Transmission device, electric vehicle including said device and method for driving said device

Abstract

To provide: a transmission device which can prolong a use life, and has a dual power source which is assured in operation accuracy; and a method for driving the device.SOLUTION: A transmission device includes a planetary gear assembly which is driven by a dual power source, and the dual power source drives an input shaft (14) which is connected to a sun gear (3), and also drives the sun gear (3) so as to rotate in a first direction with respect to its own rotation axial line by the input shaft (14). The dual power source is connected to a rotation inner tooth ring (4), and drives the rotation inner tooth ring (4) so as to rotate in a second direction opposite to the first direction with respect to the rotation axial line. At this time, a planetary gear (5) rotates in the second direction with respect to the rotation axial line, and in the planetary gear (5), a rotation motion direction around the input shaft is decided by a linear speed V1 of a pitch motion of the rotation inner tooth ring (4) and a linear speed V2 of a pitch motion of the sun gear (3).SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present disclosure relates to a transmission arrangement, and more particularly to a transmission arrangement having dual power sources. [Background technology]

[0002] A key issue with a planetary gear transmission is that the gaps (also called backlash) that occur when the teeth mesh during operation cannot be eliminated. Especially when the gears frequently change direction of motion, the backlash causes vibration, noise, wear, and other phenomena, which shorten the service life of the transmission and cause problems such as inaccurate operation. Some high-precision, compact, large-torque, advanced products with frequently changing output direction, such as RV reducers at each motion joint in industrial robot structures, have very high requirements for the material selection and manufacturing accuracy of the RV reducer in order to achieve high positioning accuracy and a very long service life of the RV reducer, which inevitably leads to an increase in manufacturing costs. However, no matter how high the processing accuracy is, it is not possible to completely eliminate the gaps between the teeth when the teeth mesh (see Figure 3). For example, when the planetary gear frequently changes direction of motion, the tooth surface of the fixed internal tooth ring is frequently subjected to the impact of two forces in different directions, and no matter how small the gaps between the gears are, the tooth surface gaps between the teeth are also frequently changed. As the gears wear, the tooth gaps between the teeth increase at an accelerating rate, rendering the RV reducer ineffective.

[0003] As is well known, FM motors are currently widely used in electric vehicles, and FM motors have high efficiency during high-speed driving, about 94%, but low efficiency during low-speed driving, about 70% or less (see Figure 4). However, when an electric vehicle is traveling, it needs to be accelerated and decelerated frequently in response to changes in road conditions, and a lot of electrical energy is wasted in the process of going from low-speed driving to high-speed driving, and this wasted electrical energy is converted into heat in the electric vehicle and flows into the cooling water.

[0004] In addition, the frequency conversion motor of an electric vehicle can be overloaded when starting the vehicle or climbing a slope under load, and the peak value of the motor output can reach more than twice the rated output. The above two issues are the key to preventing the driving of electric vehicles from reaching the designed mileage. Summary of the Invention [Means for solving the problem]

[0005] The present disclosure has been made to address the shortcomings of the prior art, and provides a transmission device having a dual power source, the transmission device including a planetary gear assembly driven by the dual power source, the planetary gear assembly including a sun gear, a rotating internal toothed ring, and a planetary gear meshed between the sun gear and the rotating internal toothed ring, the dual power source including an input shaft connected to the sun gear, the input shaft driving the sun gear to rotate in a first direction relative to its own rotation axis, the dual power source including an input shaft connected to the rotating internal toothed ring, and driving the rotating internally toothed ring to rotate in a second direction opposite to the first direction about its own rotation axis, wherein the planetary gear rotates in the second direction about its own rotation axis (for example, rotated by the drive of the dual power sources using a synchronizer to ensure that the rotating internally toothed ring and the planetary gear have the same rotation direction), and the direction of rotational motion of the planetary gear around the input shaft is determined by the linear velocity V1 of the pitch motion of the rotating internally toothed ring and the linear velocity V2 of the pitch motion of the sun gear.

[0006] According to one aspect of the present disclosure, the dual power source includes a first power source arranged to drive the sun gear through the input shaft and a second power source arranged to drive the rotatable internal tooth ring.

