DESC:FORM 2
THE PATENTS ACT 1970
(39 of 1970)
&
The Patents Rules, 2003
COMPLETE SPECIFICATION
(See section 10 and rule 13)

1. TITLE OF THE INVENTION: “ A rotational planetary gearbox for energy optimization ”
2. APPLICANT:

(a) Name : QUILL ELECTROTEC PRIVATE LIMITED
(b) Nationality : Indian
(c) Address : East – 320,
Siddhraj Z2,
Kudasan,
Podar International School Road,
Gandhinagar- 382421,
Gujarat, India.

PROVISIONAL

The following specification describes the invention. ? COMPLETE

The following specification particularly describes the invention and the manner in which it is to be performed.

Field of Invention
The present invention relates to a rotational planetary gearbox for energy optimization and more particularly it relates to the slippage free gearbox which saves the input energy and provides more efficiency in terms of torque and speed.
Background of invention
The gearbox is an essential component of machines used in various industries and fields. The purpose of gearboxes is to increase the output torque or to change the speed (revolution per minute) of a motor. The shaft of the motor is connected to one end of the gearbox and through the internal configuration of gears, provides a given output torque and speed determined by the gear ratio. Gearboxes are used in agricultural, industrial, construction, mining, and automotive equipment and are available in different designs and specifications.
The main function of this transmission is to provide high torque at the time of starting, accelerating, and pulling a load. There are mainly four number of gearbox. Namely, Sliding mesh type gearbox, Constant-mesh type gearbox, Synchromesh gearbox and Planetary (Epicyclic) gearbox. In ordinary planetary gear set, the axes of the various gears are fixed, the motion of the gears being simply rotations about their own axes. In planetary or epicyclic gearing, at least one gear not only rotates, about its own axis but also rotates bodily about some other axis.
Planetary gearbox contains sun gear, ring gear, plurality of planetary gears and carrier. These types of gearbox are the most widely used automatic transmission system. In an automatic transmission system, there is only an accelerator and brake is provided. So there will not be any clutch pedal or gear lever available on the vehicle. Such planetary gear sets are provided for many applications in automotive technology and other technical fields. A planetary gear design methodology should not only result in better gear set designs, but also save time and costs in the design process.
In such gear set an input shaft connects the differential gear system to a sun gear of the planetary stage and an output shaft is driven, via a carrier, when the ring gear is stationary. As a rule such planetary stages comprise gearwheels and a toothed rim of the ring gear with straight teeth, so that when the teeth engage no axial forces are produced that would act upon the input shaft. The disadvantage of planetary stages with straight teeth is that they do not run very smoothly, so a lot of noise is emitted.
CN1288829 comprises vehicle speed-controlling stepless speed variator, comprise planetary gears and fluid torque converter, planetary gears comprises sun gear, annular gear and planet carrier, fluid torque converter comprises turbine and pump impeller, the power intake of planetary gears links to each other with motor, its output terminal links to each other directly or indirectly with the pump impeller of fluid torque converter, the turbine of fluid torque converter links to each other with turbine shaft, turbine shaft links to each other with feedback gear, and through this turbine shaft output torque that links to each other with wheel, and the other end of described feedback gear and planetary gears directly or indirectly is meshed with a transition gear assembly.
Further in U.S. Pat. No. 5,429,557 A the two planetary gear sets are arranged coaxially over the output shaft and form the main gear set of this known automatic transmission. The ring gear of the radially inner planetary gear set and the sun gear of the radially outer planetary gear set are formed integrally, i.e., combined in a single, common transmission component. The planetary carriers of the two planetary gear sets are solidly connected to one another and are in driving connection with the output shaft.
In above mentioned prior arts one of the gears i.e., sun gear, ring gear and carrier must be in fixed position. Further these gearboxes generate less torque which is not efficient and waste the input energy. Further conventional gearbox only works on rolling motion without slipping law in vertical manner only. Hence, there is need to provide a planetary gearbox which works in rotational manner with the same law for energy optimization and to provide higher torque.
Object of invention
The main object of the present invention is to provide a rotational planetary gearbox for energy optimization.
Another object of the present invention is to provide a rotational planetary gearbox for energy optimization which saves energy in terms of power.
Still another object of the present invention is to provide a rotational planetary gearbox for energy optimization which gives more efficiency.
Another object of the present invention is to provide rotational planetary gearbox which works on the principle of rolling motion without slipping in rotational manner.
Another object of the present invention is to provide rotational planetary gearbox which minimizing the friction loss.
Yet another object of the present invention is to provide a rotational planetary gearbox for energy optimization which provides almost 1.25 times higher torque compared to conventional planetary gearbox.
Still another object of the present invention is to provide a rotational planetary gearbox to energy optimize in the sector of industry and automobile.
Yet another object of the present invention is to provide a rotational planetary gearbox for energy optimization which provides more mileage in electrical vehicles.
Yet another object of the present invention is to provide rotational planetary gearbox which overcomes the shortcoming and drawbacks of the prior conventional planetary gearbox.
Summary of invention
