CA2625019A1 - Overdrive operation of planetary gear set power transmission - Google Patents
Overdrive operation of planetary gear set power transmission Download PDFInfo
- Publication number
- CA2625019A1 CA2625019A1 CA 2625019 CA2625019A CA2625019A1 CA 2625019 A1 CA2625019 A1 CA 2625019A1 CA 2625019 CA2625019 CA 2625019 CA 2625019 A CA2625019 A CA 2625019A CA 2625019 A1 CA2625019 A1 CA 2625019A1
- Authority
- CA
- Canada
- Prior art keywords
- gear set
- planetary gear
- planetary
- main
- sun gear
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 18
- 238000000034 method Methods 0.000 claims abstract description 12
- 238000010586 diagram Methods 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- -1 wind Substances 0.000 description 1
Landscapes
- Structure Of Transmissions (AREA)
Abstract
The invention relates to the process of an overdrive operation of planetary gear set power transmission to increase both speed and torque output. The new invention can be used in mechanical transportation, vehicle, power plant, electric power generator, machinery, engine and transmission, gearbox, electric motor and other mechanical equipment with moving or rotating mechanical shaft. The power transmission has a main planetary gear set that performs the new process of an overdrive operation without any component being held. The sun gear runs in reverse direction driving by a second planetary gear set running in reverse drive operation with or without an external motor, or without the second planetary gear set just an external motor. And further include a power source or power input to drive the planetary carrier or holder of main planetary gear set.
Description
Descriptions of an Overdrive Operation of Planetary Gear Set Power Transmission The invention relates to the process of an overdrive operation of planetary gear set power transmission to increase both speed and torque output. It differs from all power transmission in regards to gear operations and power output. The present patent and existing technology of planetary gear set power transmission reduce certain amount of speed or torque to control power. The new overdrive operation has the ability to produce more power output reducing neither speed nor torque.
The principle of new overdrive operation, while the planet gears rotate and by running the sun gear in reverse direction and different speed can change the power output. The reverse sun gear helps the planet gears to achieve both speed and torque. The planet gears achieve great amount of speed and torque from the reverse sun gear while driving the ring gear in the same direction. The ring gear produces more torque, and serves as the power output.
The present technology of overdrive operation, the sun gear is stationary or held while the planet gears are walking around the sun gear. This overdrive operation drops great amount of torque to produce speed. The Simpson, Wilson, Ravigneaux and Lepelletier gear set are the four (4) planetary gear sets arrangement and operation that control power by reducing speed or torque. The present technology of power transmission involves design to reduce mechanical power looses of the transmission using one of the four (4) known planetary gear sets arrangement and operation. Power does not change during transfer on this four (4) known planetary gear sets arrangement and operation.
The new overdrive operation of the main planetary gear set has no stationary or held gears. The sun gear S2, ring gear R2, planet gears P2 and planetary carrier C2 are all rotating and represent as the main planetary gear set. This new overdrive operation of planetary gear set, the sun gear S2 runs in reverse direction driving by a second planetary gear set in reverse drive operation shown in figure 1, or a second planetary gear set and an external motor shown in figure 2, or just an external motor shown in figure 3 and further include a power source or input to drive the planetary carrier or holder C2 of main planetary gear set.
The reverse sun gear S2 of the main planetary gear set could also be driven by an external motor without the second planetary gear set shown in figure 3. Controlling the speed of this reverse sun by an external motor M produces different output of speed and torque.
The appended drawings are explained in detail below.
Figure lA illustrates the power flow of the new overdrive operation of planetary gear set power transmission with second planetary gear set running in reverse drive operation.
Figure 1B illustrates how to mechanically assemble the diagram shown in figure 1A. The new overdrive operation of planetary gear set and the second planetary gear set in reverse drive operation, share the same input shaft 1. The planetary carrier or holder C2 of the new overdrive operation of the planetary gear set is rigidly connected to the input shaft 1 and serves as the power input. The sun gear S 1 of the second planetary gear set is rigidly connected to the input shaft 1 and also serves as the power input. The ring gear R1 of the second planetary gear set is rigidly connected to the sun gear S2 of the new overdrive planetary gear set. The planetary carrier or holder Cl of the second planetary gear set is stationary or held to perform a reverse drive operation. The power output shaft 2 is rigidly connected to the ring gear R2.
Figure 2A illustrates the power flow of the new overdrive operation of planetary gear set power transmission with second planetary gear set running in reverse drive operation and driving by an external motor.
