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WO1997036362A1 - Appareil electromagnetique a vitesse variable - Google Patents

Appareil electromagnetique a vitesse variable Download PDF

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Publication number
WO1997036362A1
WO1997036362A1 PCT/US1997/004733 US9704733W WO9736362A1 WO 1997036362 A1 WO1997036362 A1 WO 1997036362A1 US 9704733 W US9704733 W US 9704733W WO 9736362 A1 WO9736362 A1 WO 9736362A1
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WO
WIPO (PCT)
Prior art keywords
gear
rotor
stator
torque
coupled
Prior art date
Application number
PCT/US1997/004733
Other languages
English (en)
Inventor
Douglas F. Parker
Original Assignee
Parker Douglas F
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Parker Douglas F filed Critical Parker Douglas F
Priority to AU25436/97A priority Critical patent/AU2543697A/en
Publication of WO1997036362A1 publication Critical patent/WO1997036362A1/fr

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Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/727—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path
    • F16H3/728—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with at least two dynamo electric machines for creating an electric power path inside the gearing, e.g. using generator and motor for a variable power torque path with means to change ratio in the mechanical gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K16/00—Machines with more than one rotor or stator
    • H02K16/005—Machines with only rotors, e.g. counter-rotating rotors

Definitions

  • This invention relates to variable speed electromagnetic machines which can be adapted for use as a motor, a generator, or a dynamic brake. Many applications would be greatly improved by a motor that operates at variable speeds, without requiring adjustment of the frequency, wave form, or applied voltage of the power applied to the motor. Similarly, it would be highly advantageous to have a generator which produced an electrical current of a desired frequency, wave form, and voltage, despite changes in the rotational velocity of the input shaft to the generator. The present invention is intended to fill these needs in the art.
  • a variable speed electromagnetic machine comprising a rotor and a stator, both of which are mounted for a rotation with respect to a reference element.
  • An output element is coupled to one of the rotor and the stator for transmitting power between said one of the rotor and the stator at an external system.
  • a variable load is coupled to the other of the rotor and the stator to apply a variable torque tending to retard rotation of the other of the rotor and the stator. This variable load reacts against the reference element, and the stator electromagnetically interacts with the rotor to produce at least one of torque and electrical power.
  • a variable speed electromagnetic machine includes a rotor comprising a rotor gear, and a stator comp ⁇ sing a stator gear.
  • a gear assembly is coupled to the rotor gear and to the stator gear and is mounted for rotation relative to both the rotor and the stator.
  • a variable torque is coupled to the gear assembly to vary the rotational speed of the gear assembly by varying the torque applied to the gear assembly.
  • the speed of the electromagnetic machine can be varied within a wide range by properly selecting the torque that is applied to the gear assembly.
  • Figures 1 , 2, and 3 are schematic representations of electromagnetic motors that illustrate the operating principles of selected embodiments of this invention.
  • Figures 4, 5, 6 and 6a are cross-sectional views of four preferred embodiments of the present invention.
  • Figure 7 is a cross-sectional view of a gear motor that incorporates another presently preferred embodiment of this invention.
  • Figure 8 is a cross-sectional view of a variation of the embodiment of Figure 7.
  • Figure 9 is a cross-sectional view of a gear motor that incorporates another embodiment of this invention.
  • Figure 10 is a partial cross-sectional view of a variation of the embodiment of Figure 9.
  • Figure 11 is a partial cross-sectional view of another variation of the embodiment of Figure 9.
  • Figures 1 through 3 will be used to provide a general overview, and then preferred embodiments of the invention will be discussed in conjunction with Figures 4 through 11.
  • FIG. 1 through 3 show schematic views of three motors that operate at variable speeds without requiring any change to the frequency, wave form, or voltage of the applied power
  • the gear motor 10 includes a rotor 12 and a stator 14
  • the rotor 12 and the stator 14 can be any conventional elect ⁇ cal rotor and stator for a motor or generator
  • the stator 14 can include conventional three-phase stator windings
  • the rotor 12 can be a conventional rotor suitable for use with such a stator
  • conventional devices as such as slip rings are used to provide electrical power to the stator 14
  • the rotor 12 interacts electromagnetically with the stator 14 in the conventional manner to produce torque or electrical power