The present invention relates to a rotational planetary gearbox for energy optimization. The present invention mainly comprises a body having an input shaft, an output shaft, a fixed sun gear, a rotatable sun gear, a carrier, a plurality of input planet gear and a plurality of guide planet gear, a planet shaft. The rotatable sun gear fixed on the input shaft and input planet gears are engaged with the rotatable sun gear. Said input planet gears supported through the planet shaft mounted between the carriers. The guide planet gear mounted on the extended planet shaft and said guide planet gear engaged with the fixed sun gear. The output shaft rigidly mounted on the output side carrier. Arrangement of these gears saves the input energy and provides more efficiency and millage which can be used in many sectors and getting energy saving machine in terms of torque. This invention provides almost 1.25 times higher torque and slippage free planetary gearbox compared to conventional mechanism. It is applicable in field of industrial sector, automobile industries, Electric vehicles segment, energy sector, windmill plants, thermal plants, hydro plants, oil industries, etc.,
Brief Description of drawings:
Other objects, advantages and novel features of the invention will become apparent from the following detailed description of the present embodiment when taken in conjunction with the accompanying drawings.
Fig. 1 shows a block view of a rotational planetary gearbox according to the present invention.
Detailed description of invention
The nature of the invention and the manner in which it works is clearly described in the provisional specification. The invention has various embodiments and they are clearly described in the following pages of the provisional specification. Before explaining the present invention, it is to be understood that the phraseology and terminology employed herein is for the purpose of description and not of limitation.
The invention discloses rotational planetary gearbox for energy optimization having an application at the Industries and automobile field.
The present invention is a rotational planetary gearbox as shown in Fig. 1. The present invention mainly comprises a body (15) having an input shaft (4), an output shaft (5), a fixed sun gear (3), a rotatable sun gear (8), a carrier (14), a plurality of input planet gear (9) and a plurality of the guide planet gear (11), a planet shaft (10).
As shown in Fig. 1, a body (15) made from the two circular end plates (1, 2) opposite to each other which comprise whole gear box assembly. At the circular end plate (1) of the body (15) configured with the fixed sun gear (3) which is fixed in the axial direction towards the circular end plate (2) in horizontal axis. Said fixed gear is a helical type gear having the teeth slanted at an angle of 25°-45°.
The input shaft (4) is passed through the centroid borehole of circular end plate (1) and the fixed sun gear (3) assembly. In the borehole of the circular end plate (1) and between said circular end plate (1) and the input shaft (4), the bearings (12) with the oil seal (13) are provided. Bearing (12) provides to rotate the shaft with minimal friction and seal rings prevent such bearing (12) from leakage and to protect the shaft and bearing (12) from ingress of dirt or foreign matter.
In similar way, the output shaft (5) is shaft is passed through the centroid borehole of circular end plate (2). In the borehole of the circular end plate (2) and between said circular end plate (2) and the output shaft (5), the bearings (12) with the oil seal (13) are provided. Bearing (12) provides to rotate the shaft with minimal friction and Seal rings prevent such bearing (12) from leakage and to protect the shaft and bearing (12) from ingress of dirt or foreign matter.
The input shaft (4) is provided with the rotatable sun gear (8) which fixed on extreme end of the input shaft (4) followed by input side carrier (6). The bearing (12) is provided between the input shaft (4) and input side carrier (6) and Said input side carrier (6) is rotationally movable over the input shaft (4) through said bearing (12).
In the output, the output side carrier (7) is fixed on the output shaft (5). Both input side carrier (6) and output side carrier (7) are assembled with each other and make whole carrier assembly (14) and the rotatable sun gear (8) is positioned between said input side carrier (6) and output side carrier (7).
The plurality of input planet gear (9) is mounted between the input side carrier (6) and output side carrier (7) through the planet shaft (10) and said planet shaft (10) is mounted between the input side carrier (6) and output side carrier (7) through the bearing (12). Said plurality of input planet gear (9) is engaged with the rotatable sun gear (8) mounted on the input shaft (4) and having opposite hand gear connections between input planet gear (9) and rotatable sun gear (8). Said input planet gear (9) and rotatable sun gear (8) are helical type gear having the teeth slanted at an angle of 25°-45°. The plurality of planet shaft (10) is extended throughout the input side carrier (6) and the guide planet gear (11) mounted at the end of the extended planet shaft (10). Said plurality of the guide planet gear (11) is engaged with the fixed sun gear (3) and having opposite hand gear connections between the guide planet gear (11) and fixed sun gear (3). Said guide planet gear (11) is helical type gear having the teeth slanted at an angle of 25°-45°.
As shown in Figure. 1, when the mechanical input is given to the input shaft (4) of the gear box assembly, the rotatable sun gear (8) rotates as it is assembled with input shaft (4) of the assembly. Due to the rotation of the rotatable sun gear (8), the plurality of input planet gear (9) are rotates surrounding the rotatable sun gear (8) in the anti-rotating direction of the rotatable sun gear (8) as the teeth of the plurality of input planet gear (9) are engaged with the slot of the sun gear in the opposite hand gear connections.
As the input planet gear (9) are situated between the input side carrier (6) and output side carrier (7) through the planet shaft (10), the carrier (14) is also rotate on the same direction as the input planet gear (9) is rotate surrounding the rotatable sun gear (8). Further, the planet shaft (10) individually carries the guide planet gear (11) which engaged with the fixed sun gear (3) mounted on the circular plate (1) of the body (15) and rotate during the rotation of the planet shaft (10). Said guide planet gear (11) is also rotate surrounding the fixed sun gear (3) in the same direction as the input planet gear (9) is rotate surrounding the rotatable sun gear (8).
As the output side carrier (7) is fixed with the output shaft (5), the rotation of the carrier (14) is transmitting to the output shaft (5) and said output rotation is given to the particular application.
Through the above arrangement of the gears in the gear box assembly according to the present invention, the optimum torque and speed can be achieved at the output and makes more efficient transmitter of the rotational/ mechanical energy.
The calculation of the output to input gear ratio can be defined by the following formulas:

