WO2014039603A1 - Appareil d'entraînement - Google Patents

Appareil d'entraînement Download PDF

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Publication number
WO2014039603A1
WO2014039603A1 PCT/US2013/058135 US2013058135W WO2014039603A1 WO 2014039603 A1 WO2014039603 A1 WO 2014039603A1 US 2013058135 W US2013058135 W US 2013058135W WO 2014039603 A1 WO2014039603 A1 WO 2014039603A1
Authority
WO
WIPO (PCT)
Prior art keywords
mass
motor
drive member
energy
drive
Prior art date
Application number
PCT/US2013/058135
Other languages
English (en)
Inventor
John E. HOFFMAN JR
Richard A. HOFFMAN SR
James M. Pagliaro
Original Assignee
Newton Engine Corporation
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 Newton Engine Corporation filed Critical Newton Engine Corporation
Priority to TW102140923A priority Critical patent/TW201509530A/zh
Publication of WO2014039603A1 publication Critical patent/WO2014039603A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C25/00—Control arrangements specially adapted for crushing or disintegrating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G3/00—Other motors, e.g. gravity or inertia motors
    • F03G3/08—Other motors, e.g. gravity or inertia motors using flywheels
    • 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
    • F16H33/00—Gearings based on repeated accumulation and delivery of energy
    • F16H33/02—Rotary transmissions with mechanical accumulators, e.g. weights, springs, intermittently-connected flywheels