Figure 2B illustrates how to mechanically assemble the diagram shown in figure 2A with second planetary gear set and an external motor. The new overdrive operation of planetary gear set and the second planetary gear set in reverse drive operation have different power input. The planetary carrier or holder C2 of the new overdrive operation of the planetary gear set is rigidly connected to the input shaft 1 and serves as the power input. The ring gear R1 of the second planetary gear set is rigidly connected to the sun gear S2 of the new overdrive planetary gear set. The planetary carrier or holder Cl of the second planetary gear set is stationary or held to perform a reverse drive operation. The power output shaft 2 is rigidly connected to the ring gear R2. The difference with figure 1, the second planetary gear set in reverse drive operation is driving by an external motor M.
The sun gear Si and the gear G2 are rigidly connected and driving by the gear G1 of the external motor. If the input shaft 1 is rotating clockwise, the external motor should be rotating counter clockwise in order for the sun gear S 1 and gear G2 to rotate the same direction with the input shaft.
Figure 3A illustrates the power flow of the new overdrive operation of planetary gear set power transmission with an external motor.
Figure 3B illustrates how to mechanically assemble the diagram shown in figure 3A with an external motor. The input shaft 1 is rigidly connected to the planetary carrier or holder C2. The gear G2 and the sun gear S2 are rigidly connected and driving by the gear G1 of the external motor. The power output shaft 2 is rigidly connected to the ring gear R2.
This mechanical assembly has no gear or part that stationary or held. If the input shaft 1 is rotating clockwise, the external motor should be rotating counter clockwise in order for the sun gear S2 and gear G2 to rotate the same direction with the input shaft.
The calculation of the present overdrive operation gear ratio is 1/ (1+S/R).
Where S is the number of teeth of the sun gear and R is the number of teeth of the ring gear.
For example, if the sun gear has 31 teeth and the ring gear has 80 teeth, the gear ratio will be .72:1.
That means, in every .72 rotation of the input shaft gives the output shaft of I rotation, or in every 1 rotation of the input shaft gives the output shaft of 1.3875 rotations.
The calculation of the new overdrive operation gear ratio is 1/ (((S1/R1 x S2 + S2) /R2) +1). Consider figure 1 B, where S l is the number of teeth of the sun gear of the second planetary gear set, R1 is the number of teeth of the ring gear of the second planetary gear set, S2 is the number of teeth of the sun gear of the main planetary gear set and R2 is the number of teeth of the main planetary gear set. For example, if the sun gear of the second planetary gear set has 33 teeth, the ring gear of the second planetary gear set has 72 teeth, the sun gear of the main planetary has 31 teeth and the ring gear of the main planetary gear set has 80 teeth, using the new formula the gear ratio will be .64:1.
That means, in every .64 rotation of the input shaft gives the output shaft of I rotation, or in every 1 rotation of the input shaft gives the output shaft of 1.5625 rotations.
The speed of the reverse sun gear of the main planetary gear set in figure 2 and 3 differ due to motor speed or rpm, the formula above could not be used. Nevertheless, if the speed or rpm of the motor is known, the output speed can be calculated using the new formula, (((S/R+1) x I x R) + (S x F)) / R where I is the input speed, F is the reverse speed, S is the number of teeth of the reverse sun gear and R is the number of teeth of the ring gear of the main planetary gear set. The speed of the reverse sun gear of the main planetary gear set must be calculated first. If the reverse sun gear is driving by a second planetary gear set, the present formula -R/S to calculate the gear ratio for the reverse drive operation can be used first. For example, consider figure 2B with a second planetary gear set and a motor drive. If the motor drive with 3,600 rpm drives the second planetary gear set with 33 teeth sun gear and 72 teeth ring gear, the reverse output speed will be 1,650 rpm. If the input speed is 6,000 rpm and using the formula above, the output speed will be 8,964 rpm.
The maximum output torque can be calculated using the radius of the planetary carrier and ring gear of the main planetary gear set. The formula T/ C x R where T is the input torque, C is the radius of the planetary carrier and R is the radius of the ring gear. This formula could be applied only if the force of the reverse sun gear is equal or greater than the force of the planetary carrier. For example, if an input torque is 500 oz-in. drive a planetary carrier with a radius of 1.5 inches and a ring gear with a radius of 2.2 inches, the maximum output torque would be 733 oz-in. If the reverse sun gear is being held similar to the present overdrive operation that means the reverse sun gear has zero force, the formula will be T/ C x 50% x R. Using this formula in the example, the output torque will be only 366 oz-in. This is where the present overdrive planetary gear set operation decrease torque but not the new overdrive planetary gear set operation.