  • an output shaft 16 is connected to the rotor 12 to rotate therewith Bearings 18, 20 mount both the rotor 12 and the stator 14 for rotation with respect to a reference element R
  • the reference element R is shown schematically in Figure 1 , but in many embodiments the reference element R will be a casing or housing for the motor 10
  • a variable load 22 is coupled to the stator 14, and this variable load 22 reacts against the reference element R
  • the speed of rotation of the output shaft 16 can be controlled between zero rpm and the maximum rated speed of the motor 10
  • the variable load 22 can initially apply zero torque to the stator 14
  • the stator 14 When the stator 14 is energized, the rotor 12 and the output shaft 16 will remain stationary, and the stator 14 will rotate at the design speed in the reverse direction
  • the variable load 22 is gradually increased, the stator 14 will slow down, and the speed of the rotor 12 and the output shaft 16 will increase
  • the variable load 22 is sufficient to hold the stator 14 in a fixed rotational position with respect to the reference element R, the rotor 12 and the output shaft 16 will rotate at the design speed of the motor 10
  • the output shaft 16' can be connected to the stator 14 and the variable load 22' can be connected to the shaft of the rotor 12
  • Operation of the motor 10' of Figure 2 is substantially the same as that of the motor 10 Figure 1 , except that it is the stator 14 that provides power to the extemal system via the output shaft 16', and it is the rotor 12 that drives the variable load 22'
  • the variable load 22" takes the form of a variable hydraulic pump, which supplies pressurized hydraulic fluid to a hydraulic motor 24"
  • the hydraulic pump 22" is coupled via gears 26", 28" to the stator 14
  • the pump 24" provides a variable load, similar to the va ⁇ able load 22 of Figure 1 , but much of the power required to drive the variable pump 22" is recovered via the motor 24"
  • the motor 24" is configured to rotate
  • FIG 4 shows a cross-sectional view of a motor 30 which is similar to the motor 10 shown in Figure 1
  • the rotor 32 is connected to an output shaft 34
  • the stator 36 is connected via spur gears 38, 40 to a brake 42
  • the brake 42 forms a variable load, and causes the motor 30 to operate as described above in conjunction with
  • the motor 30 of Figure 4 allows speed changes from zero to full speed at very low cost and low energy efficiency At full speed, the brake 42 locks, and is removed from the energy equation
  • the motor 30 therefore provides conventional motor efficiency when operating at full speed This arrangement works well in applications where an elect ⁇ cal motor is used to start a high torque load such as a ball mill. In this case, the brake 42 is used during start ⁇ up only, so total energy loss isjnsignificant.
  • the motor 30 can be started at no load.
  • FIG. 5 shows another motor 50 which operates according to the principles discussed above in conjunction with Figure 3.
  • the motor 50 includes a rotor 52 that rotates in unison with an output shaft 54.
  • a stator 56 is mounted for rotation with respect to the rotor 52 and the motor case 51.
  • the stator 56 is connected via gears 58, 60 to a variable hydraulic pump 62, which supplies pressurized hydraulic fluid to a hydraulic motor 68.
  • the hydraulic motor 68 is connected via gears 64, 66 to the output shaft 54.
  • the motor 50 of Figure 5 provides high control efficiency from zero to full torque throughout the speed range. If desired, the motor 68 and pump 62 can be switched and reversed to change rotational direction.
  • the motor 50 of Figure 5 allows rotational change without switching where the load torque is always in one direction, as in hoisting applications. In this way, full control of the load on a hoist can be provided without using brakes to stop or to change the output rotational direction.
  • the cost of stator construction to rotate at speed is proportional to the top rotational design speed. In an 1 ,800 rpm motor, the stator rotates between plus and minus 1 ,800 rpm, while the rotor rotates between 0 and 3,600 rpm.
  • the motor 70 of Figure 6 is in many ways similar to the motor 50 of Figure 5 discussed above, and comparable elements bear the same reference numeral.
  • the hydraulic motor 68 rotates a gear carrier 72 via gears 74, 76.
  • the gear carrier 72 forms part of a differential which applies torque to the output shaft 54 via the gears 78, 80, 82.
  • the motor 70 is quite similar to the motor of Figure 10 in terms of the operation of the differential.
  • FIG. 6a shows a modified version of the motor of Figure 6.
  • an additional hydraulic motor 69 is mounted to the gear case to drive the rotor 52 and the output shaft 54 directly.
  • This motor 69 is powered by the pump 62, and the hydraulic unit 68' functions as a pump or as a motor, depending on the output speed.
  • the motor 69 is larger capacity than the unit 68', which is larger capacity than the pump 62.
  • the only active hydraulic unit is the unit 68', and it is at zero speed. 50% of the output power is developed by the rotor 52, and 50% of the output power is developed by the stator 56 and transferred through the differential gear to the rotor 52 and the output shaft 54.