Definitions

  • the disclosure relates generally to the field of motors that impart force to drive a drive member, and in particular to motors that include backup energy storage to assist in driving the drive member.
  • Electric motors hydraulic motors, liquid- fueled engines, and the like are types of drive apparatus that impart force to drive a drive member attached to a load.
  • a motor imparts torque to rotate the drive member.
  • the force applied to the drive member may vary due to environmental factors affecting the load -- such as shock or other transient operating conditions.
  • the rocks being crushed by a rock crushing machine may vary in size or type and occasionally a larger or harder rock is encountered during the crushing process.
  • the motor may be required to deliver more torque to the rock crushing machine for a relatively short time to initiate crushing of the larger rock .
  • a drive apparatus for driving a drive member that includes an energy storage device -- preferably formed as a mechanical energy storage device -- storing backup energy.
  • a mechanical energy storage device stores energy as kinetic energy in a moving body or bodies .
  • the stored backup energy is available as an energy source when the drive apparatus is required to deliver increased transient force or torque to the drive member.
  • the mechanical energy storage device is itself re-energized or re-charged by a separate motor connected to an independent energy source (such as the electric power grid or a chemical fuel) while the mechanical energy storage device is not operatively connected to the load.
  • an independent energy source such as the electric power grid or a chemical fuel
  • This is in contrast to, for example, a conventional hit-and-miss engine having a flywheel in which the flywheel is recharged by the engine while the flywheel is connected to the load.
  • the motor recharges the mechanical energy storage device only when the drive apparatus is not connected to the drive member, the motor in possible embodiments of the drive apparatus is not exposed to the high transient load demands that the motor might experience if directly driving the drive member .
  • the motor can be a conventional electric or fluid motor, an internal combustion engine, or a prime mover utilizing a different power source.
  • the term "motor” is not limited to exclusively electric motors, but includes other prime movers such as engines that convert energy from an energy source independent of the drive apparatus to mechanical energy.
  • the mechanical energy storage device forms part of a power transmission unit of the drive apparatus that supplies energy/torque to the drive member.
  • the mechanical energy storage device is preferably a flywheel.
  • the power transmission unit includes a lever pivotable in a vertical plane about a horizontal pivot axis.
  • the lever is connected to the flywheel through a first transmission that converts between oscillatory motion of the lever and rotational motion of the flywheel.
  • the lever is connected to the drive member by a second transmission that converts oscillatory motion of the lever to rotary or linear motion of the drive member .
  • a mass is attached to the lever spaced away from the pivot axis.
  • the mass is movable between vertically-spaced raised and lowered positions by oscillatory, cyclical motion of the lever about the pivot axis.
  • the lever is connected to the drive member when the mass is moving from the raised position to the lowered position for transmitting energy/torque to the drive member and is disconnected from the drive member when the mass is moving from the lowered position to the raised position.
  • the drive apparatus In operation, the drive apparatus is first disconnected from the load and the flywheel is brought up to nominal operating speed by the motor to store energy in the flywheel. When the flywheel has reached nominal operating speed, the drive apparatus is connected to the load and the drive apparatus enters its normal operating mode.
  • the power transmission unit In normal operating mode, while the mass is moving from the raised position to the lowered position the power transmission unit is in the power transmission portion of the beam oscillation cycle wherein torque/energy is being transmitted to the drive member. While the mass is moving from the lowered position to the raised position the power transmission unit is in its no-load portion of the beam oscillation cycle wherein no torque/energy is being transmitted to the drive member.
  • the mass attached to the lever preferably has sufficient weight for the conversion of gravitational potential energy to work during the power transmission portion of the oscillation cycle to both displace the beam and drive the drive member under normal load. If a higher transient torque/energy is needed during the power transmission portion of an oscillation cycle, the required energy can be extracted from the flywheel.
  • the nominal energy stored in the flywheel is substantially greater than the amount of energy released by the mass moving from the raised position to the lowered position for adequate energy reserve for foreseeable transient conditions of operation.