Gear Ratio of 1st stage:
GR1= Nip/Ns
Where,
Nip = Number of teeth of Input Planet Gear
Ns = Number of teeth of Rotatable Sun Gear
Gear Ratio of 2nd stage:
GR2 = Nsf/Ngp
Where,
Nsf = Number of teeth of Fix Sun Gear
Ngp = Number of teeth of Guide Planet Gear
The equivalent gear ratio can be defined as follows:
GR equivalent = (Nip/Ns × Nsf/Ngp)-1
Where,
Nip = Number of teeth of Input Planet Gear
Ns = Number of teeth of Rotatable Sun Gear
Nsf = Number of teeth of Fix Sun Gear
Ngp = Number of teeth of Guide Planet Gear
Through the above arrangement of the gears in the gear box assembly according to the present invention, the optimum torque and speed can be achieved at the output and makes more efficient transmitter of the rotational/ mechanical energy.
In the present invention, the input shaft (4) can function as an output shaft (5) and vice versa.
The present invention is illustrated more in details in the following experimental examples. The example describes and demonstrates the embodiments within the scope of the present invention. This example is given solely for the purpose of illustration and is not to be construed as limitations of the present invention, as many variations thereof are possible without departing from spirit and scope.
Experiment 1:
The First experiment aimed to test the efficacy of the present invention on a 5HP bucket elevator, commonly utilized for vertically conveying materials across various industries. The bucket elevator consisted of 40 buckets and operated using a 5 HP motor at 140 RPM, with a gear ratio of 10.28:1 in the conventional gear box. To evaluate the performance of the present invention, the motor and gear box combination according to the present invention were replaced with those specified in the existing arrangement of the bucket elevator. The modified setup utilized a 2HP motor and a gear box with a gear ratio of 10.5:1, achieving the desired speed of 140 RPM. The subsequent data gathered from testing both the existing gear box and the gear box according to the present invention and was compared to assess the performance enhancements offered by the present invention. Further details and results of this experiment are presented below table 1.
Table:1 Performance data of the present invention in bucket elevator
Existing machine details By using the present invention
Without load
Without load
Motor Amp: 3.5 A
Motor Amp: 2.1 A

Motor VAC: 3phase, 440V, 5HP/3.7KW
Motor VAC: 3phase, 440V, 2HP/1.49KW

Motor efficiency (?): 85%
Motor efficiency (?): 88%

Motor working parameter: 1440RPM > 10.28:1 attach Gearbox > 140RPM > driven Bucket elevator in 140RPM.
Motor working parameter: 1470RPM > 10.5:1 attach Gearbox > 140RPM > driven Bucket elevator in 140RPM.

