Electro-mechanical gear drive system

Abstract

The present invention relates to anelectro-mechanical generator gear drive system which comprises a primary motor (PM), auxiliary motor (AM) and planetary gear system (10). The primary motor (PM) having a single stator and a rotor (A). Said rotor (A) having a piston inside a hollow block which is connected to a spur gear through a pusher block and rotates the particular spur gear (a, b, c) respectively and spur gear rotates the sun gear (SG) and said sun gear (SG) rotates the planet gears (AA, BB) whereby the planetary carrier (40) is rotate and transmit the rotation and torque at the output shaft (50). On the planet gear output shaft (50), the regenerative system is configured. The auxiliary motor (AM) rotates the whole primary motor (PM) and ring gear (R) which increase the speed and torque at the output shaft (50).

Description

[0001] ELECTRO-MECHANICAL GEAR DRIVE SYSTEM

[0002] Field of invention

[0003] The present invention relates to an electro-mechanical gear drive system and more particularly it relates to anelectro-mechanical gear drive system for traction vehicle and configured to transmit the mechanical energy efficiently.

[0004] Background of invention

[0005] Transportation of goods and transportation of people require from one place to other place through different type of transportation mode. Such transportation is road transportation, rail transportation, air transportation and water transportation. Intercity of any state / pro vinces preferably choose transportation through the road transportation mode. Road transportation vehicles are driven through traditional combustion engine which use the fossil fuel such as petrol and diesel.

[0006] The trend towards designing and building fuel efficient, low emission vehicles has increased dramatically over the last decade, this trend driven by concerns over the environment as well as increasing fuel costs. With aggravation of fuel shortage, environmental pollution and increasing fuel costs problems of modern society, as a new energy vehicle, an electric vehicle attracts wide attention. Due to the use of electrical energy as their power sources, electric vehicles have significant advantages in terms of emission reduction, energy saving or the like, as compared with conventional vehicles which solely use gasoline or diesel oil as power source. Therefore, in the current age of promoting green environment protection, the electric vehicles are gradually becoming the trend of development in vehicle industry. The electric vehicle is a vehicle powered by an in-vehicle power supply, using motor to drive vehicle wheels, and obeying various requirements of road traffic and safety regulations. At present, electric drives of electric vehicles and hydrogen vehicle generally use a gearboxwith single gear ratio. At present, the domestic traditional passenger car gearboxes are mainly manual and automatic gearboxes. For electric drive devices, the combination of motors and gearboxes has begun small-scale demonstration applications.

[0007] US5427196A discloses a structure for regulating the rotational direction of the output shaft of a hybrid vehicle is disclosed. The structure comprises a torque generating means for driving a drive wheel; a gear assembly unit including a first to a third element, the first element being adapted to receive a rotation from the torque generating means and the second element being adapted to transmit the rotation to an output shaft connected to the drive wheel; a case to house the gear assembly unit therein; and a rotation regulation means including a first coupler and a one-way clutch, the coupler and the one-way clutch being connected to the third element of the gear assembly unit, either of the coupler and the one-way clutch being disposed between the third element and the case, the other being disposed between the third element and a different one of the elements, so that the output shaft is only allowed to rotate in one direction when the coupler is coupled.

[0008] The limitation of the prior art and conventional vehicle is that the torque, speed and range characteristics of the electric vehicle are depend on the electrical drive of the said vehicle which is low compared to the conventional IC engine type vehicle. Its reliability and transmission efficiency have yet to be technically broken. At the present, the electric motor drive device has a single speed gear box, and it cannot fully utilize the low-speed constant torque and constant power characteristics of the motor. It is necessary to choose a drive motor with a larger torque and high rpm. Further, such gear box comprises clutch plates and the fluid coupling to transmit the rotational power. Said gear box having a complicated arrangement. The fluid coupling is a device used for transmit the power from one shaft to another shaft by means of acceleration and deceleration of hydraulic fluid. While transmit the power, the output speed is less than the input speed which called as a slip. Due to the use of the fluid coupling, there is always slipis present. Further, it cannot develop appropriate range of torque under stalling condition; the coupling dissipates energy as heat it may lead to damage.

