CN210484546U - Binary active speed variator - Google Patents

Abstract

A binary initiative derailleur, a reduction gear that can realize infinitely great to infinitesimal reduction ratio without multistage speed reduction, it is at the stator of current planetary reducer, cycloid pin wheel reduction gear or harmonic reduction gear, speed change gear or power device are introduced in the ternary drive structure of rotor and output element, make the stator have initiative rotational speed, thereby convert into binary initiative unary driven ternary drive structure, synthetic rotational speed variation range is bigger, can slow down also can accelerate, can also export in different directions, when as the reduction gear, even if do not need multistage speed reduction also can make the reduction ratio reach infinitely great at most, adopt the embodiment of double dynamical drive to need not increase complicated gearshift and just can realize stepless speed regulation, the structure is succinct, high convenience in use.

Description

Binary active speed variator

Technical Field

The utility model relates to a derailleur.

Background

The transmission is a transmission device commonly used in mechanical equipment, the number share of the speed reducer is the largest, and at present, the speed reducer mainly comprises a parallel shaft speed reducer, a crossed shaft speed reducer and a coaxial speed reducer, wherein the coaxial speed reducer is widely applied due to small volume and compact structure, and particularly, a new development opportunity is met at present in the high-speed development of the fields of aerospace, automation, robots and the like, and meanwhile, higher requirements are also put forward on the technical level. The coaxial reducer technology types mainly include a planetary reducer, a cycloidal pin gear reducer and a harmonic reducer, which have a common characteristic-all belong to a ternary transmission structure, that is, all include assemblies distributed around a common shaft and respectively used as three roles of a stator, a rotor and an output element, the stator is fixed, the rotor and the output element rotate or revolve, the rotor drives the output element by using the stator as a fulcrum, and roles among the elements can be interchanged, such as a planetary gear 101, an outer ring 102 and a sun gear 103 in the planetary reducer shown in fig. 1, a cycloidal gear 201, a pin gear 202 and an eccentric gear 203 in the cycloidal pin gear reducer shown in fig. 2, and a wave generator 301, a rigid gear 302 and a flexible gear 303 in the harmonic reducer shown in fig. 3. The speed reducers with the three-element structures can obtain various speed reduction ratios by interchanging the roles of the components, but the distance between different speed reduction ratios is not too large, one set of device generally has only one gear, and multiple stages of speed reduction are often required to obtain larger speed reduction ratios under the condition of acceptable size, so that the structure becomes complicated, and the volume, the weight and the manufacturing cost are increased.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a driven ternary transmission structure derailleur of binary initiative monobasic, contain the stator at current coaxial type reduction gear, speed change gear or power device are introduced in rotor and output element's ternary transmission structure, make the stator have initiative rotational speed for output element, thereby convert into the driven ternary transmission structure of binary initiative monobasic, synthetic rotational speed scope is big, can slow down and also can accelerate, can also be in not equidirectional output, when being the reduction gear, even if do not need multistage speed reduction also can make the reduction ratio reach infinity at most, adopt two power drive's embodiment not need increase complicated gearshift and just can realize stepless speed regulation, and the structure is succinct, and convenient for use.

The utility model discloses with the unset installation of subassembly as the stator in the coaxial reduction gear of ternary drive structure, have initiative rotational speed for output element, form binary initiative unary driven ternary drive structure from this-former rotor is first rotor, and former stator is the second rotor, and combined action decides output element's output result.

The utility model discloses a first rotor and second rotor drive output element side by side, the rotational speed of the synthetic output element of both sides' rotational speed.

The utility model discloses a first rotor is direct drive output element not, but participates in the drive second rotor and makes it have initiative rotational speed for output element, by second rotor individual drive output element, the output rotational speed of the synthetic output element of rotation speed and revolution speed of oneself.

The utility model discloses have preceding stage speed reduction structure, make first rotor and second rotor work under the rotational speed that is lower than initial input rotational speed.

The utility model discloses have the speed change gear, first rotor or second rotor have initiative rotational speed for the output element through it connects power.

The utility model discloses a first rotor and second rotor are driven by independent power device separately respectively, can change output element's rotational speed through the rotational speed of the different power device input of direct adjustment.

The utility model discloses a same first rotor, second rotor or output element's unit has the mounted position of two or more differences or the same kind structure of the same but parameter difference of function, can obtain different output results through selecting different operating position or functional parameter.

