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
  • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
  • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
  • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
• • 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
  • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
  • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
  • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
  • F16H19/043—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack for converting reciprocating movement in a continuous rotary movement or vice versa, e.g. by opposite racks engaging intermittently for a part of the stroke
• • 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
  • F16H27/00—Step-by-step mechanisms without freewheel members, e.g. Geneva drives
  • F16H27/04—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement
  • F16H27/06—Mechanisms with driving pins in driven slots, e.g. Geneva drives
• • 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
  • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
  • F16H29/20—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action the intermittently-acting members being shaped as worms, screws, or racks
• • 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
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
  • F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
• • 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
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
  • F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
  • F16H3/30—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially with driving and driven shafts not coaxial
• • 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
  • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
  • F16H3/42—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
• • 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
  • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
• • 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
  • F16H35/00—Gearings or mechanisms with other special functional features
  • F16H35/02—Gearings or mechanisms with other special functional features for conveying rotary motion with cyclically varying velocity ratio
• • 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/04—Smoothing ratio shift
  • F16H61/0403—Synchronisation before shifting
• • 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
  • F16H35/00—Gearings or mechanisms with other special functional features
  • F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
• • 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
  • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
  • F16H61/04—Smoothing ratio shift
  • F16H2061/0425—Bridging torque interruption
  • F16H2061/0429—Bridging torque interruption by torque supply with a clutch in parallel torque path
• • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
  • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds

Definitions

• This invention pertains to transmissions having variable ratios between input and output velocities. Specifically, it relates to all-gear transmissions whose velocity ratios may be changed continuously over a wide range of values ranging from zero to non-zero values, without depending on friction.
• US 5603240 does not have a co-axial input to output and therefore cannot be used for applications requiring this configuration.
• the output travels as the ratio is changed. Therefore, this design cannot be used when stationary output is required.
• US 20100199805 offers a sinusoidal output and uses several modules just to minimize the "ripple" when a steady and uniform input is provided.
• the patent US 9970520 offers a steady input to output ratio and co-axial input and output shaft in a comparably smaller envelope than that of its prior art. This is achieved with a use of a set of non-circular gears using as few as three modules. The drawback is that it is hard to mass produce the desired non-circular gears and will add significant manufacturing cost. It is also difficult to accurately design the tooth profile to achieve a uniform input to output ratio.
• the present invention uses a custom designed Geneva wheel mechanism to achieve uniform rack velocity during functional region and circular/ non-circular gear for non-functional region.
• the portion of the region used by the Geneva wheel mechanism is also non-functional region which overlap with the non-functional region achieved by the circular/non-circular gears for smooth transition. It is also possible to use Geneva wheel mechanism for functional and non-functional region. However, it will be economical to use a partial circular gear for the non-functional region.
• the path of the Geneva slot engaging with the Geneva pin determines the shape of the functional or non-functional region. Using a commonly used Geneva wheel mechanism with straight slot will not achieve uniform rack movement in the functional region and these slots has to have a specific shape to achieve uniform rack movement in the functional region. In general, a Geneva wheel mechanism has straight slot and is commonly used in applications needing indexing.
• Fig 1- IVT general assembly perspective view - Exploded.
• Fig 2- Angular velocity module using Geneva pin and wheel mechanism along with partial circular /noncircular gears
• Fig 4A-4B Scotch yoke module and rectifier module.
• Rectifier module showing rack and pinion, with pinions placed on a common output shaft on a one-way bearing along with dummy rack, and common output shaft. Showing force acting on the rack is co-planer with longitudinal axis of the pinion.
• Fig 21 A - 21 D Link Mechanism on crank pin shaft with non-circular input shaft and collar with matching orifice, using offset crank pin mounted on crank pin collar with non-circular orifice sliding on crank pin shaft with matching cross-section 21 A- Top view 21 B- Front view 21 C- Side view 21 D-Perspective view
• All the gears in the following component list can be replaced with a sprocket and chain system.
• the noncircular gear system can be replaced with a sprocket and chain system where at least one of the sprockets is non-circular.
• a Crank pin 9 (Fig. 3B), revolves around the longitudinal axis of an Input disk 10
• the input shaft is slotted to allow the crankpin and link to pass thru it allowing the longitudinal axis of the input shaft or the input disk to be co-axial with the longitudinal axis of the crank pin.
• the Slotted rack holder 11 is restricted such that it can move only in the direction that is normal to its slot.
• a Rack 12 is fastened to the Slotted rack holder 11 , such that the Rack 12 is parallel to the Slotted rack holder's 44 direction of movement.
• the Crank pin shaft 23 is orthogonal to the Input shaft 4. The revolution of the Crank pin 9 about the longitudinal axis 1021 of Input disk 10 is translated to pure linear back and forth movement or reciprocating movement of the Rack 12. This mechanism is commonly known as "Scotch-Yoke- Mechanism" in the industry.
• the distance of this linear back and forth movement is directly proportional to the radial distance of the Crank pin 9 from the longitudinal axis 1021 of the Input disk 10. Since the work done is constant, which is a product of force applied multiplied by the distance traveled (F*stroke), for a smaller stroke, the force applied is greater and for a longer stroke, the force applied is smaller.
