WO2011081510A1 - Selective leverage system - Google Patents

Selective leverage system Download PDF

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Publication number
WO2011081510A1
WO2011081510A1 PCT/MY2009/000222 MY2009000222W WO2011081510A1 WO 2011081510 A1 WO2011081510 A1 WO 2011081510A1 MY 2009000222 W MY2009000222 W MY 2009000222W WO 2011081510 A1 WO2011081510 A1 WO 2011081510A1
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WO
WIPO (PCT)
Prior art keywords
combination
torque
output
gear
gear train
Prior art date
Application number
PCT/MY2009/000222
Other languages
French (fr)
Inventor
See Ping Tiau
Original Assignee
See Ping Tiau
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 See Ping Tiau filed Critical See Ping Tiau
Priority to PCT/MY2009/000222 priority Critical patent/WO2011081510A1/en
Publication of WO2011081510A1 publication Critical patent/WO2011081510A1/en

Links

Classifications

    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/06—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the piston motion being transmitted by curved surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/06—Engines with means for equalising torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/042—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft the connections comprising gear transmissions
    • F01B2009/045—Planetary gearings

Definitions

  • the present invention relates to improved performance of a device having a pulsing behavior input or output such as combustion, engines, generators, alternators, compressors and other cyclically devices.
  • the invention provides an intermediate solution that provides some of the advantages for conventional cyclically varying input or output devices.
  • This intermediate solution includes a SLS (Selective Leverage System) gear train that uses a well known leverage principle to improve the performance of engines, AC motors and generators, alternators, compressors, etc.
  • SLS Selective Leverage System
  • the invention can use on incompressible fluid transportation and energy recirculation system.
  • a torque altering gear train is used in combination with a device having pulsating torque cycle characteristic.
  • the gear train comprises a gear train having a cyclic torque to cooperate with the pulsating torque characteristic of the device to improve the performance thereof by exponential modifying during each designated cycle the net torque of the combination.
  • the device act as transformer of a piston type four stroke motor and gear train increases the net torque output during the power stroke and decreases the net torque required during the combustion stroke.
  • the motor may be a single cylinder or multi-cylinder engine.
  • the piston type engine is a two or four cylinder engine and preferably, the gear train is defined by one elliptical-like hollow subassembly.
  • the gears cooperate to provide an increase torque in varying value by variable gear ratio and system friction losses.
  • the device can also be a driven device and in this case the gear train modifies the input force to improve the output of the driven device.
  • This has particular application with generators, turbine and piston type compressors.
  • a further embodiment of the invention includes steam and wind turbines providing the input force for the gear train and a connected AC generator or alternator.
  • the gear train is a speed cyclic transmission and the AC generator or alternator is driven at increased torque during part of its cycle to increase the power output.
  • the gear train preferably includes one elliptical-like hollow subassembly.
  • a pulsating amplitude speed cyclic transmission paired to cooperate with a turbine to increase output pressure of the pipeline.
  • Another aspect of the invention is energy recirculation system; use extra energy to produce energy.
  • the gear train has a cyclically changing torque characteristic which using a SLS gear train for matched to a cyclically changing output of the device.
  • the outer T-shape lever equipped gear train 10 of Figure 1 has one circular gear 11 secured with T-shape lever arm 13 on top.
  • the fulcrum 12 is build-in on circular gear 1.
  • This gear is simple to make and are preferred for many of the application of the SLS gear train with an elliptical hollow subassembly. This part will be the primary gear in Figures 2 to 4.
  • the SLS gear train 20 of Figure 2 has similar cyclically varying characteristics but uses ellipticallike hollow subassembly 21 rotating about fulcrum 22 and transfers the input force to lever equipped gear.
  • This SLS gear train and the T-shape lever equipped gears of Figure 1 can be used with single or double piston engines or compressors to improve the output.
  • T- shape lever arm is to maximize the transmittal of levered resultant force.
  • the SLS gear train 30 of Figure 3 shows the SLS gear train use in combination with an output shaft of a piston type internal combustion engine.
  • the cylinder subassembly has the piston starting the combustion stroke after compression of working media.