  • the large hydraulic motor 69 is operative at low speeds only. Hydraulic flow stops at 50% output speed, and the intermediate hydraulic unit 68' is operative as a motor at high output speeds.
  • This arrangement can provide an efficient variable speed electric motor that can develop full horsepower over 90% of its speed range, yet is economical.
  • differential gearing In general, the decision as to whether or not to use differential gearing will depend on the requirements of the particular application, particularly the efficiency and manufacturing cost requirements. In general, it will often be preferable to avoid differential gearing for small motors and generators, because small capacity hydraulic units are less expensive than differential gear units and high efficiency operation is often not a prime objective. Similarly, it will often be preferable to use differential gearing in large motors and generators, because (1 ) large hydraulic pumps and motors are often speed restrictive, (2) differential gearing can substantially reduce the size and expense of such pumps and motors, and (3) differential gearing can increase efficiency
  • Hydraulic pumps and motors should be chosen as appropriate for the particular application In general, the present invention is suitable for use with the widest variety of pumps and motors Simply by way of example, and without intending any limitation to the scope of the present invention, hydraulic pumps and motors such as Model 7, available from RHL (U K), have been found suitable in one application Similarly, brakes such as Model TBA (7 m-lb), available from Dana Corp , have been found suitable for another application
  • the embodiment illustrated in Figure 7 is a gear motor that operates at variable speeds without requiring any change to the frequency, wave form, or voltage of the applied power
  • the gear motor of Figure 7 is one example of an electromagnetic machine 110 Electrical generators and dynamic brakes are other examples
  • the electromagnetic machine 110 includes an output shaft 112 that is rigidly secured to a first flange 114
  • the first flange 114 is rigidly secured to a cylindrical shell 120, which is in turn secured to a second flange 116
  • the second flange 116 supports a cylindrical sleeve 118
  • the cylindrical shell 120 supports a stator winding 122, which in this embodiment is a conventional three-phase stator winding
  • the entire assembly is mounted for rotation on bearings 124, 126 Power is supplied to the stator winding 122 via conventional brushes 128
  • the stator winding 122 and the elements that rotate with the stator winding 122 together make up a stator 130
  • a stator is an electromagnetic structure that interacts with a rotor to produce torque or electrical power
  • the term "stator" is intended broadly to cover rotating devices, as shown for example in Figure 7
  • the electromagnetic machine 110 also includes a rotor 132 which is mounted for rotation in unison with a rotor shaft 134
  • the rotor shaft 134 is supported by bearings 136, 138, 140
  • the bearings 126, 140 are mounted to a gear housing 142 which in this embodiment does not rotate.
  • stator gear 144 which is in this embodiment is a ring gear that is keyed for rotation with the cylindrical sleeve 118, and therefore with the stator 130.
  • rotor gear 146 which in this embodiment is a spur gear keyed for rotation with the rotor shaft 134, and therefore with the rotor 132.
  • the gear assembly 148 includes a rotatable gear carrier 150, which is mounted for rotation on bearings 152, 154.
  • the gear carrier 150 carries a shaft 156 which is mounted for rotation in bearings 158, 160.
  • First and second gears 162, 164 are keyed to rotate in unison with the shaft 156.
  • the first gear 162 is meshed with the rotor gear 146, and the second gear 164 is meshed with the stator gear 144.
  • the gear carrier 150 supports a spur gear 166 such that the two elements 150, 166 rotate in unison.
  • the gear 166 is meshed with another spur gear 168, which is in turn keyed to a shaft of a torque gate 170.
  • the torque gate 170 includes a variable volume hydraulic pump 172. Hydraulic fluid from the pump 172 is applied via a conduit 176 to a variable volume hydraulic motor 174. The variable volume hydraulic motor 174 is coupled to drive the rotor shaft 134.
  • the torque gate 170 is a torque control device selected as appropriate for the particular application.
  • the torque gate 170 in Figure 7 retards rotation of the gear assembly 148 and allows the gear assembly 148 to transmit energy between the stator 130 and the rotor 132.
  • the torque gate 170 can take many forms. In small machines such as hand drill motors, the torque gate 170 may take the form of a current-controlled mechanical friction brake 178 which retards rotation of a brake disc 180 that rotates with the rotor shaft 134, as shown in Figure 8. On a large machine such as an oil rig draw works motor, the torque gate can take the form shown in Figure 7. With this arrangement, the hydraulic motor 174 recovers torque energy from the pump 172 back into the electromagnetic machine 110, thereby providing particularly efficient operation.
  • Figure 9 shows another embodiment 110' of the electromagnetic machine of this invention