  • the energy stored in the flywheel may, for example, be more than ten times or more greater than the energy released by the mass. The energy excess enables the flywheel to resist stalling or stopping during an oscillation cycle and typically results in a relatively small drop in flywheel RPM during oscillation cycles.
  • the drive apparatus in possible embodiments further preferably includes a control system that operatively connects the motor to the power transmission unit to recharge the flywheel during the no-load portion of the oscillation cycle and disconnects the motor from the power transmission unit during the power transmission portion of the oscillation cycle .
  • the drive apparatus includes a second, additional power transmission unit.
  • the two power transmission units operate in tandem, with the power transmission portion of the oscillation cycle of one power transmission unit occurring during the no-load portion of the power transmission cycle of the other power transmission unit so that the two power transmission units substantially continuously transmit torque/energy to the drive member.
  • Figure 1 is a front-left perspective view of a drive apparatus
  • Figure 2 is a right-side view of the drive apparatus
  • Figure 3 is a front view of the drive apparatus
  • Figure 4 is a top view of the drive apparatus
  • Figure 5 is left-side view of the drive apparatus
  • Figure 6 is a front-left perspective view of a second embodiment drive apparatus ;
  • Figure 7 is a right-side view of the second embodiment drive apparatus
  • Figure 8 is a front view of the second embodiment drive apparatus ;
  • Figure 9 is a top view of the second embodiment drive apparatus .
  • Figure 10 is left-side view of the second embodiment drive apparatus .
  • FIGS 1-5 illustrate a first embodiment drive apparatus 10.
  • the drive apparatus 10 includes a power transmission unit 12 that transmits output power to a drive member 14, and a motor 16 that provides power to the power transmission unit 12 through a first transmission 18.
  • the illustrated motor 16 is an AC electric motor (induction motor) having a rated speed of about 1700 RPM (the rated speed is the speed the motor runs when fully loaded and supplied rated nameplate voltage) .
  • a DC electric motor, a hydraulic motor, or other type of motor could be adapted to supply power to the power transmission unit 12.
  • the power transmission unit 12 includes a beam or lever 20 connected to a mechanical energy storage device 22, the illustrated device 22 formed as a flywheel.
  • the beam 20 and the flywheel 22 are interconnected to each other through a second transmission 24.
  • the beam 20 is connected to the drive member 14 by a third transmission 26.
  • the beam 20 is formed from an elongate, hollow steel pipe.
  • the beam 20 is pivotally mounted to a stationary frame 28 to form a class 1 lever for pivotal, oscillating movement in a vertical plane about a horizontal pivot axis 30 intermediate the opposite ends of the beam 20.
  • the beam 20 includes a first beam portion 32 extending away from one side of the pivot axis 30 and a second beam portion 34 extending away from the other side of the pivot axis 30. Oscillating movement of the beam 20 causes the first beam portion 32 to move in the vertical plane between a raised position shown in Figure 1 and a lowered position (not shown) .
  • the illustrated beam 20 has an angular displacement of 24.6 degrees about the pivot axis 30 moving to and from raised and lowered positions of the first beam portion 32.
  • a mass 36 is fixedly attached to the free end of the first beam portion 32.
  • the mass 36 is spaced away from the pivot axis 30 so that the weight of the mass 36 urges the first beam portion 32 to move to the lowered position.
  • the mass 36 preferably has weight significantly greater than that of the beam 20 and has sufficient weight to force the first beam portion 32 to it lowered position. That is, with the drive apparatus 10 disconnected from the load and the first portion of the beam is at the highest position with the flywheel stationary, the mass is capable of initiating rotation of the flywheel without assistance from the motor.
  • Oscillation of the beam 20 moves the mass 36 a vertical distance between raised and lowered positions of the mass 36, the raised and lowered positions of the mass 36 corresponding to the raised and lowered positions respectively of the first beam portion 32.
  • the flywheel 22 is mounted to the frame 28 for rotation about a flywheel axis 38.
  • the illustrated flywheel axis 38 is a horizontal axis but in other embodiments the flywheel axis 38 could be a vertical axis or could be disposed at some other angle between horizontal and vertical.
  • a flywheel drive shaft 40 is supported on the frame 28 by pillow blocks and extends along the flywheel axis 38.
  • the flywheel 22 is fixedly attached to the shaft 40 intermediate the ends of the shaft for conjoint rotation with the drive shaft 40.
  • the second transmission 24 is configured to convert between oscillatory motion of the beam 20 about the pivot axis 30 and rotary motion of the flywheel 22.
  • the second transmission 24 includes a link mechanism 42 connected to the beam 20 and to a drive shaft 43 rotatably mounted on the frame 28.
  • the drive shaft 43 is connected to the flywheel drive shaft 40 through a gear box 44.