The new overdrive operation of planetary gear set power transmission can be used in all kind of moving or rotating mechanical shaft to boost up power and efficiency.
The new invention can be used in mechanical transportation, vehicles, power plants, electric power generator, machinery, engine and transmission, gearbox electric motor and other mechanical equipment. This new overdrive operation of planetary gear set can change the thermodynamics of renewable cycles for all kinds of energy conversion by adapting to the power generator, electric motor or engine motor. Energy conversion such as air pressure, battery, solar, water, wind, hydrogen and other burning fuel into mechanical energy by using the new power transmission can change the thermodynamics. This is the solution to energy crisis and carbon emission problem. Research and development of free energy or perpetual motion is possible by means of this new overdrive operation of planetary gear set power transmission.
The principle of new overdrive operation, while the planet gears rotate and by running the sun gear in reverse direction and different speed can change the power output. The reverse sun gear helps the planet gears to achieve both speed and torque. The planet gears achieve great amount of speed and torque from the reverse sun gear while driving the ring gear in the same direction. The ring gear produces more torque, and serves as the power output.
The present technology of overdrive operation, the sun gear is stationary or held while the planet gears are walking around the sun gear. This overdrive operation drops great amount of torque to produce speed. The Simpson, Wilson, Ravigneaux and Lepelletier gear set are the four (4) planetary gear sets arrangement and operation that control power by reducing speed or torque. The present technology of power transmission involves design to reduce mechanical power looses of the transmission using one of the four (4) known planetary gear sets arrangement and operation. Power does not change during transfer on this four (4) known planetary gear sets arrangement and operation.
The new overdrive operation of the main planetary gear set has no stationary or held gears. The sun gear S2, ring gear R2, planet gears P2 and planetary carrier C2 are all rotating and represent as the main planetary gear set. This new overdrive operation of planetary gear set, the sun gear S2 runs in reverse direction driving by a second planetary gear set in reverse drive operation shown in figure 1, or a second planetary gear set and an external motor shown in figure 2, or just an external motor shown in figure 3 and further include a power source or input to drive the planetary carrier or holder C2 of main planetary gear set.
The reverse sun gear S2 of the main planetary gear set could also be driven by an external motor without the second planetary gear set shown in figure 3. Controlling the speed of this reverse sun by an external motor M produces different output of speed and torque.
The appended drawings are explained in detail below.
Figure lA illustrates the power flow of the new overdrive operation of planetary gear set power transmission with second planetary gear set running in reverse drive operation.
Figure 1B illustrates how to mechanically assemble the diagram shown in figure 1A. The new overdrive operation of planetary gear set and the second planetary gear set in reverse drive operation, share the same input shaft 1. The planetary carrier or holder C2 of the new overdrive operation of the planetary gear set is rigidly connected to the input shaft 1 and serves as the power input. The sun gear S 1 of the second planetary gear set is rigidly connected to the input shaft 1 and also serves as the power input. The ring gear R1 of the second planetary gear set is rigidly connected to the sun gear S2 of the new overdrive planetary gear set. The planetary carrier or holder Cl of the second planetary gear set is stationary or held to perform a reverse drive operation. The power output shaft 2 is rigidly connected to the ring gear R2.
Figure 2A illustrates the power flow of the new overdrive operation of planetary gear set power transmission with second planetary gear set running in reverse drive operation and driving by an external motor.
Figure 2B illustrates how to mechanically assemble the diagram shown in figure 2A with second planetary gear set and an external motor. The new overdrive operation of planetary gear set and the second planetary gear set in reverse drive operation have different power input. The planetary carrier or holder C2 of the new overdrive operation of the planetary gear set is rigidly connected to the input shaft 1 and serves as the power input. The ring gear R1 of the second planetary gear set is rigidly connected to the sun gear S2 of the new overdrive planetary gear set. The planetary carrier or holder Cl of the second planetary gear set is stationary or held to perform a reverse drive operation. The power output shaft 2 is rigidly connected to the ring gear R2. The difference with figure 1, the second planetary gear set in reverse drive operation is driving by an external motor M.
The sun gear Si and the gear G2 are rigidly connected and driving by the gear G1 of the external motor. If the input shaft 1 is rotating clockwise, the external motor should be rotating counter clockwise in order for the sun gear S 1 and gear G2 to rotate the same direction with the input shaft.