With load:
With load
Motor Amp: 4.1 A to 4.3 A
Motor Amp: 2.4 A to 2.5 A

Motor VAC: 3phase, 440V, 5HP/3.7KW
Motor VAC: 3phase, 440V, 2HP/1.49KW

Motor efficiency (?): 75% - 82%

Motor efficiency (?): 75% - 82%

Motor working parameter: 1440RPM > 10.28:1 attach Gearbox > 140RPM > driven Bucket elevator in 140RPM.
Motor working parameter: 1470RPM > 10.5:1 attach Gearbox > 140RPM > driven Bucket elevator in 140RPM.

Conclusion:
From the above experiment, it is conclude that in the vertical bucket conveyor, by using the gear box according to the present invention, the electricity consumption drastically reduced up to 40% compared to the existing machine configuration and due to that the overall efficiency of the machine increase. Further, it works on optimum energy consumption which leads to economical advantages.
Experiment 2:
In the Second experiment disclosed the existing flacker machine's power transmission system with a setup based on the present invention. The existing flacker machine was equipped with two 2.5-ton rollers that rotated at a speed of 160 RPM. The power was provided by a 200 HP motor connected to a pulley belt system with a speed ratio of 8.8:1. The hydraulic system used to maintain pressure operated with regular pressures between 800-1000 PSI and higher pressures between 1000-1500 PSI.
In the experiment, the aforementioned arrangement was substituted with a 200 HP motor connected to a gear box, which has a gear ratio of 8.8:1, in accordance with the invention. The aim of the experiment is to assess the performance of the modified flacker machine with the gear box in comparison to the existing setup. The expected outcomes include potential improvements in energy consumption, and the overall effectiveness of the flacking process. The comparison of performance of the existing flacker machine and flacker machine using the gear box according to the present invention are shown below table 2. Table:2 Performance data of the present invention in Flacker machine
Existing machine details By using the present invention
Without load
Without load
Motor Amp: 114 A
Motor Amp: 114 A

Motor VAC: 3phase, 440V, 200HP/149.2KW
Motor VAC: 3phase, 440V, 200HP/149.2KW

Motor frequency: 46.50Hz Motor frequency: 46.50Hz
Motor working parameter: 1408RPM > 8.8:1 Pulley-Belt system > 160RPM > driven Roller in 160RPM.
Motor working parameter: 1408RPM > 8.8:1 New Gearbox > 160RPM > driven Roller in 160RPM.

With load:
With load
Motor Amp: 141 A to 155A
Motor Amp: 118A to 129 A

Motor VAC: 3phase, 440V, 200HP/149.2KW
Motor VAC: 3phase, 440V, 200HP/149.2KW

Motor frequency: 46.50Hz Motor frequency: 46.50Hz
Motor working parameter: 1408RPM > 8.8:1 Pulley-Belt system > 160RPM > driven Roller in 160RPM.
Motor working parameter: 1408RPM > 8.8:1 New Gearbox > 160RPM > driven Roller in 160RPM.