  • the illustrated link mechanism 42 is a crank-rocker mechanism that includes a link 46A pivotally connected to the upper side of the second beam portion 34 to transmit and receive oscillatory motion of the beam 20 and a link 46B non- rotatably connected to the drive shaft 43 to transmit and receive rotary motion of the flywheel 22 via the gearbox 44.
  • the link mechanism 42 has a transmission ratio of one revolution of the drive shaft 43 for each oscillation of the beam 20.
  • the third transmission 26 is configured to convert between oscillatory motion of the beam 20 and rotary motion of the drive member 14.
  • the beam 20 extends through a pipe sleeve 48 fixedly attached to the beam 20.
  • the pipe sleeve 48 has a pair of pipe stubs 50 that receive a shaft 52 rotatably mounted on the frame 28 and defining the pivot axis 30.
  • the shaft 52 oscillates with angular displacement about the pivot axis 30 with oscillation of the beam 20.
  • An end of the shaft 52 is attached to a one-way clutch 54 having an input member 56 non-rotatably connected to the shaft 52 and an output member 58 forming the drive member 14.
  • the drive member 14 is to be driven by the power transmission unit 12 only when the first beam portion 32 is moving from the raised position to the lowered position.
  • the one-way clutch 54 is configured for conjoint rotary movement of the input member 56 and the output member 58 that transmits torque therebetween only when the input member 56 is rotating in the direction corresponding to motion of the first beam portion 32 from the raised position to the lowered position.
  • the clutch input member 56 rotates essentially freely about the clutch output member 58 whereby the drive member 14 is effectively disconnected from the power transmission unit 12.
  • the first transmission 18 includes a shaft 60 coaxial with the motor shaft 62 of the motor 16 and connected to the shaft 62 by an electric clutch 64 that forms part of a control system.
  • a belt and pulley arrangement 66 connects the shaft 60 with the flywheel shaft 40.
  • the motor 16 is connected to the first transmission 18 to transmit torque/energy to the power transmission unit 12 only when the first beam portion 32 is moving from the lowered position to the raised position.
  • the control system uses the clutch 64 to selectively connect the transmission shaft 60 with the motor shaft 62. The clutch 64 is engaged while the first beam portion 32 is moving from the lowered position to the raised position and the clutch 64 is disengaged while the first beam portion 32 is moving from the raised position to the lowered position.
  • control system includes a hemispheric disk (not shown) attached to the free end of the shaft 43 that intermittently blocks an electric eye (not shown) with rotation of the shaft 43.
  • the eye is blocked during the load portion of the beam oscillation cycle and is not blocked during the no-load portion of the beam oscillation cycle.
  • the control system utilizes blocking and unblocking of the eye as control signals determining when to engage and disengage the electric clutch 64.
  • limit switches attached to the beam 20 or other known sensor/switch arrangements can be used to sense or determine the load and no-load portions of the cycle.
  • FIGS 1-5 illustrate a test load 70 attached to the output clutch member 58/drive member 14.
  • the load 70 includes a shaft 72 attached to the clutch member 58 that drives a load flywheel 74 through a gear box 76.
  • control system 68 is bypassed to enable the motor 16 to continuously supply power to the power transmission unit 12 until the flywheel 22 reaches the desired nominal steady- state operational speed.
  • the motor 16 is connected to an appropriate energy source to run the motor; the illustrated AC motor 16 is connected to the electric utility grid.
  • the load 70 is disconnected from the clutch member 58.
  • Torque is transmitted from the motor 16 to the flywheel 22 through the first transmission 18, causing the flywheel 22 to begin rotating.
  • Rotation of the flywheel 22 causes the beam 20 to begin oscillating by action of the second transmission 24.
  • the mass 36 rises and falls in the vertical plane.
  • the motor 16 must provide sufficient torque to raise the mass 36, but after the flywheel 22 reaches sufficient rotational speed there is enough energy stored in the flywheel 22 alone to raise the mass 36.
  • the motor 16 can initially raise the mass 36 slowly to reduce horsepower requirements for the motor 16 at startup.
  • the motor 16 accelerates the flywheel 22 until the flywheel 22 reaches the nominal operating speed of 350 revolutions per minute.
  • the transmission ratio of the first transmission in the illustrated embodiment is such that the motor 16 is at rated speed when the flywheel is rotating 350 RPM.
  • the transmission ratio of the second transmission 24 in the illustrated embodiment is such that the flywheel rotation speed of 350 RMP generates 32 oscillations per minute of the beam 20 about the pivot axis 30 when the motor 12 reaches synchronous speed under load.
  • the control system 68 is now enabled so that the motor 16 supplies energy to the power transmission unit 12 only when the first beam portion 32 is moving from the raised position to the lowered position.