[0009] In order to cop-up with above difficulties, it is an immediate need to provide an electro-mechanical gear drive system for the electrical vehicle e.g. car which improves the torque and speed characteristics, increase the efficiency and eliminatesand obviates the existing problems, shortcomings and inadequacies associated with thevehicle technologies.

[0010] Object of invention

[0011] The main object of the present invention is to provide theelectro-mechanical gear drive system.

[0012] Another object of the present invention is to provide a single motor with multiple gear ratio.

[0013] Yet another object of the present invention is to provide the electromechanical gear drive system which provides the high torque and high maximum speed at output.

[0014] Still another object of the present invention is to eliminate the use of clutch and the fluid coupling which eliminates the problems and losses associated with the clutch and the fluid coupling for achieve multi gear ratio.

[0015] Yet another object of the present invention is to provide the electromechanical gear drive system which having regenerative system to increase the drive range. Still another object of the present invention is to provide the electromechanical gear drive system which utilizes the more gear ratio for meet the speed and torque requirements.

[0016] Yet another object of the present invention is to providethe automatic operation of the motor and gear drive system with required amount of output torque and speed.

[0017] Still another objective of the present invention is to provide high performance in all condition.

[0018] Yet another objective of the present invention is to improve the acceleration throughout the driving range.

[0019] Summary of invention

[0020] The present invention relates to anelectro-mechanicalgenerator gear drive system which comprises a primary motor and an auxiliary motor anda planetary gear system and a generator. The primary motor comprises an axially stator and the rotor. Said rotorhaving a motor shaft inside a hollow block of the rotor which is free to move linearly by actuator but fitted with rotor for rotary motion and that is connected to the piston along withthe pusher block. The pusher block is engagewith particular spur gear. The ring with jointer blocks is axially mounting outside of the motor shaft and the cover which has the grooves for jointer blocks is fitted inside the spur gear. Said spur gear is engaged with the step sun gear. Step sun gear is engaged with the plurality of planet gears and plurality of planet gears are meshed with the internal circumferential teeth of the ring gear.

[0021] On an output shaft of the planetary gear system, the regenerative system is configured. Said regenerative system having a feedback system whereby the generation of power is adjusting by the moving the permanent magnet of generator through actuator. The auxiliary motor rotates the whole primary motor and the ring gear which increase the speed and torque at the output shaft. Based on the feedback system, the position of the pusher block is changed and active the other spur gear and auxiliary motor.

[0022] Detail description of drawings

[0023] Fig.l illustrates a block diagram of electro-mechanicalgear drive system according to present invention.

[0024] Fig.2 illustrates a perspective view of electro-mechanicalgear drive system according to present invention.

[0025] Fig. 3 illustrates a cross section view of primary motor of electromechanicalgear drive system according to present invention.

[0026] Fig. 4 illustrates a perspective view of spur gear of primary motor of electromechanicalgear drive system according to present invention.

[0027] Fig. 5 (a) illustrates a perspective view of engage position of spur gear of primary motor of electro-mechanicalgear drive system according to present invention.

[0028] Fig. 5 (b) illustrates a cross section view of engage position of spur gear of primary motor of electro-mechanicalgear drive system according to present invention.

[0029] Fig. 6 illustrates a cross section view of sun gear with planetary gear assembly of electro-mechanicalgear drive system according to present invention.

[0030] Fig. 7(a) illustrates a perspective view of auxiliary motor of electromechanicalgear drive system according to present invention.

[0031] Fig. 7(b) illustrates a cross section view of auxiliary motor of electromechanicalgear drive system according to present invention. Fig. 8 illustrates the first gear of auxiliary motor of electro-mechanicalgear drive system according to present invention.

[0032] Fig. 9 illustrates a perspective view of planetary gear assembly with planetary carrier and generator of electro-mechanicalgear drive system according to present invention.

[0033] Fig. 10 illustrates a cross section view of planetary carrier of the planetary gear system with generator of electro-mechanical gear drive system according to the present invention.

[0034] Fig. 11 illustrates a cross section view with different stages of the generator of electro-mechanicalgear drive system according to the present invention.

[0035] Fig. 12 illustrates a perspective view of the electro-mechanicalgear drive with auxiliary motor-2 as another embodiment of electro-mechanicalgear drive system according to the present invention.