• the Rack 12 is linked to a Pinion 14 (Fig. 4A) converting this linear movement of the Rack 12 to rocking oscillation of the Pinion 14.
• This rocking oscillation is converted to a unidirectional rotation, using a One-way bearing/ Computer- Controlled-Clutch / Ratchet-mechanism 22.
• One main purpose of this invention is to achieve a CONSTANT AND UNIFORM output angular velocity when the input angular velocity is constant and uniform. However, using the steps described above, this is NOT achieved, as the output is sinusoidal.
• Patent US9970520 uses a pair of non-circular gears to achieve this. This invention achieves it by using modified Geneva mechanism customized for this.
• Angular-Velocity-Modifier-Module (Fig. 2)
• the main purpose of this module is to change the uniform power input to a reciprocal of sinusoidal output. This is to reverse the effect of the sinusoidal output in a scotch yoke mechanism.
• This module comprises of:
• a one-way bearing can be placed between the circular or non-circular gear linking the Geneva slot wheel to the partial driven gear.
• either the Geneva pin wheel or the Geneva slot wheel can be made driving or driven.
• Scotch-Yoke-Module (Fig. 4A, 4B): The main purpose of this module is to convert circular motion to a reciprocating motion. The output is sinusoidal for a steady, uniform input. This output is converted to a steady, uniform output using Angular-Velocity-Modifier-Module.
• the Input disk 10 has a radial slot.
• the Slotted rack holder 11 has a slot namely "Crank-Pin-Slot” 1013. It also has an extension on either side of the slot at the middle of the slot. This extension is normal to the Crank-Pin-Slot 1013.
• the Slotted rack holder 44 is placed on the other side of the Input disk 10 sandwiching the Input disk 10between the Slotted rack holder H and a Ratio-Changing-Mechanism, which is described in subsequent paragraphs.
• the Input shaft 66 has a non-circular hole in the middle. This is paired with a Sliding-Collar with a matching exterior contour, which is co-axially placed allowing relative axial movement while restricting rotational angular displacement with respect to each other.
• Two thrust-Bearings 40 are co-axially placed in contact with one on either end of the Sliding-Collar 67 as shown in Fig. 22D and the Sliding-Collar-Auxiliary- Shaft 67 has a pivot 1028 on the other end.
• One end of a Link 68 is attached to the pivot 1028 and the other end of the Link 68 is either attached to the Crank pin 9, as shown in (Fig.
• two Racks 64 can be placed on the Slotted rack holder 11with a phase shift of 180° engaged with their respective pinions placed co-axially on a common pinion shaft via a one-way bearing/computer-controlled clutch/a ratchet mechanism to allow the pinion shaft to rotate in a specific direction.
• Many of these scotch yoke modules can be stacked and all the pinions of all the modules can be placed on one common pinion shaft, making the pinion shaft the output of the IVT. Further this common pinion shaft can be made hollow allowing the power shaft which drives the driving Geneva pin wheel, to pass thru. With this arrangement a co-axial input to output can be achieved.
• Dummy-Crank-Pin 43 The Crank pin 9 is placed off-center when the Input disk 10 revolves. This imbalance will result in vibration. To compensate this, a Dummy-Crank-Pin 43 is placed at same distance 180° apart. This movement is identical to the movement of the Crank pin 9.
• the dummy crank pin is attached to a dummy link that links to the dummy crank pin 43 that is pivoted to the collar placed to move in the opposite direction of the crank-pin.
• the input shaft is slotted to allow the link and crank pin and dummy link and dummy crank pin to pass thru
• Dummy-Rack 55 for counter oscillation As the Input disk 10 rotates the Slotted Rack holder 11 has an oscillatory motion which will result in vibration. It is cancelled by having an appropriate mass oscillating in the opposite direction. This is achieved by pinion as shown in Fig.4A&4B in contact with the Rack 12, which will spin back and forth. Bringing an appropriate mass in contact with the pinion at 180° apart will compensate for this vibration. A separate wheel can also be used in spite of the pinion or a lever pivoting on the pinion shaft can be used to link the rack and the dummy rack such that they move in opposite direction. A slider connecting the lever and sliding in a slot normal to the rack teeth will guide the lever allowing the rack and dummy rack to only slide in the direction of the longitudinal axis of the rack.
• the Input shaft 4 is directly linked to the Sun-Gear of the planetary-Gear-System with following 2 sub-options a.
• the Co-Axial-Output-Element-With-lnternal-Gear/Planetary-Gear 65 is directly linked to the Carrier of the Planetary-Gear-System and Ring-Gear of the Planetary-Gear-System functions as the final output or wheel system 1022 b.
• the Co-Axial-Output-Element-With-lnternal-Gear/Planetary-Gear 65 is linked to the Ring-Gear of the Planetary-Gear-System and the Carrier functions as the final output or wheel system 1022.