Figure 3A illustrates the power flow of the new overdrive operation of planetary gear set power transmission with an external motor.
Figure 3B illustrates how to mechanically assemble the diagram shown in figure 3A with an external motor. The input shaft 1 is rigidly connected to the planetary carrier or holder C2. The gear G2 and the sun gear S2 are rigidly connected and driving by the gear G1 of the external motor. The power output shaft 2 is rigidly connected to the ring gear R2.
This mechanical assembly has no gear or part that stationary or held. If the input shaft 1 is rotating clockwise, the external motor should be rotating counter clockwise in order for the sun gear S2 and gear G2 to rotate the same direction with the input shaft.
The calculation of the present overdrive operation gear ratio is 1/ (1+S/R).
Where S is the number of teeth of the sun gear and R is the number of teeth of the ring gear.
For example, if the sun gear has 31 teeth and the ring gear has 80 teeth, the gear ratio will be .72:1.
That means, in every .72 rotation of the input shaft gives the output shaft of I rotation, or in every 1 rotation of the input shaft gives the output shaft of 1.3875 rotations.
The calculation of the new overdrive operation gear ratio is 1/ (((S1/R1 x S2 + S2) /R2) +1). Consider figure 1 B, where S l is the number of teeth of the sun gear of the second planetary gear set, R1 is the number of teeth of the ring gear of the second planetary gear set, S2 is the number of teeth of the sun gear of the main planetary gear set and R2 is the number of teeth of the main planetary gear set. For example, if the sun gear of the second planetary gear set has 33 teeth, the ring gear of the second planetary gear set has 72 teeth, the sun gear of the main planetary has 31 teeth and the ring gear of the main planetary gear set has 80 teeth, using the new formula the gear ratio will be .64:1.
That means, in every .64 rotation of the input shaft gives the output shaft of I rotation, or in every 1 rotation of the input shaft gives the output shaft of 1.5625 rotations.
The speed of the reverse sun gear of the main planetary gear set in figure 2 and 3 differ due to motor speed or rpm, the formula above could not be used. Nevertheless, if the speed or rpm of the motor is known, the output speed can be calculated using the new formula, (((S/R+1) x I x R) + (S x F)) / R where I is the input speed, F is the reverse speed, S is the number of teeth of the reverse sun gear and R is the number of teeth of the ring gear of the main planetary gear set. The speed of the reverse sun gear of the main planetary gear set must be calculated first. If the reverse sun gear is driving by a second planetary gear set, the present formula -R/S to calculate the gear ratio for the reverse drive operation can be used first. For example, consider figure 2B with a second planetary gear set and a motor drive. If the motor drive with 3,600 rpm drives the second planetary gear set with 33 teeth sun gear and 72 teeth ring gear, the reverse output speed will be 1,650 rpm. If the input speed is 6,000 rpm and using the formula above, the output speed will be 8,964 rpm.
The maximum output torque can be calculated using the radius of the planetary carrier and ring gear of the main planetary gear set. The formula T/ C x R where T is the input torque, C is the radius of the planetary carrier and R is the radius of the ring gear. This formula could be applied only if the force of the reverse sun gear is equal or greater than the force of the planetary carrier. For example, if an input torque is 500 oz-in. drive a planetary carrier with a radius of 1.5 inches and a ring gear with a radius of 2.2 inches, the maximum output torque would be 733 oz-in. If the reverse sun gear is being held similar to the present overdrive operation that means the reverse sun gear has zero force, the formula will be T/ C x 50% x R. Using this formula in the example, the output torque will be only 366 oz-in. This is where the present overdrive planetary gear set operation decrease torque but not the new overdrive planetary gear set operation.
The new overdrive operation of planetary gear set power transmission can be used in all kind of moving or rotating mechanical shaft to boost up power and efficiency.
The new invention can be used in mechanical transportation, vehicles, power plants, electric power generator, machinery, engine and transmission, gearbox electric motor and other mechanical equipment. This new overdrive operation of planetary gear set can change the thermodynamics of renewable cycles for all kinds of energy conversion by adapting to the power generator, electric motor or engine motor. Energy conversion such as air pressure, battery, solar, water, wind, hydrogen and other burning fuel into mechanical energy by using the new power transmission can change the thermodynamics. This is the solution to energy crisis and carbon emission problem. Research and development of free energy or perpetual motion is possible by means of this new overdrive operation of planetary gear set power transmission.