Conclusion:
From the above experiment, it is conclude that in the flacker machine, by using the power transmission through the gear box according to the present invention, the electricity consumption drastically reduced compared to the existing machine configuration and due to that the overall efficiency of the machine increase.
Experiment 3:
In the third experiment, an Electric Vehicle (EV) utilizing two different gearboxes. This experiment aimed to demonstrate the potential improvements and advantages of the gearbox of the present invention in comparison to the traditional gearbox. Initially, the EV was operated using its standard, conventional gearbox, and various performance data were recorded. Subsequently, in order to assess the impact of the new invention, the conventional gearbox was replaced with the gearbox according to the present invention. The EV was then operated under similar conditions, and the performance data were once again recorded for comparison.
The comparison of performance of the EV with conventional gear box and using the gear box according to the present invention are shown below table 3.
Table:3 Performance data of the present invention in Electrial Vehicle
Sr. No Parameters Technical Things while using the conventional gear box Technical Things while using the present invention
1. HUB motor 750W 750W
2. Controller 60V DC- 35A 60V DC- 35A
3. Battery 60V – 24Ah 60V – 24Ah
4. Wheel Parameter 90/90-12 90/90-12
Diameter inches (mm) 18.38 (466.8) 18.38 (466.8)
Width inches (mm) 3.54 (90) 3.54 (90)
Circum. Inches (mm) 57.74 (1466.5) 57.74 (1466.5)
Sidewall height inches (mm) 3.19 (81) 3.19 (81)
Revolution per mile (mm) 1097.41 (681.9) 1097.41 (681.9)
5. Speed Min. to Max. (single charge with drive testing) Min. to Max. (single charge with drive testing)
Top Speed 45Kmph 45Kmph
Single Charge Average 0-72 Km 0-92 Km
Conclusion:
From the above experiment, it is conclude that in the Electrical vehicle, by using the power transmission through the gear box according to the present invention, the EV can runs at the top speed and increase the mileage of EV as well as electricity consumption drastically reduced compared to using the conventional gear box configuration in EV.
The present invention have various application in field of industrial sector, automobile industries, Electric vehicles segment, energy sector, windmill plants, thermal plants, hydro plants, oil industries, etc., as it will save energy and provides more efficiency and millage which can be used in many sectors.
In another embodiment numbers of planetary gear sets are provided on the same shaft in serial manner for transmitting high input and output ratios with gears of moderate size. Further the number of teeth of gears can be modified for required speed and torque as number of teeth depends on the same.
The invention has been explained in relation to specific embodiment. It is inferred that the foregoing description is only illustrative of the present invention and it is not intended that the invention be limited or restrictive there to. Many other specific embodiments of the present invention will be apparent to one skilled in the art from the foregoing disclosure.
Reference Numerals:
Circular end plate
Circular end plate
Fixed sun gear
Input shaft
Output shaft
Input side carrier
Output side carrier
Rotatable sun gear
Input planet gear
Planet shaft
Guide planet gear
Bearing
Oil seal
Carrier
Body

,CLAIMS:We Claim:
1. A rotational planetary gearbox for energy optimization comprises a body (15) having two circular end plate (1, 2) positioned parallel and opposite to each other; the circular end plate (1) provided with a fixed sun gear (3) having axial direction towards the circular end plate (2) in horizontal axis;
a carrier assembly (14) having an input side carrier (6) and output side carrier (7); Said input side carrier (6) and output side carrier (7) are assembled opposite to each other;
a rotatable sun gear (8) rigidly mounted on an input shaft (4) extended in the horizontal axis and disposed in the centroid borehole of the circular end plate (1) followed by the input side carrier (6) and the fixed sun gear (3);
a plurality of input planet gear (9) arranged in between the input side carrier (6) and output side carrier (7) through a planet shaft (10); said plurality of the input planet gear (9) engaged with the rotatable sun gear (8);
the plurality of planet shaft (10) extended through the input side carrier (6); Said extended end of planet shaft (10), a guide planet gear (11) mounted; said guide planet gear (11) engaged with the fixed sun gear (3);
an output shaft (5) is rigidly mounted with the output side carrier (7) of the carrier assembly (14); said output shaft (5) is extended in the horizontal axis and throughout the centroid borehole of the circular end plate (2).
2. The rotational planetary gearbox as claimed in claim 1, wherein the plurality of the input planetary gear and plurality of the guide planet gear (11) are rotate at the same angular velocity.
3. The rotational planetary gearbox as claimed in claim 1, wherein a bearing (12) with oil seal (13) are provided in the centroid borehole of circular end plates (1, 2) through which the input shaft (4) and output shaft (5) is extended.
4. The rotational planetary gearbox as claimed in claim 1, wherein the fixed sun gear (3) and guide planet gear (11) are helical gears having teeth slanted at an angle of 25°-45° and are in opposite hand gear connection.
5. The rotational planetary gearbox as claimed in claim 1, wherein the rotatable sun gear (8) and input planet gear (9) are helical gears having teeth slanted at an angle of 25°-45° and are in opposite hand gear connection.
6. The rotational planetary gearbox as claimed in claim 1, wherein a bearing (12) is provided in the input side carrier (6) and output side carrier (7) through which the planet shaft (10) is extended.
7. The rotational planetary gearbox as claimed in claim 4, wherein the fixed sun gear (3) and guide planet gear (11) are rolling without slippage which reduces friction loss.
Dated this on 01st day of August, 2023.