[0007] According to the above aspects of the present disclosure, the planetary gears are mounted on a planetary gear cage having an output shaft mounted thereon, the sun gear is coaxially mounted on the rotating internal tooth ring, and the output shaft is coaxially mounted on the input shaft.

[0008] According to each of the above aspects of the present disclosure, when the first direction is the clockwise direction, the second direction is the counterclockwise direction, and when the first direction is the counterclockwise direction, the second direction is the clockwise direction.

[0009] According to each of the above aspects of the present disclosure, when V1 > V2, the rotational movement direction of the planetary gear and the planetary gear cage around the input shaft is opposite to the rotational direction of the input shaft, the rotational direction of the output shaft itself is opposite to the rotational direction of the input shaft, and the tooth surface gap between the tooth surface of the planetary gear and the tooth surface of the rotating internal tooth ring meshing therewith is located only on one side of the teeth of the planetary gear.

[0010] When V1 < V2, the rotational movement direction of the planetary gear and the planetary gear cage around the input shaft is the same as the rotational direction of the input shaft, the rotational direction of the output shaft itself is the same as the rotational direction of the input shaft, and the tooth surface gap between the tooth surface of the planetary gear and the tooth surface of the rotating internal tooth ring meshing therewith is held on the one side of the teeth of the planetary gear.

[0011] When V1 = V2, the rotational speed of the planetary gear and the planetary gear cage around the input shaft is zero, and the rotational speed of the output shaft itself is zero.

[0012] According to each of the above aspects of the present disclosure, a parallel gear is installed on the rotating internal tooth ring and is driven by the second power source. Drive The internal tooth ring is driven by the gear meshing with the parallel gear.

[0013] According to each of the above aspects of the present disclosure, a sun gear front gear is installed on the input shaft and is driven by the first power source. Sun gear drive The sun gear is driven by the gear meshing with the sun gear front gear.

[0014] According to the above aspects of the present disclosure, the first power source has a constant power output and the second power source has an adjustable speed power output, and an electronic control device is connected to the first power source by an input control line and processes errors such as slowdown or instability in rotation speed when the first power source has a different power.

[0015] According to the above aspects of the present disclosure, when the second power source rolls with the rotating internal toothed ring, motion data of the rotating internal toothed ring is transmitted to the electronic control device via a real-time data collection line connected to the second power source, and the electronic control device processes an internal program or an external command to control and adjust the power output of the second power source power source via the real-time data collection line, so that the output shaft can reach various speeds required under different working conditions.

[0016] According to the above aspects of the present disclosure, the first power source has an adjustable speed power output, and the electronic controller controls the power output of the first power source via an input control line.

[0017] According to the above aspects of the present disclosure, the first power source and the second power source are controllable, speed adjustable power machines.

[0018] According to the above aspects of the present disclosure, the controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

[0019] According to the present disclosure, there is further provided an electric vehicle including a transmission device having a dual power source as described in each of the above aspects.

[0020] The present disclosure further provides a driving method for driving the transmission device described above, the transmission device including a dual power source driving a planetary gear assembly, the planetary gear assembly including a sun gear, a rotating internally toothed ring, and a planetary gear meshing between the sun gear and the rotating internally toothed ring, the dual power source including an input shaft connected to the sun gear and arranged to drive the sun gear to rotate in a first direction relative to its own rotation axis by the input shaft, the dual power source being connected to the rotating internally toothed ring and driving the rotating internally toothed ring to rotate in a second direction opposite to the first direction relative to its own rotation axis, wherein the planetary gear rotates in the second direction relative to its own rotation axis, and a direction of rotational movement of the planetary gear around the input shaft is determined by a linear velocity V1 of a pitch motion of the rotating internally toothed ring and a linear velocity V2 of a pitch motion of the sun gear.

[0021] According to one aspect of the driving method described above, the dual power source includes a first power source and a second power source, the first power source being arranged to drive the sun gear by the input shaft, and the second power source being arranged to drive the rotating internal toothed ring.

[0022] According to each aspect of the driving method described above, the planetary gears are mounted on a planetary gear cage, an output shaft is installed on the planetary gear cage, the sun gear is coaxially installed on the rotating internal tooth ring, and the output shaft is coaxially installed on the input shaft.

[0023] According to each aspect of the driving method described above, when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, the second direction is a clockwise direction.