  • the same reference numerals are used as in Figure 7 for comparable parts
  • the same reference numerals with an added prime are used for parts which, though somewhat different in configuration, perform similar or related functions as the corresponding unp ⁇ med reference numeral elements of Figure 7
  • the following discussion will take up only the elements associated with the primed reference numerals in Figure 9
  • a stator gear 144' takes the form of a bevel gear, as does the rotor gear 146'
  • the gear assembly 148' includes a gear carrier 150' in the form of a differential gear cage
  • the gear carrier 150' is mounted for rotation by bearings 152', 154', and the gear carrier 150' supports two collmear shafts 156'
  • the shafts 156' support respective first and second gears 162', 164'
  • the gears 162', 164' are bevel gears which are both in constant mesh both with the stator gear 144' and the rotor gear 146'
  • This assembly forms a mechanical differential
  • the gear assembly 148' can include only a single gear 162', 164'
  • the gear carrier 150' supports on its exterior surface a spur gear 166' which is meshed with a spur gear 168' that supplies rotation to a torque gate 170'
  • the torque gate 170' controls rotation of the gear assembly 148' to operate at a speed between zero and 900 rpm (for a 1 ,800 rpm motor)
  • This arrangement transfers approximately one-half of the power from the stator 130 to the output shaft 112 at full speed, bypassing the gear unit
  • the torque gate 170" controls output speed in a manner similar to that discussed above
  • Figure 10 shows a variation of the embodiment of Figure 9
  • double-primed reference numerals have been used to show corresponding elements to those marked with single-primed reference numerals in Figure 9
  • the rotor shaft 134 and the flange 116 are shown in fragmentary form, and the remaining elements of the stator and the rotor are not shown
  • the unshown elements can be identical to those shown in Figure 9
  • the gear assembly 148" includes only the gear carrier 150", the shaft 156", the gear 164", and the gear 166".
  • the torque gate 170" takes the form of a variable volume hydraulic pump 172" which is coupled via a conduit 176" to a variable volume hydraulic motor 174".
  • the variable volume hydraulic motor 174" rotates a shaft 178" which is keyed to a gear 180".
  • the gear 180" is in constant mesh with a gear 182" that is in turn keyed to the sleeve 118 and thereby to the stator (not shown).
  • the hydraulic motor 174" applies torque to the stator so that this torque is added to the torque in the output shaft 112 ( Figure 9) developed as a result of the action of the pump 172".
  • the hydraulic pump 172" and the hydraulic motor 174" are both variable volume units.
  • the hydraulic pump 172" When the output shaft is at full speed, the hydraulic pump 172" will be at zero speed, with the volume at full.
  • the hydraulic motor 174" will be at full speed with the volume at zero.
  • the hydraulic pump 172" will develop full torque load and zero hydraulic flow.
  • the hydraulic motor 174" When the output shaft is at zero speed, the hydraulic motor 174" will be at zero speed and full volume.
  • the pump 172" will be at full speed with the volume at zero.
  • the hydraulic motor 174" will develop full torque and zero hydraulic flow.
  • the output shaft can be modulated both in torque and speed to meet the needed load requirements.
  • Figure 10 will be nearly 100% energy efficient at zero and full speed, and will exhibit a somewhat reduced efficiency at intermediate speeds.
  • Figure 11 shows a further variation of the embodiment of Figure 9
  • the rotor and stator though not shown in Figure 11 , can be identical to the structures shown in Figure 9.
  • Corresponding elements in Figures 9 and 11 are provided with the same reference numerals.
  • Figure 11 shows a variation in which the hydraulic motor 174" is coupled by a journalled shaft 184" and a bevel gear 186" to a second bevel gear 188".
  • the second bevel gear 188" is mounted on a rotatable shaft 190" that is in turn mounted to a gear carrier 165".
  • the gear carrier 165" is keyed to both the gear carrier 150" and to the gear 166".
  • the gear 188" meshes with a bevel gear 192" that is keyed to the shaft 134.
  • the power developed in the hydraulic pump 172" is used by the motor 174" to slow the shaft 134, thereby increasing the speed of the output shaft 112 ( Figure 9).
  • the function of the torque gate 170 is to select or adjust the torque and thereby the power that the rotor 132 can deliver through the gears 146,
  • the desired speed under the currently prevailing load for the output shaft 112 is easily obtained by adjusting the torque gate 170 to allow sufficient power to pass from the rotor 132 through the gear train 146, 162, 164, 144 to the stator 130 and thereby to the output shaft 112.
  • the torque gate should be sized to handle the torque of the shaft 112.
  • the torque developed energy in the stator winding 122 is added to the shaft 112 directly and does not go through the gear unit.