The utility model discloses have controlling device, can be used for controlling output element's output rotational speed.

The utility model has a hollow shaft or a hollow shaft power device.

The utility model discloses have its characterized in that and have birotor structure motor, the rotational speed of two rotors of motor can independent control, is arranged in driving first rotor and the second rotor among the ternary drive structure respectively.

Drawings

FIG. 1 is a three-gear transmission configuration of a planetary reducer;

FIG. 2 is a three-gear transmission configuration of a cycloidal pin gear reducer;

FIG. 3 is a triple drive configuration of a harmonic reducer;

FIG. 4 is an axial view of an embodiment of a parallel configuration;

FIG. 5 is a radial view of an embodiment of a parallel configuration;

FIG. 6 is a radial view of an embodiment with a pre-stage retarding arrangement;

FIG. 7 is an axial view of a tandem configuration for variable speed revolution;

FIG. 8 is a radial view of a tandem configuration of variable speed revolutions;

FIG. 9 is an axial view of a variable speed self-rotating tandem structure;

FIG. 10 is a mechanical multi-gear configuration;

fig. 11 is a motor of a double rotor structure.

Detailed Description

The utility model comprises three components which are respectively used as a rotor, a stator and an output element in the coaxial reducer of the prior ternary transmission structure, and a middle shaft which is used as a common shaft, wherein the roles of the rotor, the stator and the output element in the transmission relation can be exchanged, the specific types of the components can be a sun wheel, an outer ring and a planet wheel of a planetary reducer, a cycloid wheel, an eccentric wheel and a pin wheel of a cycloid pin wheel reducer, a wave generator, a rigid wheel and a flexible wheel in a harmonic reducer, and three components of other reducers with the common characteristics of the same-shaft ternary transmission structure reducers, the difference is that the components which are used as the stator are not fixedly arranged in the utility model, and the three components have driving rotating speeds relative to the output element, thereby forming a binary driving unitary driven ternary transmission structure, namely that the original rotor is the first rotor, and the original stator is the second rotor 2, the co-operation determines the output result of the output element. The use of "first" or "second" followed by "rotor" is intended merely to indicate that the components are not the same as one another, and the roles may be reversed. Referring to the embodiment of the planetary reducer with the parallel structure shown in fig. 4 and 5, a central shaft 5 is used as a power input shaft, a sun gear 4 is used as a first rotor, an outer ring 2 is used as a second rotor, the sun gear and the outer ring drive a planetary gear 3 which is used as an output element in parallel, and the planetary gear 3 revolves or rotates around the central shaft 5; the sun gear 4 is of a single-layer structure or a stepped structure and is fixedly connected with the middle shaft 5; a plurality of planet wheels 3 which are uniformly distributed in the circumferential direction are rotationally connected with a planet carrier 7 to form a whole body which can rotate relative to a middle shaft 5, and the planet wheels 3 are respectively in transmission with a sun wheel 4 and an outer ring 2 and also play a role in speed change when being used as an output element; the planet wheels 1 are used as special variable-speed transmission devices, are uniformly distributed in the circumferential direction, are arranged on the base 6 in a fixed-shaft rotating mode and are respectively in transmission with the sun wheel 4 and the outer ring 2; each unit planet wheel 1 or planet wheel 3 can be a single-layer structure, can also be a ladder structure with a speed change function, can be a single-shaft structure, and can also be a composite structure which is formed by combining a plurality of parallel-shaft planet wheels and can change direction or speed for many times; the outer ring 2 can be of a single-layer structure or a stepped structure and can be respectively in transmission with the planet wheel 1 and the planet wheel 3 at different radius positions; when the central shaft 5 drives the sun gear 4 to rotate to drive the planet gears 3, power is simultaneously shunted to the outer ring 2 through the planet gears 1 to enable the planet gears 3 to have active rotating speed, the sun gear 4 and the outer ring 2 simultaneously and actively drive the planet gears 3 from the same direction or the opposite direction, and the rotation speed vectors of the sun gear 4 and the outer ring 2 are converted into revolution speed vectors of the rotation centers of the planet gears 3, namely the rotation speed vectors of the planet carrier 7, and the revolution speed vectors are used as output results. When the angular speed directions of the sun gear 4 and the outer ring 2 are the same in size, namely the relative speed is zero, the reduction ratio is 1, the ratio of the absolute values of the angular speeds of the sun gear 4 and the outer ring 2 is closer to the inverse ratio of the teeth numbers of the sun gear 4 and the outer ring 2, the absolute value of the reduction ratio is larger, when the ratio of the absolute values of the angular speeds of the sun gear 4 and the outer ring 2 is equal to the inverse ratio of the teeth numbers of the sun gear 4 and the outer ring 2, the linear speeds of the radial positions of the transmission of the planet gear 3 are opposite in size, the output rotating speed is zero, and the reduction ratio is. The power input, the power split and the power combination can also adopt the mode that the power is input from the outer ring 2, the outer ring 2 drives the sun wheel 4 through the planet wheel 1, the outer ring 2 and the sun wheel 4 drive the planet wheel 3 in parallel, or the structure is adjusted to be that the power is directly divided into two paths to respectively reach the planet wheel 3 through the sun wheel 4 and the outer ring 2, and the link that the sun wheel 4 and the outer ring 2 are connected in series is not available in the whole process. The sun gear 4 and the outer ring 2 can be driven by the same power device by dividing power, and can also be driven by independent power devices respectively; when the sun wheel 4 and the outer ring 2 are respectively driven by independent power devices, the planet wheel 1 as a special variable-speed transmission device can be omitted; the power device can be of the type including but not limited to an electric motor, an engine, an external device and a component of the system. The transmission modes between the sun gear 4, the planet gears 3 and the outer ring 2 include, but are not limited to, friction transmission, meshing transmission, magnetic transmission or flexible transmission. The outer ring 2, the planetary wheels 3 and the sun wheel 4 can be replaced by the cycloidal wheel 201, the pin wheel 202 and the eccentric wheel 203 of the cycloidal pin gear speed reducer shown in fig. 2, or replaced by the wave generator 301, the rigid wheel 302 and the flexible wheel 303 of the harmonic speed reducer shown in fig. 3, or replaced by other assemblies of coaxial speed reducers with stators, rotors and output elements according to the same binary driving and one-element driven transmission relation, thereby forming a new embodiment. The first rotor and the second rotor are in a parallel drive relationship in the embodiment of fig. 4, and a series drive configuration as shown in the embodiments of fig. 8 and 9, described in detail below, may also be employed.