[0024] According to each aspect of the driving method described above, when V1 > V2, the rotational movement direction of the planetary gear and the planetary gear cage around the input shaft is opposite to the rotational direction of the input shaft, the rotational direction of the output shaft itself is opposite to the rotational direction of the input shaft, and the tooth surface gap between the tooth surface of the planetary gear and the tooth surface of the rotating internal tooth ring meshing therewith is located only on one side of the teeth of the planetary gear.

[0025] When V1 < V2, the rotational movement direction of the planetary gear and the planetary gear cage around the input shaft is the same as the rotational direction of the input shaft, the rotational direction of the output shaft itself is the same as the rotational direction of the input shaft, and the tooth surface gap between the tooth surface of the planetary gear and the tooth surface of the rotating internal tooth ring meshing therewith is held on the one side of the teeth of the planetary gear.

[0026] When V1 = V2, the rotational speed of the planetary gear and the planetary gear cage around the input shaft is zero, and the rotational speed of the output shaft itself is zero.

[0027] According to each aspect of the driving method described above, the first power source is installed to output a constant power, the second power source is installed to output a power with adjustable speed, and an electronic control device is installed to process the rotational speed reduction or unstable error of the first power source when it has different powers through an input control line.

[0028] According to each aspect of the driving method described above, the second power source rolls with the rotating internal tooth ring, and the movement data of the rotating internal tooth ring is transmitted to the electronic control device through a real-time data acquisition line connected to the second power source. The electronic control device controls and adjusts the power output of the second power source through the real-time data acquisition line by processing an internal program or an external command, so that the output shaft reaches various speeds required in the working condition.

[0029] According to each aspect of the driving method described above, the first power source is installed to output a power with adjustable speed, and the electronic control device controls the power output of the first power source through an input control line.

[0030] According to each aspect of the driving method described above, the first power source and the second power source are configured as a controllable, speed-adjustable power machine.

[0031] According to each aspect of the drive method described above, the controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

[0032] According to each aspect of the above-described driving method, a parallel gear is installed on the rotating internally toothed ring, and the internally toothed ring is driven by the second power source. Drive A gear meshes with the parallel gears to drive the rotating internally toothed ring.

[0033] According to each aspect of the driving method described above, a front sun gear is installed on the input shaft and driven by the first power source. Sun gear drive A gear meshes with the front sun gear to drive the sun gear.

[0034] One of the features of the transmission device with dual power sources according to the present disclosure is that it applies a mechatronics composite structure to fundamentally resolve the key issue of the inability to eliminate the gap (also called backlash) between the teeth of the planetary gear and the teeth of the internal tooth ring when the planetary gear transmission is in operation, particularly the vibration, noise, wear and other defects caused by the impact between the teeth due to the backlash when the gears frequently change direction of motion, thereby extending the service life of the transmission and ensuring the operation precision.

[0035] The transmission device with dual power sources according to the present disclosure may be applied to advanced products with high precision, small size, large torque, and frequent output direction changes, such as industrial robot structures with RV reducers installed at each moving joint. The present disclosure realizes high positioning precision and very long service life of the RV reducer. In particular, when the planetary gear frequently changes the direction of motion, the tooth surface of the rotating inner tooth ring is not frequently subjected to the impact of two forces in different directions, and the backlash between the teeth is not frequently changed. In addition, even if the gear is worn out, the backlash between the teeth is not accelerated and expanded by the speed adjustment control of the electronic control device, so that the RV reducer is prevented from being disabled.

[0036] In the dual power transmission device of the present disclosure, when the sun gear, planetary gear, and rotating inner tooth ring keep their own rotation direction unchanged, the output shaft can conveniently rotate forward or backward (as shown in FIG. 2), but the backlash between the teeth remains only on one side, and the direction of the force between the teeth does not change, so the backlash between the teeth does not change due to frequent changes in the direction of the output shaft. Since the teeth are tightly meshed only on one side during operation, no impact force is generated due to the change in backlash. Therefore, the positioning accuracy of the transmission device of the present disclosure is higher and the service life is longer. Moreover, even if there is a large wear between the teeth and the backlash between the teeth is increased, the other side of the teeth is tightly meshed, so that the perfect positioning accuracy and service effect can be achieved by the correction control of the electronic control device.