  • the force exerted on the piston is transmitted through the connecting rod and rotates the elliptical-like hollow subassembly 31.
  • Figure 3 shows the SLS gear train 30 paired with a one cylinder subassembly 32, crankshaft 33, primary gear 34, secondary gear 35 and output shaft 36. These figures will also be explained relative to the graph of Figure 6.
  • the cylinder subassembly 32 of Figure 3 has the piston starting the combustion stroke after compression of working media. The force exerted on the piston is transmitted through the connecting rod and rotates the crankshaft 33. During the next 90 degree shaft rotation, variable torque is produced as generally shown on Figure 5.
  • Each of the SLS gear trains of Figures 1 through 3 provides a pulsating mechanical advantage or 'lever 1 during each cycle. This advantage is matched or paired with cyclically varying characteristics of a driven or a drive device.
  • FIG. 3 shows one for this detail.
  • crankshaft 33 coupled with elliptical hollow subassembly 31 to external/internal primary gear 34 having secondary gear 35 connected to output shaft 36 which is aligned with original engine shaft/crankshaft.
  • This arrangement could be incorporated into the engine, into a stationary housing or into a clutch.
  • Figure 5 indicates changing torque being produced at every 90 degree shaft rotation. From Figure 3 it can be understood that, if engine shaft 33 with elliptical-like hollow subassembly 31 rotates clockwise, the torque at shaft 36 is increased due to the multiplying or leverage affect produced by the gear 34. The maximum leverage occurs at every 90 degree engine shaft and gear 34 key position is meet to elliptical-like hollow subassembly 31.
  • the cyclically varying gear multiplier or leverage is varied; depending on ellipse parameters and the length of lever also including the gear ratio, these numbers could vary.
  • Figures 4 show different SLS gear train arrangements where rotation of one of the gears at a constant input/output speed produces cyclically torque characteristic.
  • the average leverage is depend for combination with difference ways of force input, instantaneous torque characteristic will be add on to the invention. It is important for efficiency of the present method to find point of engine maximum torque and key the leading gear of the SLS gear train to provide the cyclically varying mechanical advantage.
  • Figure 6 shows example of SLS effect when adding the invention builds with turbine 61 and pump 62.
  • driven device is pulsing energy device (for example piston compressor) positive effect will be even greater if this device is aligned properly.
  • Figure 7 shows a double hook subassembly 71 that can be an alternative design for elliptical-like hollow subassembly 31
  • the driven device is a pulsing driven device (for example a piston compressor) the positive effect will be even greater if this device is aligned properly.
  • the SLS gear train connected to its shaft, and driven by turbine or other input source (engine, turbine and etc.) it will supply, with properly alignment, higher torque to the rotor when required by the load. Without load, the rotor will have maximum speed variation and with load the speed variation becomes insignificant.
  • the timed mechanical advantage of the present system has been described with respect to modifying the output of a lower pulsating drive device having changing torque characteristics, but it is also useful to increase the pressure for the incompressible fluid in pipeline.
  • Figure 1 is a combination perspective view of an outer T-shape lever equipped gear with build-in fulcrum on gear and the mounted T-shape lever, also name as primary gear;
  • Figure 2 is a combination perspective view of the SLS gear train using one elliptical hollow subassembly to rotate about a central through six outer leverage gears (primary gears);
  • Figure 3 is schematics showing the SLS gear train used in combination with an output shaft of a piston type internal combustion engine
  • Figure 4 is schematics of the SLS gear train in each 45 degree rotate
  • Figure 5 is a torque/ degree of rotation graph in difference lever ratio
  • Figure 6 is a side view of the use of the SLS gear train as pump in the pipeline attached the flow direction.
  • Figure 7 is an alternative design for elliptical hollow subassembly.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)

Abstract

An alteration torque transmission is used in combination with an input or output device having pulsating torque application characteristic. The transmission has a gear train of cooperating gears that during each rotate produce a pulsing leverage effect. With the T-shape lever and fulcrum that build on gear, the altering leverage effect is matched to the input/output device to improve the performance thereof. A variable leverage gear set is disclosed for providing an increased torque effect in pulse. This combination is beneficial with many devices, including reciprocating engine, wing driven turbines and generators. Even build with turbine to increase the pipeline pressure and recirculation energy.