[0036] Detail description of invention

[0037] The nature of the invention and the manner in which it works is clearly described in the complete specification. The invention has various embodiments and they are clearly described in the following pages of the complete specification. Before explaining the present invention, it is to be understood that the invention is not limited in its application.

[0038] It is to be understood that in the drawings of the planet gear, we have provided only two planet gears (AA and BB) in the planet gear system (10) for clarity regarding cross sectional view and their depth understanding of the configuration. Actually for the working of the invention, at least three planet gears are used. The bearings are also used for reducing the friction (not shown). The invention discloses anelectro-mechanicalgear drive system. Referring Fig. land 2of the present invention shows the block diagram, perspective view and cross section view of the electro-mechanicalgear drive system. Theelectro-mechanical gear drive system, in accordance with embodiments of the present invention, mainly comprisesa primary motor (PM) and an auxiliary motor (AM) in which the primary motor (PMhaving a single stator (S),a single rotor (A), a motor shaft (39), and spur gears (a, b, c); the auxiliary motor (AM) having a single stator (T) and a rotor (X); A planetary gear system (10) comprises a common sun gear (SG), aplurality of planet gears(AA, BB, CC (CC-not shown)), a ring gear (R) and a planetary carrier (40); a generator (11) having a generator stator (30) and a rotor (20) mounted onan output shaft (50)which rotate the wheel and also generates the electrical energy and store the electrical energy in abattery (100). Said primary motor (PM) and auxiliary motor (AM) are driven through the battery (100). Said battery (100)is charged through external supply e.g. service mains. The primary motor (PM), auxiliary motor (AM) and the generator (11) are controlled by the actuators (80) through an electric control unit (ECU)according to the feedback signals provided from the sensors i.e. throttle position sensor and RPM sensor configured at the input side and output side respectively.

[0039] Referring Fig. 2 of the present invention shows the perspective view of the electro-mechanicalgear drive system.Now, as shown in Fig. 3, theprimary motor (PM) comprises the stator (S)configured above the rotor (A). The rotor (A) is provided with a piston (P) in the hollow block inner side and a motor shaft (39) is connected with the pistonwhich is free to move linearly by an actuator (80). The motor shaft (39) is fitted with rotor for rotary motion and that is connected to the piston along with the pusher block (45) on the other end. The piston (P) is smaller than hollow blocksuch that it can only move linearly inside the hollow block. The motor shaft (39) having a pusher block (45) fitted on the surface of the motor shaft (39) outside the hollow block. The rotor (A) is connected with the spur gear (a, b, c) through pusher block (45) of the motor shaft (39). Referring Fig. 4, at the end of the motor shaft (39) of the rotor (A) of the primary motor (PM), the spur gear (a), spur gear (b) and spur gear (c)is mounted respectively in different vertical plane. Said three spur gears (a, b, c) having different numbers of teeth and diameter. The spur gear(c)having less number of teeth compared to spur gear(b). In similar way, the spur gear (b) having less number of teeth compared to the spur gear (a). Said spur gear (a, b, c)are aligned with each other such that the size and number of teeth of the spur gears (a, b, c) are arranged in the step manner. The sun gear (SG)of the planetary gear system (10) is configured over the said spur gears (a, b, c) as shown in Fig. 6.

[0040] Referring Fig. 4 and Fig. 5, each spur gear (a, b, c) is mounted on a hollow cover having internal groove (42). The internal grove (42) coveris mounted on aring (41) having a jointer blocks (51) where the jointer blocks (51) provides connection between the motor shaft (39) and the spur gear (a or b or c) by engaging in the internal groove (42) of the hollow cover. The piston (P) of the rotor (A) provides linear motion through actuator (80) and push the jointer block (51) in outward direction, where the pusher block (45) reaches at the place of the jointer block (51), the pusher block (45) push the jointer block (51) to outward direction. The jointer blocks (51) of the ring (41) fixed in the internal grooves (42) of the hollow cover to provide connectivity with the spur gear (a or b or c). As the jointer blocks (51) engage with the internal grooves (42) of respective hollow cover of the spur gear (a or bor c), the spur gear (a or b or c) also rotate with the motor shaft (39).

[0041] Said stator (S) and rotor (A) are assembled and form the primary motor (PM) and enclosed in the enclosure body (70). A ring gear (R’) is rigidly mounted on the enclosure body of the primary motor (PM) such that the whole primary motor (PM) is being surrounded by the teeth of the ring gear (R’) as shown in Fig.2.