[0037] The transmission device with dual power sources according to the present disclosure is also applied to the transmission device of a battery electric vehicle, and the two electric motors can run completely within the maximum efficiency speed range of the frequency conversion motor during frequency conversion. In addition, the output shaft can be zero rotation speed or forward / reverse stepless speed change. It can also generate the required torque several tens of times more than that of a conventional battery electric vehicle. If a conventional EVB320-140-180 frequency conversion motor is adopted, its rated power is 30KW, its peak power is 60KW, but its peak torque is only 180N·M. When a battery electric vehicle runs, the speed is frequently changed according to the road conditions, and the battery electric vehicle needs to repeatedly accelerate from static to dynamic, and also needs to climb different slopes and bear different loads, so the frequency conversion motor adopted by the conventional battery electric vehicle needs a large reserve power and a low efficiency region where the motor runs at less than 70% for a long time.

[0038] However, under the condition of driving in the same road conditions, according to the present disclosure, two dual power transmission devices of 10KW each may be adopted, the total power is only 20KW, and the maximum torque is 9000N·M to 10000N·M (as shown in FIG. 5), and the two motors continue to run in the high efficiency range of 95%. The large torque of more than 9000N·M can fully meet the driving of the battery electric vehicle in all road conditions.

[0039] Comparing a conventional frequency conversion motor with a peak power of 60KW and a peak torque of 180N·M with the dual power transmission device of the present disclosure with a power of 20KW and a torque of up to 9000N·M or more, it can be concluded that a motor with a lower power can be selected and arranged when traveling under the same road conditions, since the transmission device of the present disclosure can keep the motor running within a high-efficiency operating speed range and avoid the low-efficiency area of ​​low-speed operation of frequency conversion for a battery electric vehicle based on the same road conditions. Therefore, if the dual power planetary gear transmission device of the present disclosure is adopted for a conventional battery electric vehicle, it can be highly adapted to the operating conditions of the vehicle and can greatly extend the driving distance. The dual power source in the present disclosure may be a controllable, speed-adjustable internal combustion engine or other power machine with a higher power when a transmission device with a higher power and higher torque output is required. The present disclosure may be applied to other mechanical products that require forward and reverse rotation speed change. [Brief description of the drawings]

[0040] [Figure 1] FIG. 1 is a schematic diagram illustrating a transmission apparatus having dual power sources according to the present disclosure. [Diagram 2] FIG. 2 illustrates the backlash between the teeth of the rotating internal toothed ring and the teeth of the planetary gears when a sun gear according to the present disclosure is rotated in a clockwise direction. [Diagram 3] FIG. 3 shows that backlash exists in a transmission having a conventional planetary gear assembly in the prior art. [Figure 4] Figure 4 shows the torque diagram of a conventional FM motor. [Diagram 5] FIG. 5 illustrates a torque diagram for a dual power source transmission arrangement according to the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0041] Hereinafter, embodiments of the present disclosure will be described in detail with reference to the drawings.

[0042] FIG. 1 shows a schematic diagram of a transmission apparatus having a dual power source according to one embodiment of the present disclosure, the transmission apparatus having a dual power source includes a planetary gear assembly driven by the dual power sources.

[0043] The planetary gear assembly includes a sun gear 3, a rotating internally toothed ring 4, and planetary gears 5 meshing between the sun gear 3 and the rotating internally toothed ring 4.

[0044] The dual power source includes an input shaft 14 connected to the sun gear 3, a first power source 1, and a second power source 2, and is arranged to drive the sun gear 3 to rotate in a first direction about its own rotation axis by the input shaft 14, and the dual power source is connected to the rotating internally toothed ring 4 and drives the rotating internally toothed ring 4 to rotate in a second direction opposite to the first direction about its own rotation axis, at which time the planetary gears 5 rotate in the second direction about their own rotation axis, and the direction of the rotational movement of the planetary gears 5 around the input shaft 14 is determined by the linear velocity V1 of the pitch motion of the rotating internally toothed ring 4 and the linear velocity V2 of the pitch motion of the sun gear 3.

[0045] According to one embodiment of the present disclosure, the first power source 1 is arranged to drive the sun gear 3 via the input shaft 14, and the second power source 2 is arranged to drive the rotating internal toothed ring 4.