  • the electrical power generated by the electromagnetic machine 110 increases as the torque gate 170 is set to higher torques and decreases as the torque gate 170 is set to lower torques.
  • Tables 1 and 2 provide the tooth count for selected gears, and the gear speed for selected gears in two modes of operation
  • the center column of Table 2 is for the output shaft 112 at a standstill, and the right hand column of Table 2 is for the output shaft 112 at full design speed of 300 rpm. Note that when the output shaft 112 is at 0 rpm the gear 166 and therefore the gear assembly 150 rotate at 300 rpm.
  • the following general considerations apply to the embodiments described above. In general, in order for the electrical rotating magnetic flux energy imparted to the stator to be added directly to the output shaft, the stator and the rotor are rotated in opposite directions.
  • this braking force When a braking force is applied to the rotating assembly, this braking force will tend to slow the assembly down, thereby causing the stator to rotate. If a driving force using the energy developed by the braking force is added directly to the rotor, this driving force will not aid the torque gate or braking force in developing torque at the output shaft. If a driving force using the energy developed by the braking force is added to the rotor through a mechanical differential to slow the rotor down, this driving force will aid the torque gate or braking force in developing torque at the output shaft. If the developed torque in the output shaft is greater than the load torque, the output shaft will accelerate, and can accelerate to full design speed. If the developed torque in the output shaft is less than the load torque, the output shaft can decelerate. If necessary, the output shaft can decelerate through zero speed and begin to rotate in a reverse direction.
  • the electromagnetic machines described above can operate as a variable speed motor, as a variable speed generator, or as a variable speed dynamic brake with equal ease.
  • the electromagnetic machines 30, 50, 70, 110, 110' provide a number of important advantages.
  • the speed of rotation of the output shaft 112 can be made to vary without altering the frequency, waveform, or voltage of the applied power to the stator windings.
  • that motor can be made into a variable speed gear motor using the techniques discussed above.
  • the machines 30, 50, 70, 110, 110' provide an inherent torque limit to limit shock loads jnto the machine. Shock loads greater than this applied torque cause a speed reduction rather than increased torque in the driver.
  • the control energy required to operate the torque gate 170, 170', 170" is zero when the output shaft 112 is operating at full speed, and this control energy is comparatively small at speeds lower than full speed.
  • the rotor runs at design full speed relative to the stator at all output speeds of the shaft. For this reason cooling of the stator winding and the rotor is always sufficient.
  • the machines 30, 50, 70, 110, 110' can operate at any speed, including a stalled condition, with full output torque on the shaft without damaging the stator winding or the rotor.
  • the machines 30, 50, 70, 110, 110' when operating as a motor can always start at no load with zero torque at 42, 62, 170, 170', 170".
  • the stator develops horsepower in the output shaft in the ratio of the speed of the shaft to the relative speed of the rotor to the stator.
  • the gear train can be modified substantially from the illustrated gear train.
  • a spur gear may be substituted for the gear 144, and a reversing idler gear may be used between this spur gear and the gear 164.
  • the gear train operates as a mechanical differential. This allows speed control for the shaft 112 as a result of torque applied by the torque gate 170.
  • the differential gearing permits control of speed at relatively low torque and low speed, providing a relatively low power loss of control energy while the machine 110 operates at a high power level.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Un moteur électromagnétique (69), un générateur ou un frein dynamique à vitesse variable comprend un rotor (52) et un stator (56), montés tous deux de façon à tourner par rapport à un élément de référence. Un arbre moteur est couplé à l'un des éléments: rotor ou stator, tandis qu'une charge variable contrôlée est couplée à l'autre de ces éléments. La charge variable réagit par rapport à l'élément de référence de façon à appliquer un couple variable qui tend à retarder la rotation de l'autre des éléments: rotor ou stator. Ainsi, la vitesse de l'arbre moteur et la puissance transmise par celui-ci sont contrôlées. Un autre moteur électromagnétique, générateur ou frein dynamique à vitesse variable comprend un rotor comportant une roue de rotor (74) et un stator comportant une roue de stator (76). La roue (76) est couplée à la roue de rotor de façon à former un différentiel mécanique qui fait tourner le rotor et le stator en sens inverse lorsque la roue tourne.
PCT/US1997/004733 1996-03-27 1997-03-24 Appareil electromagnetique a vitesse variable WO1997036362A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU25436/97A AU2543697A (en) 1996-03-27 1997-03-24 Variable speed electromagnetic machine