  • the drive member 14 is now operationally attached to the load 70 for transmission of power from the power transmission unit 12 to the load.
  • the power transmission unit 12 When the first beam portion 32 is moving from the raised position to the lowered position, the power transmission unit 12 is in the power transmission portion of the beam oscillation cycle.
  • the one-way clutch 54 is engaged to transmit torque through the output member 58/drive member 14 and to the load.
  • the one-way clutch 54 rotates the drive member 24.6 degrees during the power transmission portion of the beam oscillation cycle.
  • the energy transmitted through the drive member 14 driving the load during the power transmission cycle portion is provided substantially solely by the mass 32 dropping a vertical distance of 15 inches and from the rotational energy stored in the flywheel 22.
  • the illustrated flywheel 22 has a moment of inertia of about 1900 in-ibf-sec-sec and so stores about 51 times the energy released by the fall of the mass 36.
  • the mass 36 is preferably sized to provide sufficient gravitational potential energy when at the raised position to power the drive member during the power transmission portion of the beam oscillation cycle. That is, the mass 36 is preferably sized to provide sufficient potential energy to both pivot the beam 20 and nominally drive the load during the power transmission portion of the beam oscillation cycle. If a shock or transient condition is encountered requiring application of a higher drive force to drive the drive member during the power transmission portion, the increased energy/torque demand is provided by the energy stored in flywheel 22.
  • the power transmission unit 12 When the first beam portion 32 is moving from the lowered position to the raised position, the power transmission unit 12 is in its no-load portion of the beam oscillation cycle.
  • the one-way clutch 54 disengages the clutch output member 58/drive member 14 from the power transmission unit 12 and the power transmission unit 12 does not transfer energy to the load.
  • the control system 68 acts to engage the electric clutch 64, enabling the motor 16 to transfer energy to the flywheel 22.
  • the energy transferred to the flywheel 22 "recharges" the power transmission unit 12 and re- supplies the energy transferred to the load during the power transmission portion of the oscillation cycle and any energy loss associated with friction losses, windage losses, and the like.
  • the motor 16 applies torque to the flywheel 22 urging the flywheel 22 back up to speed.
  • the flywheel 22 also is working to raise the mass 36, and the motor 16 continues to apply torque while the motor 16 is attempting to regain rated speed.
  • the flywheel 22 If the flywheel 22 is rotating faster than its nominal 350 RMP at the beginning of the no-load portion of the oscillation cycle, the additional energy transferred to the flywheel 22 is used in initially raising the mass 36. This slows down the flywheel 22. When the flywheel speed drops below 350 RPM, the motor 16 transfers torque/energy to the flywheel 22 as the motor attempts to regain rated speed.
  • the flywheel 22 If the flywheel 22 is rotating at or slower than its nominal 350 RMP at the beginning of the no-load portion of the oscillation cycle, the energy transferred from the flywheel 22 raising the mass 36 causes the flywheel 22 to slow down.
  • the motor 16 applies torque to the flywheel 22 as the motor attempts to regain rated speed.
  • the motor 16 transfers energy smoothly to the flywheel 22 without experiencing shock loads that the motor 16 might have otherwise experienced if the motor 16 were driving the load directly. If a transient energy/torque supplied by the flywheel 22 to the load during a power transmission portion of an oscillation cycle is sufficiently large, it may take more than one oscillation cycle for the motor 16 to recharge the power transmission unit. If necessary, the flywheel 22 may supply transient energy/torque for multiple transients before the motor 16 fully recharges the power transmission unit 12.
  • the drive apparatus 10 may include design features or devices (such as, for a non- limiting example, an overload clutch) that act to disconnect the load from the power transmission unit 12 and resist mechanical overload of the power transmission unit 12 in the event that the flywheel 22 is asked to extract rotational energy at an excessive rate.
  • an overload clutch such as, for a non- limiting example, an overload clutch
  • the design of the drive apparatus 10 can be modified from the illustrated embodiment to meet the engineering requirements of a given application.
  • the weight of the mass 36, the length of the beam 20, the position of the beam 20 with respect to the pivot axis 30, the transmission ratios of the transmission units, the size and type of motor 16, and the inertia and nominal rotational speed of the flywheel 22 can each vary from the illustrated embodiment to meet the specific energy/torque requirements imposed by a load application and its operating environment.
  • the third transmission 26 may be configured to generate linear, rather than rotary, movement of the drive member 14.