Description

Selective Leverage System
Field Of Invention
The present invention relates to improved performance of a device having a pulsing behavior input or output such as combustion, engines, generators, alternators, compressors and other cyclically devices.
Background Art
Structures to enhance the performance for rotating devices, with the same propose in the PCT application, which has been previously described in PCT/CA2006/000526. This design is defined by 2 elliptical-liked gears.
The invention provides an intermediate solution that provides some of the advantages for conventional cyclically varying input or output devices. This intermediate solution includes a SLS (Selective Leverage System) gear train that uses a well known leverage principle to improve the performance of engines, AC motors and generators, alternators, compressors, etc.
Further, the invention can use on incompressible fluid transportation and energy recirculation system.
Technical Field
According to the invention a torque altering gear train is used in combination with a device having pulsating torque cycle characteristic. The gear train comprises a gear train having a cyclic torque to cooperate with the pulsating torque characteristic of the device to improve the performance thereof by exponential modifying during each designated cycle the net torque of the combination.
An aspect of the invention, the device act as transformer of a piston type four stroke motor and gear train increases the net torque output during the power stroke and decreases the net torque required during the combustion stroke. The motor may be a single cylinder or multi-cylinder engine.
In a preferred aspect of the invention the piston type engine is a two or four cylinder engine and preferably, the gear train is defined by one elliptical-like hollow subassembly. In yet further aspects of the invention the gears cooperate to provide an increase torque in varying value by variable gear ratio and system friction losses.
The device can also be a driven device and in this case the gear train modifies the input force to improve the output of the driven device. This has particular application with generators, turbine and piston type compressors.
A further embodiment of the invention includes steam and wind turbines providing the input force for the gear train and a connected AC generator or alternator. The gear train is a speed cyclic transmission and the AC generator or alternator is driven at increased torque during part of its cycle to increase the power output. The gear train preferably includes one elliptical-like hollow subassembly.
In a further aspect of the invention is a pulsating amplitude speed cyclic transmission paired to cooperate with a turbine to increase output pressure of the pipeline. Another aspect of the invention is energy recirculation system; use extra energy to produce energy.
With the present invention, the gear train has a cyclically changing torque characteristic which using a SLS gear train for matched to a cyclically changing output of the device. Description of Drawings
The outer T-shape lever equipped gear train 10 of Figure 1 has one circular gear 11 secured with T-shape lever arm 13 on top. The fulcrum 12 is build-in on circular gear 1. This gear is simple to make and are preferred for many of the application of the SLS gear train with an elliptical hollow subassembly. This part will be the primary gear in Figures 2 to 4.
The SLS gear train 20 of Figure 2 has similar cyclically varying characteristics but uses ellipticallike hollow subassembly 21 rotating about fulcrum 22 and transfers the input force to lever equipped gear. This SLS gear train and the T-shape lever equipped gears of Figure 1 can be used with single or double piston engines or compressors to improve the output.
At the contact point of elliptical-like hollow subassembly 31 with T-shape lever arm 13, the input force will sequentially decompose into components in two perpendicular directions. And the function of T- shape lever arm is to maximize the transmittal of levered resultant force.
The SLS gear train 30 of Figure 3 shows the SLS gear train use in combination with an output shaft of a piston type internal combustion engine. The cylinder subassembly has the piston starting the combustion stroke after compression of working media. The force exerted on the piston is transmitted through the connecting rod and rotates the elliptical-like hollow subassembly 31.
Figure 3 shows the SLS gear train 30 paired with a one cylinder subassembly 32, crankshaft 33, primary gear 34, secondary gear 35 and output shaft 36. These figures will also be explained relative to the graph of Figure 6. The cylinder subassembly 32 of Figure 3 has the piston starting the combustion stroke after compression of working media. The force exerted on the piston is transmitted through the connecting rod and rotates the crankshaft 33. During the next 90 degree shaft rotation, variable torque is produced as generally shown on Figure 5.