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US62490696A 1996-03-27 1996-03-27
US08/624,906 1996-03-27
US79828597A 1997-02-07 1997-02-07
US08/798,285 1997-02-07

Publications (1)

Publication Number Publication Date
WO1997036362A1 true WO1997036362A1 (fr) 1997-10-02

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PCT/US1997/004733 WO1997036362A1 (fr) 1996-03-27 1997-03-24 Appareil electromagnetique a vitesse variable

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WO (1) WO1997036362A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000037350A1 (fr) * 1998-12-22 2000-06-29 Otis Elevator Company Machinerie d'ascenseur avec rotors contre-rotatifs
FR3018880A1 (fr) * 2014-03-24 2015-09-25 Messier Bugatti Dowty Actionneur electromecanique de frein a blocage de parc pour aeronef
EP2728717A4 (fr) * 2011-05-05 2016-04-27 Yuchi Wang Moteur générateur pour véhicule
US20230011200A1 (en) * 2021-07-08 2023-01-12 Differential Dynamics Corporation Converting variable renewable energy to constant frequency electricity by a voltage regulated speed converter, a voltage-controlled motor generator set or a voltage converter

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2564741A (en) * 1947-03-06 1951-08-21 Vermillion Lewis Safford Dynamoelectric machine
US3675507A (en) * 1969-10-03 1972-07-11 Takekawa Iron Works Hydraulic transmission mechanism for heavy rolling stocks and the like
US4056746A (en) * 1974-12-20 1977-11-01 Burtis Wilson A Counterrotation electric motor
US4110676A (en) * 1976-08-30 1978-08-29 Reliance Electric Company Dynamoelectric machine and tachometer
US5508574A (en) * 1994-11-23 1996-04-16 Vlock; Alexander Vehicle transmission system with variable speed drive

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2564741A (en) * 1947-03-06 1951-08-21 Vermillion Lewis Safford Dynamoelectric machine
US3675507A (en) * 1969-10-03 1972-07-11 Takekawa Iron Works Hydraulic transmission mechanism for heavy rolling stocks and the like
US4056746A (en) * 1974-12-20 1977-11-01 Burtis Wilson A Counterrotation electric motor
US4110676A (en) * 1976-08-30 1978-08-29 Reliance Electric Company Dynamoelectric machine and tachometer
US5508574A (en) * 1994-11-23 1996-04-16 Vlock; Alexander Vehicle transmission system with variable speed drive

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000037350A1 (fr) * 1998-12-22 2000-06-29 Otis Elevator Company Machinerie d'ascenseur avec rotors contre-rotatifs
US6325177B1 (en) 1998-12-22 2001-12-04 Otis Elevator Company Elevator machine with counter-rotating rotors
JP2002532367A (ja) * 1998-12-22 2002-10-02 オーチス エレベータ カンパニー 反転式ローターを有するエレベーター機械
CN1108976C (zh) * 1998-12-22 2003-05-21 奥蒂斯电梯公司 带有相对旋转的转子的电梯机械
EP2728717A4 (fr) * 2011-05-05 2016-04-27 Yuchi Wang Moteur générateur pour véhicule
FR3018880A1 (fr) * 2014-03-24 2015-09-25 Messier Bugatti Dowty Actionneur electromecanique de frein a blocage de parc pour aeronef
EP2944521A1 (fr) * 2014-03-24 2015-11-18 Messier-Bugatti-Dowty Actionneur électromécanique de frein à blocage de parc pour aéronef
US20230011200A1 (en) * 2021-07-08 2023-01-12 Differential Dynamics Corporation Converting variable renewable energy to constant frequency electricity by a voltage regulated speed converter, a voltage-controlled motor generator set or a voltage converter

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