  • a more sophisticated motor control system may be used to regulate the speed of the motor 16 when transferring energy from the motor 16 to the power transmission unit 12.
  • a variable frequency drive (VFD) may be used in controlling motor speed of an induction motor.
  • the motor 16 may be permanently connected to the flywheel 22 by the first transmission 18 -- that is, the first transmission 18 is capable of transmitting torque/energy between the induction motor 16 and the flywheel 22 during an entire oscillation cycle. Changes in speed of the flywheel 22 are reflected in the attempted changes in speed of the induction motor 16 applied through the first transmission 18 urging the motor's operating speed to differ from the motor's rated speed.
  • the clutch 64 is eliminated.
  • the control system 68 operates instead as a "passive" control system that utilizes the speed-torque curve of the motor 16 and differences in motor speed with respect to the motor's rated speed to, in effect, operatively connect and disconnect the motor 16 and the flywheel 22. There would be no active changing of the physical configuration of the first transmission 18 as would occur through engaging and disengaging the clutch 64.
  • control system 68 acts to connect and disconnect the motor from the motor's energy source to thereby effectively operatively connect and disconnect the motor from the flywheel.
  • the drive apparatus 10 drives the drive member 14 during only half the beam oscillation cycle.
  • Figures 6-10 illustrate a second embodiment drive apparatus 110 that includes a pair of power transmission units operating in tandem to drive a common drive member 114 essentially continuously during operation of the drive apparatus 110.
  • the drive apparatus 110 includes a first power transmission unit 12A and a second, like power transmission unit 12B.
  • Each power transmission unit 12A, 12B is substantially like the power transmission unit 12 of the drive apparatus 10 and so only the differences will be discussed, with corresponding reference numbers used for corresponding features .
  • the power transmission units 12A, 12B operate in tandem to supply substantially continuous torque/energy to the common drive member 114 formed by a common shaft 52.
  • the shaft 52 is keyed to the inner portions of a pair of one-way clutches (each one-way clutch similar in operation to the one-way clutch 54) mounted in respective sleeves 48.
  • the outer portion of one one-way clutch is driven by one beam 20 and the outer portion of the other one-way clutch is driven by the other beam 20.
  • Each one-way clutch transmits torque from the outer portion of the clutch to the inner portion of the oneway clutch and from there to the shaft 52 only during the load cycle of the beam 20 driving the one-way clutch.
  • the pivot axes 30 are coaxial with one another, with the masses 36 located on the same side of the common pivot axis 30. This way, downward motion of each first beam portion 32 drives the drive member 14 the same direction of rotation.
  • the beams 20 of the power transmission units 12A, 12B oscillate out of phase with each other ( Figures 6-10 illustrate the power transmission units 112A, 112B when the masses 36 are vertically adjacent each other) .
  • Figures 6-10 illustrate the power transmission units 112A, 112B when the masses 36 are vertically adjacent each other
  • the power transmission units 12A, 12B are each recharged by a common DC motor 16 that is connected to a DC battery pack 116.
  • the power pack 116 receives its energy from the electric grid.
  • the power transmission units 12A, 12B are positioned in a side-by-side relationship but with the flywheels 22 and gear boxes 44 located on opposite sides of the apparatus 110.
  • the flywheels 22 are non-rotatably mounted on a common drive shaft connected to the motor 16 and together combine to form, in effect, a single common flywheel (consisting of the two disks 22) shared in common with both power transmission units.
  • the motor 16 is in effect continuously recharging the flywheels 22 for the energy needed to raise the masses 36 and to drive the drive member. Due to this continuous recharging, the motor 16 is connected to the flywheels 22 throughout the oscillation cycles of both power transmission units 12A, 12B.
  • Embodiments that include multiple power transmission units (whether having separate mechanical energy storage devices or having a shared, common mechanical energy storage device) recharged by a common, single motor may include a control system that limits force or torque applied by the motor when recharging the power transmission units.
  • a control system coupled to an AC induction motor may include a reduced voltage torque limiter.
  • a power transmission unit may require more than one load cycle to be recharged. Limiting the force or torque applied by the motor may be acceptable in many applications even if recharging takes more than one load cycle occasionally during use .
  • each unit may include its own non- shared motor to recharge the energy storage device associated with the unit.
  • a single flywheel can be used as a common mechanical storage device for both power transmission units.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Supply And Distribution Of Alternating Current (AREA)