Claims (9)
1. A process for an overdrive operation of planetary gear set power transmission which comprises:
- A main planetary gear set to perform the new overdrive operation;
- A second planetary gear set for driving the sun gear of the main planetary gear set via ring gear in reverse direction;
- An input shaft common to the main and second planetary gear set if an external motor not adapted;
- An external motor for driving the sun gear of the second planetary gear set, or the sun gear of the main planetary gear set without the present of the second planetary gear set.
- A main planetary gear set to perform the new overdrive operation;
- A second planetary gear set for driving the sun gear of the main planetary gear set via ring gear in reverse direction;
- An input shaft common to the main and second planetary gear set if an external motor not adapted;
- An external motor for driving the sun gear of the second planetary gear set, or the sun gear of the main planetary gear set without the present of the second planetary gear set.
2. A process as defined in claim 1, in which the ring gear, planetary carrier or holder, planetary gears and sun gear of the main planetary gear set are all rotating.
3. A process as defined in claim 1 and 2, in which the ring gear, planetary carrier or holder and planetary gears are running in the same direction while the sun gear in other direction.
4. A process as defined in claim 1, in which the sun gear of the main planetary gear set is driving by a second planetary gear set with or without an external motor, or by an external motor without the second planetary gear set.
5. A process as defined in claim 1, in which the sun gear of the main planetary gear set, is firmly connected to the ring gear of the second planetary gear set.
6. A process as defined in claim 1 and 5, in which the input shaft common to the main and second planetary gear set, drives the sun gear of the second planetary gear set without an external motor and the planetary carrier or holder of the main planetary gear set at the same time.
7. A process as defined in claim 1, in which an external motor is used to drive the sun gear of the second planetary gear set while the planetary carrier or holder of the main planetary gear set is driving by the input shaft.
8. A process as defined in claim 1, in which an external motor is used to drive the sun gear of the main planetary gear set in reverse direction without the second planetary gear set while the planetary carrier or holder is driving by the input shaft.
9. A process as defined in claim 1, in which the sun gear of the main planetary gear set is running in reverse direction that provides more speed and torque to the planetary gears and ring gear of the main planetary gear set resulting to power output boost up.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US1171508P | 2008-01-22 | 2008-01-22 | |
| US61/011,715 | 2008-01-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2625019A1 true CA2625019A1 (en) | 2009-07-22 |
Family
ID=40900701
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2625019 Abandoned CA2625019A1 (en) | 2008-01-22 | 2008-03-20 | Overdrive operation of planetary gear set power transmission |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2625019A1 (en) |
-
2008
- 2008-03-20 CA CA 2625019 patent/CA2625019A1/en not_active Abandoned
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5678299B2 (en) | Hybrid vehicle transmission | |
| CN102844588B (en) | Continuously variable transmission device having power split | |
| CN103161889B (en) | Hybrid gearbox | |
| US8944949B2 (en) | Multi-speed transmission with integrated electric motor | |
| CN101371061B (en) | Electric transmission with three interconnected planetary gear sets | |
| DE50007835D1 (en) | Gearbox for a wind turbine | |
| JP2011105296A (en) | Transmission of hybrid vehicle | |
| WO2008020184A8 (en) | A method of operating a supercharger | |
| US20130133335A1 (en) | Power Plant Line Having a Variable-Speed Pump | |
| TWI568614B (en) | Hybrid power transmission integrated system and control method thereof | |
| CN109849640A (en) | A kind of electromechanical coupling transmission device for automotive power | |
| CN102529677A (en) | Variable ratio power-split hybrid transmission | |
| WO2011067633A1 (en) | Gear tooth profile for a wind turbine | |
| CN109578527A (en) | Modularized wind power generation main-gear box | |
| CN102943737A (en) | Ocean current energy generating set | |
| CN101349323A (en) | Novel gear box suitable for solar energy thermal current wind power generation system | |
| CA2625019A1 (en) | Overdrive operation of planetary gear set power transmission | |
| FR2918003B1 (en) | HYBRID TRACTION DEVICE FOR HEAVY VEHICLE. | |
| CN111550534A (en) | Six-gear hybrid power transmission | |
| CN206807220U (en) | A kind of brushless direct-current planet-gear speed reducing motor | |
| CN102673368A (en) | Variable ratio power-split hybrid transmission | |
| CN1808856B (en) | Electric wheel hub | |
| CN205745168U (en) | A kind of dual planetary gear mechanical differential | |
| CN101586653B (en) | Energy-saving combination machinery | |
| CN209671534U (en) | Modularized wind power generation main-gear box |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Dead |
Effective date: 20130320 |