the brush clear of the rotor slip ring after actuation, said brush strap comprising a plurality of laminations.
3. The homopolar generator of Claim 2 wherein there are at least two independent laminations of different types of metal, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes and yielding in a predetermined manner after each actuation, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
4. The homopolar generator of Claim 2, wherein the lamina-tions of said brush strap include three lamination layers of copper.
5. The homopolar generator of Claim 2 or 4, further comprising, a conductor electrically connected to the end of said brush strap opposite the brush, for receiving current from said brush strap flowing in one direction and directing it in a reverse direction so as to be in opposition to the current in said brush strap.
6. A brush mechanism for a homopolar generator having a rotor with a slip ring surface defined thereon and rotational in a stator magnetic field to produce electri-cal discharge current, comprising:
a brush for contacting the rotor slip ring surface to collect discharge current;
means for repeatedly actuating the brush into contact with the rotor slip ring, and a brush strap having the brush attached to one end and being fixedly mounted at the opposite end, for transferring discharge current and for lifting the brush clear of the rotor slip ring after actuation, said brush strap comprising a plurality of laminations.
a brush for contacting the rotor slip ring surface to collect discharge current;
means for repeatedly actuating the brush into contact with the rotor slip ring, and a brush strap having the brush attached to one end and being fixedly mounted at the opposite end, for transferring discharge current and for lifting the brush clear of the rotor slip ring after actuation, said brush strap comprising a plurality of laminations.
7. The brush mechanism of Claim 6 wherein there are at least two independent laminations of different types of metal, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes and yielding in a predetermined manner after each actuation, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
8. The brush mechanism of Claim 6, wherein the laminations of said brush strap include three lamination layers of copper.
9. The brush mechanism of Claims 6 and 8, further comprising, a conductor electrically connected to the end of said brush strap opposite the brush, for receiving current from said brush strap and directing it in a direction opposite to the current in said brush strap.
10. A brush mechanism for a rotating electrical machine having a slip ring surface from which electrical current can be collected, comprising:
a brush for contacting a slip ring surface to collect current; and a brush strap having the brush attached to one end, for supporting the brush with respect to the slip ring surface, said brush strap comprising a plurality of laminations.
a brush for contacting a slip ring surface to collect current; and a brush strap having the brush attached to one end, for supporting the brush with respect to the slip ring surface, said brush strap comprising a plurality of laminations.
11. The brush mechanism of Claim 10 wherein there are at least two independent laminations of different types of metal, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes and yielding in a predetermined manner after each actuation, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
12. A brush mechanism for a rotating electrical machine having a slip ring surface, comprising:
a brush for contacting a slip ring surface to collect current;
a trailing arm brush strap having the brush attached to one end, for supporting the brush with respect to the slip ring surface and transferring collected current; and a conductor electrically connected to the end of the brush strap opposite the brush, for receiving current from the brush strap and directing it opposite to the direction of current in the brush strap.
a brush for contacting a slip ring surface to collect current;
a trailing arm brush strap having the brush attached to one end, for supporting the brush with respect to the slip ring surface and transferring collected current; and a conductor electrically connected to the end of the brush strap opposite the brush, for receiving current from the brush strap and directing it opposite to the direction of current in the brush strap.
13. A homopolar generator, comprising:
a stators for producing a magnetic field;
a rotor having a slip ring surface defined thereon, for rotation within the stators magnetic field to generate an electrical potential;
a brush for contacting the rotor slip ring surface to collect current therefrom;
means for activating the brush into contact with the rotor slip ring; and a brush strap having the brush attached thereto, for transferring current and for lifting the brush clear of the rotor slip ring after actuation;
said brush strap comprising laminations including two lamination layers of a first type of copper and a third lamination layer of a second type of copper, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
a stators for producing a magnetic field;
a rotor having a slip ring surface defined thereon, for rotation within the stators magnetic field to generate an electrical potential;
a brush for contacting the rotor slip ring surface to collect current therefrom;
means for activating the brush into contact with the rotor slip ring; and a brush strap having the brush attached thereto, for transferring current and for lifting the brush clear of the rotor slip ring after actuation;
said brush strap comprising laminations including two lamination layers of a first type of copper and a third lamination layer of a second type of copper, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
14. The homopolar generator of Claim 13, further comprising:
a conductor electrically connected to the end of said brush strap opposite the brush, for receiving current from said brush strap and directing it in a direction of current opposite to the current in said brush strap.
a conductor electrically connected to the end of said brush strap opposite the brush, for receiving current from said brush strap and directing it in a direction of current opposite to the current in said brush strap.