Abstract

L'invention porte sur un appareil d'entraînement pour entraîner un élément d'entraînement, lequel appareil comprend un stockage mécanique d'énergie de sauvegarde. L'énergie stockée est utilisée pour délivrer une force transitoire élevée à l'élément d'entraînement lorsque cela est nécessaire. Le stockage mécanique est réalimenté par un moteur séparé quand l'appareil d'entraînement n'est pas relié de façon fonctionnelle à l'élément d'entraînement, de telle sorte que le moteur n'est pas exposé à des charges transitoires élevées.
PCT/US2013/058135 2012-09-06 2013-09-05 Appareil d'entraînement WO2014039603A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
TW102140923A TW201509530A (zh) 2013-09-05 2013-11-11 驅動裝置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201261697471P 2012-09-06 2012-09-06
US61/697,471 2012-09-06

Publications (1)

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WO2014039603A1 true WO2014039603A1 (fr) 2014-03-13

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3251749A1 (fr) * 2016-06-01 2017-12-06 Manuel Lindner Broyeur de dechets mobile dote d'un entrainement hybride en serie
EP3251748A1 (fr) * 2016-06-01 2017-12-06 Manuel Lindner Broyeur de déchets mobile doté d'un entrainement hybride parallèle
EP3251750A1 (fr) * 2016-06-01 2017-12-06 Manuel Lindner Dispositif broyeur de dechets fixe comprenant un accumulateur d'energie

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Publication number Priority date Publication date Assignee Title
US3610362A (en) * 1968-12-21 1971-10-05 Nippon Denso Co Antiskid device with clutch releasing means
US3749213A (en) * 1970-09-18 1973-07-31 Luk Lamellen & Kupplungsbau Friction clutch assembly
US3805514A (en) * 1973-01-05 1974-04-23 A Bodine Power system utilizing free-piston engine and torsionally resonant transmission
US4875699A (en) * 1985-12-16 1989-10-24 Shmuel Levavi Human powered vehicles and mechanisms particularly useful therein
US20110187101A1 (en) * 2005-11-07 2011-08-04 Beane Glenn L System for Producing Energy Through the Action of Waves

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3610362A (en) * 1968-12-21 1971-10-05 Nippon Denso Co Antiskid device with clutch releasing means
US3749213A (en) * 1970-09-18 1973-07-31 Luk Lamellen & Kupplungsbau Friction clutch assembly
US3805514A (en) * 1973-01-05 1974-04-23 A Bodine Power system utilizing free-piston engine and torsionally resonant transmission
US4875699A (en) * 1985-12-16 1989-10-24 Shmuel Levavi Human powered vehicles and mechanisms particularly useful therein
US20110187101A1 (en) * 2005-11-07 2011-08-04 Beane Glenn L System for Producing Energy Through the Action of Waves

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3251749A1 (fr) * 2016-06-01 2017-12-06 Manuel Lindner Broyeur de dechets mobile dote d'un entrainement hybride en serie
EP3251748A1 (fr) * 2016-06-01 2017-12-06 Manuel Lindner Broyeur de déchets mobile doté d'un entrainement hybride parallèle
EP3251750A1 (fr) * 2016-06-01 2017-12-06 Manuel Lindner Dispositif broyeur de dechets fixe comprenant un accumulateur d'energie
WO2017207350A1 (fr) * 2016-06-01 2017-12-07 Manuel Lindner Dispositif mobile de broyage de déchets équipé d'une propulsion hybride parallèle
WO2017207345A1 (fr) * 2016-06-01 2017-12-07 Manuel Lindner Dispositif mobile de broyage de déchets équipé d'une propulsion hybride sérielle
WO2017207349A1 (fr) * 2016-06-01 2017-12-07 Manuel Lindner Dispositif de broyage de déchets fixe équipé d'un accumulateur d'énergie
EP3251750B1 (fr) 2016-06-01 2019-02-06 Manuel Lindner Dispositif broyeur de dechets fixe comprenant un accumulateur d'energie
CN109414700A (zh) * 2016-06-01 2019-03-01 曼纽尔·林德纳 串联混合驱动的移动式废物粉碎设备
CN109475877A (zh) * 2016-06-01 2019-03-15 曼纽尔·林德纳 具有能量储存器的固定式废物粉碎装置
US11097281B2 (en) 2016-06-01 2021-08-24 Manuel Lindner Mobile waste comminuting device comprising a parallel hybrid drive system
US11298704B2 (en) 2016-06-01 2022-04-12 Manuel Lindner Stationary waste comminuting device having an energy accumulator
US11571700B2 (en) 2016-06-01 2023-02-07 Manuel Lindner Mobile waste comminuting device comprising a series-connected hybrid drive system

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