[0042] Referring Fig. 6, the planetary gear system (10) comprises the common sun gear (SG) having teeth on outer circumferential surface and inner circumferential surface. In the inner circumferential surface’s teeth are configured in such step manner that the inner circumferential surface’s teeth are engaged with the spur gear (a or b or c)mounted on the shafts of the rotor (A) of the primary motor (PM).

[0043] As shown in Fig. 2 and 6, the planet gears (AA, BB) are engaged with the teeth of the outer circumferential surface of the sun gears (SG). In said gear system, plurality of the planet gears (AA, BB) can be arranged and the number of the planet gears is at least three. On the said combination of the planet gears (AA, BB) with the sun gear (SG), thering gear (R) is set uphaving teeth in inner circumferential surface and is configured such that each planet gear teeth (AA, BB)engaged with said inner teeth of the ring gear (R). Said ring gear (R) also having the teeth on the outer circumferential surface.

[0044] Referring Fig. 6 and 9, the planetary carrier (40) is configured with the planet gears (AA, BB) through the bearing (not shown). On thecentre of said planetary carrier (40), the output shaft (50) is axially mounted.

[0045] The whole combination of the sun gear (SG), planet gears (AA, BB), ring gear (R) and planetary carrier (40) forms the planetary gear assembly (10).

[0046] Referring Fig. 1, 2 and 10, the output shaft (50)configured with the adjustable permanent magnet generator (11). The shaft of the generator’ srotor (20) is configured with output shaft (50) and on the surrounding of the said generator’s rotor (20), the generator’s stator (30) generator (l l)is configured.

[0047] Referring Fig. 7(a), 7(b) and 8 of the present invention shows the auxiliary motor (AM) configuration. The auxiliary motor (AM) comprises one stator (T) and rotor (X).

[0048] At the end of the shaft of the rotor (X), the spur gear (x’) and spur gear (y’) is mounted respectively. Said spur gear (x’, y’) aligned with each other such that the size and number of teeth of the spur gears (x’, y’) are arranged in the step manner as shown in Fig. 7(b).

[0049] Said spur gear (x’) is mounted on the motor shaft (39) of the rotor (X) in such way that spur gar (x’) is rotate when motor shaft (39)rotate but linearly not fixed with motor shaft (39). So, when motor shaft (39) of rotor (X) rotate spur gear (x’) rotate but motor shaft (39) is linearly move by actuator (80) the spur gear (x’) is not linearly move. Said motor shaft (39) allow rotation of the spur gear (x’) through the activating the rotor (X) without rotating the spur gear (y’). However, the motor shaft (39) allows the rotation of the spur gear (x’) while activating the rotor (X) to rotate thespur gear (y’).

[0050] Said spur gear (x’) is being engaged with the ring gear (R) of the planetary gear system (10) as shown in Fig. 2. In similar way, the spur gear (y’) of the auxiliary motor (AM) is being engaged with the ring gear (R’) mounted on the enclosure body (70) of the primary motor (PM) as shown in Fig. 2. Said auxiliary motor (AM) develop the additional torque and speed as per the position changed in the movable shaft with pusher block (45) of the rotor (X) of auxiliary motor (AM).

[0051] The rotor (X) of the auxiliary motor (AM) rotates the whole primary motor (PM) by engagements of the ring gear (R’) mounted on the body (70) of the primary motor (PM) and spur gear (y’) of the rotor (X). Due to the motor shaft (39), rotation of the spur gear (y’) also rotates the spur gear (x’) mounted on the shaft of the rotor (X) of auxiliary motor (AM). Due to the rotation of the rotor (X) of the auxiliary motor (AM), the ring gear (R)of the planetary gear system (10) is rotate.Due to the two input i.e. whole primary motor (PM) rotation and ring gear (R) rotation by the auxiliary motor (AM), the additional torque and speed is developed and said auxiliary motor (AM) rotates the whole primary motor (PM) and ring gear (R) of the planet gear system (10) as per the feedback signals and control signals from the electronic control unit (ECU). The primary motor (PM) and auxiliary motor (AM) are driven through the battery (100) and generated power by the generator (11) mounted on the output shaft (50) is stored in the battery (100). In the present invention, the higher gear ratio is used for the working of the generation of the electrical energy through the generator (11). Said generator (11) having actuator (80)which adjust the permanent magnets of the stator (30) of the generator based on receiving the feedback signalsas shown in Fig. 11. As shown in Fig. 11, the permanent magnet of the stator (30)are moving inward or outward with respect to the generator’s rotor (20) by the actuator (80) as per the feedback signals and control signals from the electronic control unit (ECU). The electronic control unit (ECU) collects the data from the feedback sensor i.e. position sensor, RPM sensor etc. and determine the load on the output shaft (50) of the system and input given by the user to the system i.e. throttle paddle position. Based on the determination, the control signal is given to the actuator (80) of the generator (11).