The utility model discloses a first rotor and second rotor drive output element side by side, the synthetic output element's of both sides's rotational speed. Referring to the embodiment of the planetary reducer with the parallel structure shown in fig. 4 and 5, a central shaft 5 is used as a power input shaft, a sun gear 4 is used as a first rotor, an outer ring 2 is used as a second rotor, the sun gear and the outer ring drive a planetary gear 3 which is used as an output element in parallel, and the planetary gear 3 revolves or rotates around the central shaft 5; the sun gear 4 is of a single-layer structure or a stepped structure and is fixedly connected with the middle shaft 5; a plurality of planet wheels 3 which are uniformly distributed in the circumferential direction are rotationally connected with a planet carrier 7 to form a whole body which can rotate relative to a middle shaft 5, and the planet wheels 3 are respectively in transmission with a sun wheel 4 and an outer ring 2 and also play a role in speed change when being used as an output element; the planet wheels 1 are used as special variable-speed transmission devices, are uniformly distributed in the circumferential direction, are arranged on the base 6 in a fixed-shaft rotating mode and are respectively in transmission with the sun wheel 4 and the outer ring 2; each unit planet wheel 1 or planet wheel 3 can be a single-layer structure, can also be a ladder structure with a speed change function, can be a single-shaft structure, and can also be a composite structure which is formed by combining a plurality of parallel-shaft planet wheels and can change direction or speed for many times; the outer ring 2 can be of a single-layer structure or a stepped structure and can be respectively in transmission with the planet wheel 1 and the planet wheel 3 at different radius positions; when the central shaft 5 drives the sun gear 4 to rotate to drive the planet gears 3, power is simultaneously shunted to the outer ring 2 through the planet gears 1 to enable the planet gears 3 to have active rotating speed, the sun gear 4 and the outer ring 2 simultaneously and actively drive the planet gears 3 from the same direction or the opposite direction, and the rotation speed vectors of the sun gear 4 and the outer ring 2 are converted into revolution speed vectors of the rotation centers of the planet gears 3, namely the rotation speed vectors of the planet carrier 7, and the revolution speed vectors are used as output results. When the angular speed directions of the sun gear 4 and the outer ring 2 are the same in size, namely the relative speed is zero, the reduction ratio is 1, the ratio of the absolute values of the angular speeds of the sun gear 4 and the outer ring 2 is closer to the inverse ratio of the teeth numbers of the sun gear 4 and the outer ring 2, the absolute value of the reduction ratio is larger, when the ratio of the absolute values of the angular speeds of the sun gear 4 and the outer ring 2 is equal to the inverse ratio of the teeth numbers of the sun gear 4 and the outer ring 2, the linear speeds of the radial positions of the transmission of the planet gear 3 are opposite in size, the output rotating speed is zero, and the reduction ratio is. The power input, the power split and the power combination can also adopt the mode that the power is input from the outer ring 2, the outer ring 2 drives the sun wheel 4 through the planet wheel 1, the outer ring 2 and the sun wheel 4 drive the planet wheel 3 in parallel, or the structure is adjusted to be that the power is directly divided into two paths to respectively reach the planet wheel 3 through the sun wheel 4 and the outer ring 2, and the link that the sun wheel 4 and the outer ring 2 are connected in series is not available in the whole process.