Each of the SLS gear trains of Figures 1 through 3 provides a pulsating mechanical advantage or 'lever1 during each cycle. This advantage is matched or paired with cyclically varying characteristics of a driven or a drive device.
Figure 3 shows one for this detail. In this case crankshaft 33 coupled with elliptical hollow subassembly 31 to external/internal primary gear 34 having secondary gear 35 connected to output shaft 36 which is aligned with original engine shaft/crankshaft. This arrangement could be incorporated into the engine, into a stationary housing or into a clutch.
Figure 5 indicates changing torque being produced at every 90 degree shaft rotation. From Figure 3 it can be understood that, if engine shaft 33 with elliptical-like hollow subassembly 31 rotates clockwise, the torque at shaft 36 is increased due to the multiplying or leverage affect produced by the gear 34. The maximum leverage occurs at every 90 degree engine shaft and gear 34 key position is meet to elliptical-like hollow subassembly 31.
The cyclically varying gear multiplier or leverage is varied; depending on ellipse parameters and the length of lever also including the gear ratio, these numbers could vary.
Figures 4 show different SLS gear train arrangements where rotation of one of the gears at a constant input/output speed produces cyclically torque characteristic. The rotation of input and output to be in inversely with arrangement shown in Figure 4,
With 90 degree rotation of elliptical-like hollow subassembly 31 , primary gear 34 rotation is about 180 degree; secondary shaft 36 rotation is result by the gear ratio. With analysis of exponential curve 51 Figure 5 shows that maximum torque is produced during maximum gears leverage with unchanged RPM (revolutions per minute) for input ad output, and in these particular cases (between lever ratio 1.6 to 1.9), torque magnification is approximately 75 to 160 percent, excluding friction loss effect. The curves under the axis means decreasing of torque force and increase force if the curves above the axis. Total change of torque in system can be defining though effective degree in the curves. Effective degree means the position where the transmittal force is on action. The maximum effective degree is 90 degree, due to the elliptical-like hollow subassembly 31. Effective degree is calculated by divide 360 with the number of outer T-shape lever equipped gear, which are equally array in circle.
The average leverage is depend for combination with difference ways of force input, instantaneous torque characteristic will be add on to the invention. It is important for efficiency of the present method to find point of engine maximum torque and key the leading gear of the SLS gear train to provide the cyclically varying mechanical advantage.
Figure 6 shows example of SLS effect when adding the invention builds with turbine 61 and pump 62. By the increased torque, the pressure after improved invention will get an addition. If driven device is pulsing energy device (for example piston compressor) positive effect will be even greater if this device is aligned properly.
Figure 7 shows a double hook subassembly 71 that can be an alternative design for elliptical-like hollow subassembly 31
If the driven device is a pulsing driven device (for example a piston compressor) the positive effect will be even greater if this device is aligned properly. In case of an AC generator, using the SLS gear train connected to its shaft, and driven by turbine or other input source (engine, turbine and etc.) it will supply, with properly alignment, higher torque to the rotor when required by the load. Without load, the rotor will have maximum speed variation and with load the speed variation becomes insignificant.
The timed mechanical advantage of the present system has been described with respect to modifying the output of a lower pulsating drive device having changing torque characteristics, but it is also useful to increase the pressure for the incompressible fluid in pipeline.
While I have illustrated and described a preferred embodiment of my invention, it will be understood that variations may be made thereto without departing from the spirit of the invention or the scope of the appended claims.
Brief Description of the Drawings
Figure 1 is a combination perspective view of an outer T-shape lever equipped gear with build-in fulcrum on gear and the mounted T-shape lever, also name as primary gear;
Figure 2 is a combination perspective view of the SLS gear train using one elliptical hollow subassembly to rotate about a central through six outer leverage gears (primary gears);
Figure 3 is schematics showing the SLS gear train used in combination with an output shaft of a piston type internal combustion engine;
Figure 4 is schematics of the SLS gear train in each 45 degree rotate;
Figure 5 is a torque/ degree of rotation graph in difference lever ratio; and
Figure 6 is a side view of the use of the SLS gear train as pump in the pipeline attached the flow direction. Figure 7 is an alternative design for elliptical hollow subassembly.