[0052] E.g.when the load on the output shaft is negligible or on no load condition, the permanent magnets of the generator’s stator (30) are forms minimum air gap between the stator (30)permanent magnetas shown in Fig. 11(a) and generate the maximum electrical energy from output shaft.

[0053] When the load on the output shaft (50) gradually increases, the air gap between the stator (30) permanent magnetis also gradually increased by moving the adjustable permanent magnets of the stator (30) in outward direction through the actuator (80) controlled by the ECUas shown in Fig. 11 (b) & (c).

[0054] In similar way, when the load on the output shaft (50) gradually decreases, the air gap between the stator (30)permanent magnetis also gradually decreases by moving adjustable permanent magnets of the stator (30) to inner ward direction through the actuator (80) controlled by the ECUas shown in Fig. 11 (a).

[0055] Hence, as per the condition of the load on output shaft (50) and requirement of the load, the adjustable permanent magnet of the generator (11) adjust the position and generates the maximum output electrical energy from the generator (11) by using the waste or non-usable mechanical energy from the system during the operationand without affecting the performance of the driving. Said generated electric power is store in the battery (100).

[0056] It is to be understood that in the present invention, the generation of electrical energy using generator not limited only thereto. The other generation system which can operate through the variable load and speed can be used for the production of the electrical energy.

[0057] The torque and speed of the output (50) is depends on the configuration of the primary motor (PM), auxiliary motor (AM) and the planetary gear system(lO). In the present invention, in the primary motor (PM) having pusher block (45) which moves linearly with the piston (P) of the motor shaft (39) according to the requirement of the torque and speed. An electronic control unit (ECU)takes the feedback signal from the output shaft (50)through the RPM (revolution per minute) sensor and throttle position sensor. According to the feedback signal from the said sensors, the control unit (ECU) change the position of the pusher block (45) of primary motor (PM) throughthe actuator (80)and due to that the automatically gear ratio is changed and manage speed and torqueof the output shaft (50).

[0058] Referring Fig. 1 and 2, Electric control unit (ECU) comprises a controller which collect all data from the sensor i.e. position sensor and the RPM sensor and according to that data, the ECU sends the signal to the actuator (80). Said actuator (80)actuate the position of pusher block (45) of the primary motor (PM) and of the auxiliary motor (AM). Further, the actuator (80) also actuates the permanent magnets of the stator (30) of the generator (11).

[0059] To achieve the highergear ratio, the actuator (80)actuates the position of thepusher block (45) of the motor shaft (39) of the rotor (A) to push the jointer blocks (51) in outward direction to engage with the internal grooves (42) of the hollow cover of the spur gear (c). Hence, the rotor (A) of the primary motor (PM) rotates the spur gear (c) and due to that the common sun gear (SG) is also rotate. As the sun gear’s (SG) outer teeth are engaged with the planet gears (AA, BB), the planet gears (AA, BB) are rotate. Said planet gears (AA, BB) are rotates on the internal teeth of the ring gear (R). However, at that time of the rotation of the planet gears (AA, BB), the ring gear (R) is fixed. The output is carried out from the output shaft (50) of the planetary carrier(40) mounted on the planet gears (AA, BB).

[0060] The formula for calculation of the output speed while the input is from the sun gear (SG) through the primary motor (PM),

[0061] Where,

[0062] Nout ut = Speed of planetary carrier (output speed)

[0063] Nsun gear =Speed of sun gear

[0064] Ts=Number of teeth of sun gear

[0065] Tr=Number of teeth of ring gear

[0066] For instance, an activation to rotate the motor shaft (39) of the rotor (A) of the primary motor (PM) for rotate the spur gear (c), the spur gear (a, b) is also rotate. Due to the common engagement of the sun gear (SG) with the spur gear (a, b, c), other inactive spur gears (a, b) are also being rotate.