The utility model discloses a first rotor is direct drive output element not, but participates in the drive second rotor and makes it have initiative rotational speed for output element, by second rotor individual drive output element, the output rotational speed of the synthetic output element of rotation speed and revolution speed of oneself. Referring to fig. 7 and 8, the sun gear 19 is a first rotor, the planet gears 11 are second rotors, and the sun gear 19 is connected with power and drives the planet gears 11 to drive the outer ring 13 as an output element; the sun gear 19 is fixed on a middle shaft 20 serving as a power input shaft and can actively drive the planet gear 11 to rotate; more than two planet wheels 11 are rotatably arranged on a planet carrier 14, the planet carrier 14 is fixedly connected with a sun wheel 17 and can rotate relative to a middle shaft 20 together, and the middle shaft 20 is fixedly connected with the sun wheel 16; the speed change ring 15, the sun wheel 16 and the sun wheel 17, as well as the planet wheel 12 and the planet wheel 21 which are arranged on the base 18 in a fixed-shaft rotating manner form a speed change device; the speed changing ring 15 is of a single-layer structure or a stepped structure and is respectively driven by the planet wheels 12 and the planet wheels 21 at different axial positions; one path of power of the middle shaft 20 drives the planetary gear 11 to rotate through the sun gear 19, the other path of power sequentially passes through the sun gear 16, the planetary gear 12, the speed change ring 15, the planetary gear 21 and the sun gear 17 to change speed, and finally the planetary gear 11 is driven to revolve through the planet carrier 14; the outer ring 13 is driven by the planet wheel 11, the revolution speed and the rotation speed of the planet wheel 11 jointly determine the rotation speed of the outer ring 13, when the revolution angular speed of the planet wheel 11 is the same as the rotation angular speed of the sun wheel 19 in direction and equal in size, the reduction ratio is 1, the absolute value of the ratio of the revolution angular speed of the planet wheel 11 to the rotation angular speed of the sun wheel 19 is closer to the gear ratio of the sun wheel 19 to the outer ring 13, the absolute value of the reduction ratio is larger, and when the absolute value of the ratio of the revolution angular speed of the planet wheel 11 to the rotation angular speed of the sun wheel 19 is equal to the gear ratio of the sun wheel 19 to the outer ring 13, the reduction ratio is infinite or infinitesimal. In the embodiment of fig. 7 and 8, the moving planetary gear 11 as the second rotor obtains the revolution speed through the driving of the speed changing device, but the structure scheme shown in fig. 9 can also be adopted, the moving planetary gear 31 as the second rotor obtains the rotation speed through the driving of the speed changing device-the sun gear 39 is the first rotor, the planetary gear 31 is the second rotor, and the outer ring 33 is the output element; the planet wheels 32 and 41 are fixed-shaft rotationally mounted on the base 38 and are respectively driven with the movable speed change ring 35 at different axial positions, and the speed change ring 35 can be of a single-layer structure or a stepped structure with different driving radiuses; the planet carrier 34 of the planet wheel 31 is fixed on the middle shaft 40 and can drive the planet wheel 31 which is driven by the outer ring 33 to revolve; the sun wheel 39 is rotationally connected with the middle shaft 40 and is respectively driven with the planet wheel 31 and the planet wheel 41 at different axial positions; the planet wheel 32 is in transmission with a sun wheel 36 fixedly connected with a middle shaft 40; the power is input from the middle shaft 40 and then divided into two paths, one path drives the planet wheel 31 to revolve through the planet carrier 34, the other path drives the planet wheel 31 to rotate after speed change is carried out through the sun wheel 36, the planet wheel 32, the speed change ring 35, the planet wheel 41 and the sun wheel 39, and the planet wheel 31 drives the outer ring 33 to rotate by means of the revolution and rotation speed of the planet wheel 31. The power transmission direction of the series structure can also be reversed, the power is input from the outer ring and output from the sun gear after being transmitted by the planet gear, and the connection mode of the speed change device needs to be correspondingly adjusted.