15. A brush mechanism for a homopolar generator having a rotor with a slip ring surface defined thereon and rotational in a stators magnetic field to produce electrical discharge current, comprising:
a brush for contacting the rotor slip ring surface to collect discharge current;
means for actuating the brush into contact with the rotor slip ring;
a brush strap having the brush attached to one end and being fixedly mounted at the opposite end, for transferring discharge current and for lifting the brush clear of the rotor slip ring after actuation;
and said brush strap comprising laminations including two lamination layers of a first type of copper and a third lamination of a second type of copper, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
a brush for contacting the rotor slip ring surface to collect discharge current;
means for actuating the brush into contact with the rotor slip ring;
a brush strap having the brush attached to one end and being fixedly mounted at the opposite end, for transferring discharge current and for lifting the brush clear of the rotor slip ring after actuation;
and said brush strap comprising laminations including two lamination layers of a first type of copper and a third lamination of a second type of copper, for providing predetermined stiffness and dynamic stability in the axial and circumferential planes, so that the brush will swing through the same arc and make contact in the same location on the rotor slip ring with each actuation, and providing sufficient softness radially to allow the brush to track the slip ring.
16. The brush mechanism of Claim 15, further comprising:
a conductor electrically connected to the end of said brush strap opposite the brush, for receiving current from said brush strap and directing it in a direction opposite to the current in said brush strap.
a conductor electrically connected to the end of said brush strap opposite the brush, for receiving current from said brush strap and directing it in a direction opposite to the current in said brush strap.
17. A homopolar generator, comprising:
a support structure;
a stator assembly inwardly disposed within said support structure for producing a stator magnetic field;
a shaft mounted in said support structure;
a rotor carried on said shaft, said rotor including two mating rotor halves together defining a recess in the peripheral surface of the rotor, for fitting around the stator assembly to enclose the same;
an inner brush mechanism disposed within the recess in the rotor, for contacting a surface of the rotor defined by the recess to collect discharge current;
and an outer brush mechanism disposed within the support structure, for contacting the peripheral surface of the rotor adjacent the recess to collect discharge current.
a support structure;
a stator assembly inwardly disposed within said support structure for producing a stator magnetic field;
a shaft mounted in said support structure;
a rotor carried on said shaft, said rotor including two mating rotor halves together defining a recess in the peripheral surface of the rotor, for fitting around the stator assembly to enclose the same;
an inner brush mechanism disposed within the recess in the rotor, for contacting a surface of the rotor defined by the recess to collect discharge current;
and an outer brush mechanism disposed within the support structure, for contacting the peripheral surface of the rotor adjacent the recess to collect discharge current.
18. The generator of Claim 17 further comprising:
means for electrically isolating the rotor halves from one another; and means for interconnecting the brush mechanisms to establish the rotor halves in series electrically.
means for electrically isolating the rotor halves from one another; and means for interconnecting the brush mechanisms to establish the rotor halves in series electrically.
19. The homopolar generator of Claim 17 wherein the shaft comprises a groove extending circumferentially thereabout at a location between the midpoint thereof and an end, and having a port extending therethrough from said end to groove, for conducting fluid under high pressure to the interface between said shaft and one rotor half.
20. The homopolar generator of Claim 19, further comprising first and second high-pressure seals disposed on opposite sides of said circumferential groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000507926A CA1221722A (en) | 1982-05-26 | 1986-04-29 | Homopolar generator power supply system and rotor assembly therefor |
Applications Claiming Priority (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US38192882A | 1982-05-26 | 1982-05-26 | |
| US381,927 | 1982-05-26 | ||
| US381,928 | 1982-05-26 | ||
| US06/381,927 US4544874A (en) | 1982-05-26 | 1982-05-26 | Homopolar generator power supply system |
| US06/381,926 US4562368A (en) | 1982-05-26 | 1982-05-26 | Brush mechanism for a homopolar generator |
| US06/381,925 US4459504A (en) | 1982-05-26 | 1982-05-26 | Brush actuator for homopolar generator |
| US381,925 | 1982-05-26 | ||
| US381,926 | 1982-05-26 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000507926A Division CA1221722A (en) | 1982-05-26 | 1986-04-29 | Homopolar generator power supply system and rotor assembly therefor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1215097A true CA1215097A (en) | 1986-12-09 |
Family
ID=27503206
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000428867A Expired CA1215097A (en) | 1982-05-26 | 1983-05-25 | Brush mechanism for a homopolar generator |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1215097A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106314405A (en) * | 2016-09-17 | 2017-01-11 | 西安科技大学 | Large-tonnage hydraulic mining vehicle braking system and method |
| CN111727532A (en) * | 2018-02-14 | 2020-09-29 | 菲尼克斯电气公司 | Method for producing contact plug and contact plug |
| CN114362463A (en) * | 2022-01-17 | 2022-04-15 | 浙江伟康电机有限公司 | Motor assembly all-in-one machine |
-
1983
- 1983-05-25 CA CA000428867A patent/CA1215097A/en not_active Expired
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106314405A (en) * | 2016-09-17 | 2017-01-11 | 西安科技大学 | Large-tonnage hydraulic mining vehicle braking system and method |
| CN106314405B (en) * | 2016-09-17 | 2023-03-14 | 西安科技大学 | Hydraulic braking system and method for large-tonnage mining vehicle |
| CN111727532A (en) * | 2018-02-14 | 2020-09-29 | 菲尼克斯电气公司 | Method for producing contact plug and contact plug |
| CN114362463A (en) * | 2022-01-17 | 2022-04-15 | 浙江伟康电机有限公司 | Motor assembly all-in-one machine |
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| Date | Code | Title | Description |
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| MKEX | Expiry |