• the Co-Axial-Output-Element-With-lnternal-Gear/Planetary-Gear 65 is directly linked to the Sun-Gear of the Planetary-Gear-System with following 2 sub-options.
• the Input shaft 4 is directly linked to the Carrier of the Planetary-Gear-System and the Ring-Gear of the Planetary-Gear-System functions as the final output or wheel system 1022.
• the Input shaft 4 is directly linked to the Ring-Gear of the Planetary-Gear- System and the Carrier functions as the final output or wheel system.
• the Input shaft 4 is directly linked to the Ring-Gear of the planetary-Gear-System with following 2 sub-options a.
• the Co-Axial-Output-Element-With-lnternal-Gear/Planetary-Gear 65 is directly linked to the Ring-Gear of the Planetary-Gear-System with following 2 sub-options.
• the Input shaft 4 is directly linked to the Carrier of the Planetary-Gear-System and the Carrier of the Planetary-Gear-System and the Sun-Gear of the Planetary- Gear-System functions as the final output or wheel system 1022.
• the Input shaft 4 is directly linked to the Sun-Gear of the Planetary-Gear-System and the Carrier functions as the final output or wheel system 1022.
• the Co-Axial-Output-Element-With-lnternal-Gear/Planetary-Gear 65 is directly linked to the Carrier of the Planetary-Gear-System with following 2 sub-options.
• the Input shaft 4 is directly linked to the Ring-Gear of the Planetary-Gear- System and the Ring-Gear of the Planetary-Gear-System and the Sun-Gear of the Planetary-Gear-System functions as the final output or wheel system 1022.
• the Input shaft 4 is directly linked to the Sun-Gear of the Planetary-Gear-System and the Ring-Gear functions as the final output or wheel system 1022.
• the Co-Axial-Output-Element-With-lnternal-Gear/Planetary-Gear 65 is connected to one of the three elements, either a Ring-Gear, a Carrier, or a Sun-Gear of a Planetary-Gear-System.
• the Input shaft 4 is connected to one of the remaining two elements of the Planetary-Gear-System.
• the third remaining element of the Planetary-System functions as the final output or wheel system 1022. This converts the CVT to an IVT.
• the ideal rack velocity profile is as follows:
• a planetary system can be used to compensate for any deviations from the desired Rack 12 movement profile.
• a Stationary Sun Gear 36 with respective to the ratio modifier frame 2 is placed co-axial with a driven circular or non-circular gear 40 which is driven by a driving circular or non-circular gear 39 as appropriate. This can be used in addition to the Geneva wheel system. This is shown in Fig.43A& 43B. This driving circular or non-circular gear is mounted on the power shaft 29.
• One or more Shaft-Cam 37 is placed on the driven circular or non-circular gear 40 which acts like a carrier of the planetary gear system.
• a Cam-Gear 38 is rigidly attached on the Shaft-Cam 37.
• Each of this Cam-Gear 38 is made to engage another Cam-Input-Shaft 41 each, which is rigidly attached on the Input shaft 8.
• the cams can be designed to give a desired rack velocity profile. The above configuration will also work when the stationary sun is replaced with a stationary ring gear. This is shown in Fig. 44A&44B.
• CTR is a center-to-center distance of the driving non-circular gear and the driven non-circular gear
• ⁇ is an angular displacement of the driving non-circular gear
• ⁇ is an angular displacement of the driven non-circular gear
• N is a number of times the input disk rotates when the driven non-circular gear rotates once;
• n is a number of times the driven non-circular gear rotates when the driving non-circular gear rotates once; regions where the piece-wise function for the rack velocity is constant are functional regions and regions where the piece-wise function for the rack velocity is not constant are non-functional regions which can be linear or non-linear functions of ⁇ ;
• ⁇ 1i , ⁇ 2i , ⁇ 3 i , ⁇ 4i are specific angular positions of the driving non-circular gear, the values of which are solved for using a solution to the piece-wise differential equation;
• ⁇ 1 , ⁇ 2 , ⁇ 3 , ⁇ 4 are specific angular positions of the driven non-circular gear corresponding to angular positions ⁇ 1i , ⁇ 2i , ⁇ 3 i , ⁇ 4i of the driving non-circular gear respectively, and are a cutoff between the functional and non-functional regions, values of ⁇ 1 , ⁇ 2 , ⁇ 3 , ⁇ 4 which can to be solved for by using arbitrary values for ⁇ 1i , ⁇ 2i , ⁇ 3 i , ⁇ 4i ; and k i are constants, which are all equal.

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

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• 2021
  • 2021-02-12 CA CA3165829A patent/CA3165829A1/en active Pending
  • 2021-02-12 EP EP21752950.2A patent/EP4103863A4/en active Pending
  • 2021-02-12 WO PCT/US2021/017984 patent/WO2021163583A1/en not_active Ceased
  • 2021-02-12 CN CN202180004826.3A patent/CN114423966B/zh active Active
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  • 2021-06-07 EP EP21821579.6A patent/EP4162175A4/en active Pending
  • 2021-06-07 KR KR1020237000576A patent/KR20230020526A/ko active Pending
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