The utility model discloses have preceding stage speed reduction structure, make first rotor and second rotor work under lower rotational speed. In order to enable the first rotor and the second rotor to work at a rotating speed lower than the initial input rotating speed, an embodiment with a preceding-stage speed reducing structure is adopted as shown in fig. 6, a sun wheel 8 fixedly connected with a middle shaft 5 and driven by a planet wheel 1 is added on the basis of the embodiment of fig. 4, meanwhile, the connection and driving modes of other components are also partially adjusted, namely the sun wheel 4 is rotationally connected with the middle shaft 5, the rotating speed input from the middle shaft 5 sequentially passes through the sun wheel 8 and the planet wheel 1 and then is further transmitted to an outer ring 2 and the sun wheel 4 respectively, a speed reducing link is arranged on the combination of the sun wheel 8 and the planet wheel 1, the combination of the planet wheel 1 and the outer ring 2 and the combination of the planet wheel 1 and the sun wheel 4 can also be arranged, or the three combinations have a speed reducing function, and the rotating speed is reduced in advance and then transmitted to the first rotor and the. The structure types of the front stage speed reducing mechanism include but are not limited to a planetary structure, and the transmission modes include but are not limited to gear transmission, flexible transmission, friction transmission and magnetic transmission.

The utility model discloses have speed change gear, first rotor or second rotor have initiative rotational speed for output element through its connection power, like the planet wheel 1 of fig. 5, be used for changing the size or the direction of upper reaches component speed as special speed change gear, can be single-layer structure, also can be the stair structure that has the variable speed function, can be single-shaft structure, also can be the composite construction of a plurality of parallel shaft planet wheel combinations and forming diversion or variable speed many times, rotate at circumference equipartition and dead axle and install on base 6, play transmission and variable speed effect with sun gear 4 and 2 transmissions of outer loop respectively, make outer loop 2 as the second rotor have suitable initiative rotational speed for planet wheel 3 as output element. The sun gear 16, the planetary gears 12, the shift ring 15, the planetary gears 21 and the sun gear 17 in fig. 8, and the sun gear 36, the planetary gears 32, the shift ring 35 and the planetary gears 41 in fig. 9 also have the shifting function.

The utility model discloses a first rotor and second rotor are driven by independent power device separately respectively, can change output element's rotational speed through the rotational speed of the different power device input of direct adjustment. In the embodiment shown in fig. 4, the sun gear 4 and the outer ring 2 may be driven by the middle shaft 5 to split the input power and may also be driven by independently controllable power devices, which may be of types including but not limited to motors, engines, external devices, or components of the system itself.

The utility model discloses a same first rotor, second rotor or output element's unit has the mounted position of two or more differences or the same kind structure of the same but parameter difference of function, can obtain different output results through selecting different operating position or functional parameter. Taking fig. 10 as an example, the planet wheel 11 as the second rotor is of a stepped structure, and can drive the outer rings 13A, 13B and 13C with different diameters as output elements at different radial positions or orientations, respectively, and different rotating speeds can be output by selecting different working positions.