[0046] According to the above-mentioned embodiments of the present disclosure, the planetary gears 5 are mounted on a planetary gear cage 6 having an output shaft 7 mounted thereon, the sun gear 3 is coaxially mounted on the rotating internal toothed ring 4, and the output shaft 7 is coaxially mounted on the input shaft 14.

[0047] According to each of the above-described embodiments of the present disclosure, when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, the second direction is a clockwise direction.

[0048] According to the above-mentioned embodiments of the present disclosure, when V1>V2, the direction of rotational movement of the planetary gears 5 and the planetary gear cage 6 around the input shaft 14 is opposite to the direction of rotation of the input shaft 14, the direction of rotation of the output shaft 7 itself is opposite to the direction of rotation of the input shaft 14, and the tooth surface gap (also called backlash) between the tooth surface of the planetary gears 5 and the tooth surface 16 of the rotating internal toothed ring 4 meshing therewith is located only on one side of the teeth of the planetary gears 5. For example, as shown in FIG. 2, when the input shaft 14 drives the sun gear 3 to rotate in a clockwise direction about its own rotation axis, the output shaft 7 itself rotates in a counterclockwise direction, and the tooth surface gap is located only on the right side of the teeth of the planetary gears 5, but the left side of the teeth of the planetary gears 5 is contacted with the tooth surface of the rotating internal toothed ring 4. It will be understood by those skilled in the art that when the input shaft 14 drives the sun gear 3 to rotate in a counterclockwise direction about its own axis of rotation (not shown), the output shaft 7 itself rotates in a clockwise direction and the tooth flank gap is located only on the left side of the teeth of the planetary gears 5, but the right side of the teeth of the planetary gears 5 contact the tooth flank of the rotating internal toothed ring 4.

[0049] When V1 < V2, the rotational movement directions of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 are the same as the rotational direction of the input shaft 14, the rotational direction of the output shaft 7 itself is the same as the rotational direction of the input shaft 14, and the tooth surface clearance between the tooth surface of the planetary gear 5 and the tooth surface of the rotating internal gear ring 4 meshing therewith is held on the one side of the teeth of the planetary gear 5. For example, as shown in FIG. 2, when the input shaft 14 drives the sun gear 3 to rotate in the clockwise direction with respect to its own rotation axis, the output shaft 7 itself rotates in the clockwise direction, the tooth surface clearance is still located only on the right side of the teeth of the planetary gear 5, and the left side of the teeth of the planetary gear 5 is still in contact with the tooth surface of the rotating internal gear ring 4. When the input shaft 14 drives the sun gear 3 to rotate in the counterclockwise direction with respect to its own rotation axis (not shown), the output shaft 7 itself rotates in the counterclockwise direction, the tooth surface clearance is still located only on the left side of the teeth of the planetary gear 5, and it is understandable to those skilled in the art that the right side of the teeth of the planetary gear 5 is still in contact with the tooth surface of the rotating internal gear ring 4.

[0050] When V1 = V2, the rotational speeds of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 are zero, and the rotational speed of the output shaft 7 itself is zero.

[0051] According to each aspect of the present disclosure, a parallel gear 8 is installed on the rotating internal gear ring 4 and is an internal gear ring driven by the second power source 2 Drive The internal gear 9 meshes with the parallel gear 8, whereby the rotating internal gear ring 4 is driven.

[0052] According to each embodiment of the present disclosure, a sun gear front gear 10 is installed on the input shaft 14 and is driven by the first power source 1 Sun gear drive The gear 15 meshes with the sun gear front gear 10, whereby the sun gear 3 is driven.

[0053] Internal gear ring Drive The internal gear 9 is installed to mesh with the parallel gear 8, and Sun gear driveBy arranging the gear 15 and the front sun gear 10 to mesh with each other, more space can be provided to accommodate the first and second power sources, especially when a large-volume, high-power power source is required.

[0054] According to the above-mentioned embodiments of the present disclosure, the first power source 1 has a constant power output, and the second power source 2 has an adjustable speed power output, and the electronic control device 11 processes the error of the rotation speed reduction or instability when the first power source 1 has a different power through the input control line 13.