[0067] After achieving the appropriate speed and torque at the output shaft (50), the change in the gear ratio, speed and torque can be achieved by using the movement ofthe pusher block (45) along with jointer block (51) of the rotor (A) of primary motor (PM). The change in the position of the pusher block (45) of primary motor (PM)is according to the feedback signal received by the ECU. As the speed of the inactive spur gear (a, b) is already achieved through the rotation of the common sun gear (SG), it does not required to catch the previous speed from starting when the jointer block (51) moves over the another inactive spur gear (a, b). Said mechanism of the sun gear (SG) with the spur gear (a, b, c) for back motion of the rotation is carried out smooth operation, avoid the jerk during the change in gear ratio, no extra power consumption and receives the torque and speed according to the feedback signals on the output shaft (50).

[0068] When more torque-speed is required, the ECU activates the auxiliary motor (AM). Initially, the actuator (80) actuates the position of the stator (T) of the auxiliary motor (AM) over the rotor (X) which associated with the spur gear (x’) having lower number of teeth. Hence, the rotor (X) of the auxiliary motor (AM) rotates the spur gear (x’) and said additional mechanical energy transferred to the ring gear (R) of planetary gear system (10).

[0069] Due to the input from the sun gear (SG) through the primary motor (PM) and input from the ring gear (R) through the auxiliary motor (AM), the planetary gear transfer more power to the output shaft (50).

[0070] The formula for calculation of the output speed while two inputsare given i.e. input from the sun gear (SG) through the primary gear (PM) and input from the ring gear (R) through the auxiliary motor (AM),

[0071] Where,

[0072] Nout ut = Speed of planetary carrier (output speed) Nsun gear =Speed of sun gear Nring gear =Speed of ring gear Ts=Number of teeth of sun gear

[0073] Tr=Number of teeth of ring gear

[0074] The ratio of the spur gear (x’) of the rotor (X) of the auxiliary motor (AM)and the ring gear (R) of planetary gear system (10) is high which gives the high torque to the output shaft (50).

[0075] For addition of the speed, the ECU activates the auxiliary motor (AM) in which the actuator (80)actuates the position ofpusher block (45) of the auxiliary motor (AM) over the rotor (X) which associated with the spur gear (y’) having higher number of teeth. Hence, the rotor (X) of the auxiliary motor (AM) rotates the spur gear (y’) and said additional mechanical energy transferred to the ring gear (R’) surrounded on the enclosurebody (70)of the primary motor (PM). As a single shaft for spur gear (x’) and (y’) when ECU active the spur gear (y’) by pusher block(45) movement the spur gear (x’) is also active and deliver the rotational power by the spur gear (x’) to the ring gear (R).

[0076] As the rotation of the whole primary motor (PM) through the auxiliary motor (AM), the relative speed is increase. Further, the rotation of the ring gear (R) also sum up in the output speed at the output shaft (50).

[0077] The formula for calculation of the output speed while the whole primary motor (PM)rotate through the auxiliary motor (AM), input from the sun gear (SG) through the primary gear (PM) and at same time input is given to the ring gear (R) of the planetary gear system (10) through the auxiliary motor (AM) is,

[0078] Where,

[0079] NOut ut= Speed of planetary carrier (output speed) Nsun gear =Speed of sun gear

[0080] Nnng gear =Speed of ring gear

[0081] NPm=Speed of ring gear mounted on the body of the primary motor

[0082] Ts=Number of teeth of sun gear

[0083] Tr=Number of teeth of ring gear

[0084] Another embodiment of the present invention is shown in Fig. 12. The Fig. 12 shows the configuration of the auxiliary motor (AM) of the present invention with an auxiliary motor-2 (AM2). In this embodiment, the primary motor (PM), auxiliary motor (AX) and planet gear system (10) having similar construction according to the present invention. As shown in Fig. 12, auxiliary motor-2 (AM2) having a ring gear (R”) surrounded on the enclosure body-2 (90). On the shaft of the auxiliary motor-2 (AM2), the spur gear (u) is mounted.