The utility model discloses have controlling device, can be used for controlling output element's output rotational speed. Fig. 10 shows a mechanical control embodiment, in which the end surfaces of the outer rings 13A, 13B and 13C as output elements are provided with raised stoppers 22, which may also be grooves, pins, pin holes, magnets or continuous tooth shapes, and the load elements driven by the output elements are correspondingly provided with axially movable stoppers, grooves, pins, pin holes, magnets or tooth rings as locking devices at the same diameter positions, and there are technical types including but not limited to cables, push rods, push rings, lead screws, electromagnetic, pneumatic or hydraulic control devices to axially move the locking devices to be locked with or unlocked from the outer rings 13A, 13B or 13C, thereby controlling the output rotation speed. The embodiment that the power device directly drives the rotor is provided with a potentiometer or an accelerator controller to control the output rotating speed, and is manually controlled or is provided with an automatic control system to control.

The utility model discloses have and have hollow shaft or hollow shaft power device. In order to save axial space or facilitate structural design in the aspects of transmission, control, wiring and the like, a rotating shaft of the power device adopts a hollow structure and is coaxially mounted with a central shaft of the ternary transmission component, and the ternary transmission component can be surrounded in the middle. In the embodiment where the power plant is a hollow shaft motor, the motor stator, motor rotor and hollow shaft are nested radially to enclose the variator's tertiary assembly in the middle.

The utility model discloses have birotor structure motor, the rotational speed of two rotors of motor can independent control, is arranged in driving first rotor and the second rotor among the ternary drive structure respectively. Referring to fig. 11, the motor of the system is a radial multilayer nested structure, and the central shaft 26 of the ternary component is used as the shaft or is coaxially installed with the shaft, and the system is provided with an inner layer of motor rotor 24 and an outer layer of motor rotor 25, and simultaneously forms a motor unit with the motor stator 23 respectively, and the motor unit can independently rotate and respectively drive the first rotor and the second rotor in the ternary transmission structure. The speed regulating device can respectively control the rotating speed of the motor rotor 24 and the rotating speed of the motor rotor 25, and the output rotating speed of the speed changer can be continuously regulated by continuously regulating the rotating speeds of different rotors. The radial arrangement order of the motor rotors 24 and 25 and the motor stator 23 is not limited to that shown in the drawings, and the motor rotors 24 and 25 may have motor stators respectively independently associated therewith.

Claims (10)

1. Binary initiative derailleur, including as three kinds of subassemblies of rotor, stator and output element respectively in the coaxial reduction gear of ternary drive structure to reach the axis as the sharing axle, its characterized in that: the component as the stator in the three-element transmission structure coaxial reducer is not fixedly installed and has a driving rotating speed relative to the output element, so that a two-element driving and one-element driven three-element transmission structure is formed, wherein the original rotor is a first rotor, the original stator is a second rotor, and the output result of the output element is determined by the combined action of the first rotor and the second rotor.

2. The binary active transmission of claim 1 wherein the first and second rotors drive the output member in parallel, combining the rotational speeds of the two rotors to the rotational speed of the output member.

3. The binary active transmission of claim 1 wherein the first rotor does not directly drive the output member but participates in driving the second rotor to have an active speed relative to the output member, the output member being driven by the second rotor alone, combining its own rotation speed and revolution speed into the output speed of the output member.

4. A binary active transmission as claimed in claim 1, 2 or 3 characterised by a pre-stage reduction arrangement to operate the first and second rotors at a lower speed than the initial input speed.

5. The binary active transmission of claim 4, characterized by a transmission through which the first or second rotor is connected to power to have an active speed relative to the output member.

6. A binary active transmission according to claim 1, 2 or 3 characterised in that the first and second rotors are each driven by separate power units, the speed of rotation of the output member being variable by direct adjustment of the speed of rotation of the inputs to the different power units.

7. A twin drive transmission as defined in claim 6 in which the same unit of first rotor, second rotor or output member has more than two different mounting positions or similar structures of the same function but different parameters, different output results being obtainable by selecting different operating positions or functional parameters.

8. The binary active transmission according to claim 1, 2, 3, 5 or 7, characterized by having a control device operable to control the output speed of the output member.

9. The binary active transmission according to claim 8, characterized by a hollow shaft or a hollow shaft power plant.

10. The binary active transmission according to claim 1, 2, 3, 7 or 9, characterized by a motor with a double rotor structure, the rotational speeds of the two rotors of which can be independently controlled, for driving the first rotor and the second rotor, respectively, in a triple drive structure.

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