Claims

Claims
<1 >An alternation torque transmission arrangement in combination with a device having a pulsating torque cycle characteristic; said transmission arrangement comprising a gear set for creation of a cyclic torque variation selected to cooperate with the pulsating torque characteristic of said device to improve the performance thereof by a number of exponentials modifying during each cycle the net torque of the combination.
<2>The combination of claim 1 wherein said device/is an output device to said arrangement.
<3>The combination as claimed in claim 2 wherein said output device is a piston type four stroke motor and said gear set increases the net torque output during the power stroke and decreases the net torque required during the compression stroke.
<4>The combination as claimed in claim 3 wherein said piston type engine is a single or multi-cylinder engine.
<5>The combination as claimed in claim 4 wherein said gear train has an elliptical hollow subassembly with at least four T-shape lever equipped gears.
<6>The combination as claimed in claim 5 wherein said gears cooperate to provide a vary increase in peak torque.
<7>The combination as claimed in claim 1 wherein said device is a driven device and said gear train modifies the input force to improve the output of the driven device, said characteristic that created by elliptical-like hollow subassembly or a double hook subassembly rotating about fulcrum and transfers the input force to T-shape lever equipped gear.
<8>The combination as claimed in claim 7 wherein said driven device is an AC generator or alternator.
<9>The combination as claimed in claim 7 wherein said drive force is a steam or wind turbine for said arrangement.
<10>The combination as claimed in claim 7 wherein said drive force is a combustion engine.
<11 >The combination as claimed in claim 7 wherein said drive force is a pump.
<12>The combination as claimed in claim 1 wherein said gear train is a varying speed cyclic transmission paired to function with a cyclically varying torque output of said device.
<13>The combination as claimed in claim 1 wherein said gear train has a cyclically varying torque characteristic matched to a cyclically varying requirement for output of said device.
<14>The combination as claimed in claim 1 wherein said gear train has at least four T-shape lever equipped gears in said gear train, and said output device being a piston type internal combustion engine, and wherein each gear includes a elliptical-like hollow part or a double hook part paired to a respective piston-cylinder combination for increasing torque output during the power stroke in this cylinder.
<15>A method of modifying a pulsing energy source device having an output shaft, said method comprising using a cyclically varying transmission having at least four T-shape lever equipped gears, connecting one of said gears to the output shaft of the pulsing energy source device and aligned therewith such that during each pulse of the energy source device the transmission modifies the output to improve performance with respect to energy efficiency. <16>The method as claimed in claim 15 where the center gear is aligned with a driven device input and further improves performance with respect to energy efficiency, said center gear can connect to planetary gearing system.
<17>The method as claimed in claim 15 where a pulsating amplitude speed cyclic transmission paired to cooperate with a turbine to increase output pressure of the pipeline.
<18>The method as claimed in claim 15 where the invention is install in an energy recirculation system, said system produce energy from produced energy.
PCT/MY2009/000222 2009-12-29 2009-12-29 Selective leverage system WO2011081510A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/MY2009/000222 WO2011081510A1 (en) 2009-12-29 2009-12-29 Selective leverage system

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Application Number Priority Date Filing Date Title
PCT/MY2009/000222 WO2011081510A1 (en) 2009-12-29 2009-12-29 Selective leverage system

Publications (1)

Publication Number Publication Date
WO2011081510A1 true WO2011081510A1 (en) 2011-07-07

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4608875A (en) * 1982-09-20 1986-09-02 Wallace Associated Research Inertial transmission
US4907474A (en) * 1988-10-07 1990-03-13 Inductran Corporation Mechanical torque converter
US6260443B1 (en) * 1997-11-06 2001-07-17 Steven E. Spirer Hand wrench with torque augmenting means
US20060225690A1 (en) * 2005-03-17 2006-10-12 Anatoly Arov Selective leverage technique and devices

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4608875A (en) * 1982-09-20 1986-09-02 Wallace Associated Research Inertial transmission
US4907474A (en) * 1988-10-07 1990-03-13 Inductran Corporation Mechanical torque converter
US6260443B1 (en) * 1997-11-06 2001-07-17 Steven E. Spirer Hand wrench with torque augmenting means
US20060225690A1 (en) * 2005-03-17 2006-10-12 Anatoly Arov Selective leverage technique and devices

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