[0085] The ring gear (R”) of the auxiliary motor-2 (AM2) is engaged with the spur gear (x’) of auxiliary motor (AM) according to the present invention. The spur gear (u) of the auxiliary motor-2 (AM2)is configured with the ring gear (R) of the planetary gear system (10) according to the present invention.

[0086] The spur gear (y’) of the auxiliary motor (AM) is configured with the ring gear (R’) surrounded on the enclosure body (70) of the primary motor (PM) according to the present invention.

[0087] When spur gear (x’) of the auxiliary motor (AM) activate to rotate by ECU, whole auxiliary motor-2 (AM2) is rotate through the ring gear (R”). Said arrangement increases the relative speed of the auxiliary motor-2 (AM2). The speed of the spur gear (u) of auxiliary motor-2 (AM2) is increases. The formula for calculation of the output speed while primary motor is active and the spur gear (x’) of the auxiliary motor (AM) is active the rotation of the whole auxiliary motor-2 (AM2) and also the auxiliary motor -2 (AM2) is also active,

[0088] Where,

[0089] Nout ut=Speed of planetary carrier (output speed)

[0090] Nsun gear =Speed of sun gear

[0091] Nring gear =Speed of ring gear

[0092] Nam-2 =Speed of ring gear mounted on the body of the auxiliary motor-2

[0093] Ts=Number of teeth of sun gear

[0094] Tr=Number of teeth of ring gear

[0095] When spur gear (y’) of the auxiliary motor (AM) activates to rotate by ECU, the spur gear (x’) of the auxiliary motor (AM) also rotate due to a single common shaft arrangement according to the present invention. Due to rotation of the spur gear (x’, y’), the whole auxiliary motor-2 (AM2) and primary motor (PM) are rotate through the ring gear (R”) and ring gear (R’) respectively. Said arrangement increases the relative speed of the auxiliary motor-2 (AM2) as well as primary motor (PM).

[0096] The formula for calculation of the output speed while the spur gear (x’) of the auxiliary motor (AM) activates the rotation of the whole auxiliary motor-2 (AM2) and simultaneously the auxiliary motor -2 (AM2) is active and also at same time, spur gear (y’) of the auxiliary motor (AM) actives the rotation of the whole primary gear (PM) and simultaneously, the primary motor (PM) is active, Where,

[0097] Noutput= Speed of planetary carrier (output speed)

[0098] Nsun gear =Speed of sun gear

[0099] Nnng gear =Speed of ring gear NPm= Speed of ring gear mounted on the body of the primary motor

[0100] Nam-2 =Speed of ring gear mounted on the body of the auxiliary motor-2

[0101] Ts=Number of teeth of sun gear

[0102] Tr=Number of teeth of ring gear

[0103] As describes in the above, the primary motor (PM) with planetary gear system (10) generates the speed and torque and auxiliary motor (AM) generated the additional torque and speed as per the requirements and achieve higher efficiency. The numbers of the auxiliary motors (AM)varies and configured with the Primary motor (PM) according to the present invention and are not limited thereto.

[0104] By using the above configuration of the auxiliary motor (AM) with primary motor (PM), different range of the speed and torque can be achieved at the output shaft (50). These can be achieved in the following type of the motor combinations.

[0105] It is to be understood that the present invention is configured with the Al (artificial intelligence) and ML (Machine learning) system. By using of Al and ML in the present invention, said Al and ML system collect daily data of the different type of drivers and his driving skill behavior of driving andpattern like throttling pattern, driving modes, breaking pattern etc. and generates the different types of the data packs for different types of the drivers. The drivers can choose the mode of the operating the vehicle i.e. economical mode, power mode and auto mode. The selection of the economical mode configured to operate the system in power saving mode. The power mode configured to operate the system in high torque and speed output mode. The auto mode is configured to provide an automatic operation of the driving system based on the data packs of particular driver collected by Al and ML.

[0106] Said Al and ML of the system also configured with the online mapping system applications which give the information regarding the route, speed limit and the conditions of the route i.e. slope, traffic, type of road etc. to control and regulate the system of the present invention. The ECU of the present invention collects the data and based on the condition of the route the ECU automatically change the mode from economical mode to power mode for the particular time of the conditions in auto mode. Further, the Al and ML change the gear ratio as per driver requirements in different condition automatically in auto mode.

[0107] Further, the generator of the present invention able to produce the electrical energy while the system of the present invention is configured with the vehicle and no input is provided in the down slop, the momentum of the vehicle rotates the generator’s rotor and generates the electrical energy which stored in the battery of the system according to the present invention.

[0108] It is to be understood that the present invention is used for the electrical vehicle, hybrid vehicle and hydrogen vehicle system or in automobile industries and it is not limited thereto. Further, the present invention has an application in electric power generation sector and industrial sector where the load and speed are variable with respect to the time.

[0109] 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.

[0110] Reference Numerals

[0111] Primary motor (PM)

[0112] Auxiliary motor (AM)

[0113] Rotor of the primary motor (A)

[0114] Rotor of the auxiliary motor (X, Y)

[0115] Stator of the primary motor (S)

[0116] Stator of the auxiliary motor (T)

[0117] Spur gear rotor of primary motor (a, b, c)

[0118] Spur gear rotor of auxiliary motor (x’, y’)

[0119] Sun gear (SG)

[0120] Planet gear (AA, BB)

[0121] Ring gear (R)

[0122] Ring gear of body of Primary motor (R’)

[0123] Planetary gear system (10)

[0124] Generator (11)

[0125] Generator rotor (20)

[0126] Generator stator (30)

[0127] Planetary carrier(40)

[0128] Output shaft (50)

[0129] Enclosure Body of the Primary motor (70)

[0130] Actuator (80)

[0131] Battery (100)

[0132] Enclosure Body of the auxiliary motor-2 (90)

[0133] Auxiliary motor-2 (AM2)

[0134] Ring gear of enclosure body of auxiliary motor - 2 (R”) Spur gear of the auxiliary motor (u)

[0135] Piston (P)

[0136] Pusher block (45)

[0137] Jointer blocks (51) Motor Shaft (39)

[0138] Internal grooves (42)

[0139] Ring (41)

Claims

We Claim:

1. A electro-mechanicalgenerator gear drive system comprises a primary motor (PM), at least one auxiliary motor (AM) anda planetary gear assembly (10); characterized in that, said primary motor (PM) comprises, a stator (S) mounted on a rotor (A), said rotor (A) mounted on a motor shaft (39), said motor shaft (39) comprising of a piston (P) connected with actuator (80) on one side and a pusher block (45) on the surface of the motor shaft (39) on other side; at extreme end of the motor shaft (39) having a corresponding spur gear (a, b, c) aligned with each other and the size and number of teeth of saidspur gears (a, b, c) are arranged in the step manner;and said spur gear (a, b, c) mounted on a hollow cover with an internal groove (42), said hollow cover having jointer blocks (51) to engage with the motor shaft (39); said primary motor (PM)enclosed in an enclosure body (70) and said enclosure body (70) of the primary motor (PM) is surrounded by the teeth of a ring gear (R’); said the auxiliary motor (AM) comprises, an axially movable rotor shaft; at extreme end of the plurality of shaft having a corresponding spur gear (x’, y’) aligned with each other and the size and number of teeth of the spur gears (x’, y’) are arranged in the step manner; and corresponding spur gear (y’) of auxiliary motor (AM) is engaged with the ring gear (R’) surrounded on the primary motor (PM);said planetary gear assembly (10) comprises, a sun gear (SG) having outer and inner circumferential surface configured with a teeth in a manner as teeth are engaged with the plurality of spur gear (a, b, c) of primary motor (PM); a plurality of planet gear (AA, BB)areengaged with the sun gear (SG); a ring gear (R) having a teeth at outer and inner circumferential surface and said teeth of inner circumferential surface of ring gear (R) are engaged with a plurality of planet gear (AA, BB) and said teethof outer circumferential surface are engaged with the corresponding spur gear (x’) of auxiliary motor (AM); a planetary carrier (40) being rotatably connected to said planet gear (AA, BB) of planetary gear system (10) and an output shaft (50) being axially connected with the planetary carrier (40);2. The electro-mechanicalgenerator gear drive system as claimed in claim 1, wherein the motor shaft (39) of the primary motor (PM)connected with the respective spur gear (a, b, c)through pusher block (45) by engaging to the internal groove (42) of the spur gear (a, b, c).

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