[0055] According to the above-mentioned embodiments of the present disclosure, when the second power source 2 rolls with the rotating internal toothed ring 4, the motion data of the rotating internal toothed ring 4 is transmitted to the electronic control device 11 through a real-time data collection line 12 connected to the second power source 2, and the electronic control device 11 processes an internal program or an external command to control and adjust the power output of the second power source 2 through the real-time data collection line 12, so that the output shaft 7 can reach various speeds required under different working conditions.

[0056] According to the above embodiments of the present disclosure, the first power source 1 is a speed adjustable power output, and the electronic controller 11 controls the power output of the first power source 1 via an input control line 13 .

[0057] The correction control of the electronic control device 11 helps to maintain the tooth surface gap between the tooth surface of the planetary gear 5 and the tooth surface of the rotating internal tooth ring 4 that meshes with it, located only on one side of the teeth of the planetary gear 5.

[0058] According to the above embodiments of the present disclosure, the first power source and the second power source are controllable, speed adjustable power machines.

[0059] According to the above embodiments of the present disclosure, the controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

[0060] In the dual power transmission device of the present disclosure, when the sun gear 3, the planetary gear 5, and the rotating inner tooth ring 4 do not change their own rotation direction, the output shaft 7 can conveniently rotate forward or backward (as shown in FIG. 2), but the backlash between the teeth remains only on one side, and the direction of the force between the teeth does not change, so the backlash between the teeth does not change due to frequent changes in the direction of the output shaft 7. Since the teeth are tightly meshed only on one side during operation, no impact force is generated due to the change in backlash. Therefore, the positioning accuracy of the transmission device of the present disclosure is higher and the service life is longer. Moreover, even if there is a large wear between the teeth and the backlash between the teeth is increased, the other side of the teeth is tightly meshed, so that the electronic control device 11 can achieve perfect positioning accuracy and service effect by the correction control.

[0061] The present disclosure further provides an electric vehicle including a transmission device with dual power sources as described in each of the above embodiments.

[0062] The transmission device with dual power sources according to the present disclosure is applied to the transmission of a battery electric vehicle, and the two electric motors can operate completely within the speed range of the most efficient frequency conversion motor during frequency conversion. In addition, the output shaft 7 can be zero rotation speed or forward / reverse infinitely variable speed. In addition, it can generate the required torque several tens of times more than that of a conventional battery electric vehicle.

[0063] If a conventional EVB320-140-180 frequency conversion motor is used, its rated power is 30KW, its peak power is 60KW, but its peak torque is only 180N·M. When a battery electric vehicle runs, its speed changes frequently according to road conditions, and the battery electric vehicle needs to repeatedly accelerate from static to dynamic, and also needs to climb different slopes and bear different loads, so the frequency conversion motor used by the conventional battery electric vehicle needs a large reserve power and a low-efficiency region where the motor runs at less than 70% for a long time.

[0064] However, under the condition of driving in the same road conditions, according to the present disclosure, two dual power transmission devices of 10KW each may be adopted, the total power is only 20KW, and the maximum torque is 9000N·M to 10000N·M (as shown in FIG. 5), and the two motors continue to run in the high efficiency range of 95%. The large torque of more than 9000N·M can fully meet the driving of the battery electric vehicle in all road conditions.

[0065] Comparing a conventional frequency conversion motor with a peak power of 60KW and a peak torque of 180N·M with the dual power transmission device of the present disclosure with a power of 20KW and a torque of up to 9000N·M or more, it can be concluded that a motor with a lower power can be selected and arranged when traveling under the same road conditions, since the transmission device of the present disclosure can keep the motor running within a high-efficiency operating speed range and avoid the low-efficiency area of ​​low-speed operation of frequency conversion for a battery electric vehicle based on the same road conditions. Therefore, if the dual power planetary gear transmission device of the present disclosure is adopted for a conventional battery electric vehicle, it can be highly adapted to the operating conditions of the vehicle and can greatly extend the driving distance. The dual power source in the present disclosure may be a controllable, speed-adjustable internal combustion engine or other power machine with a higher power when a transmission device with a higher power and higher torque output is required. The present disclosure may be applied to other mechanical products that require forward and reverse rotation speed change.

[0066] The present disclosure further provides a driving method for driving the transmission device described above, the transmission device including a dual power source driving a planetary gear assembly, the planetary gear assembly including a sun gear 3, a rotating internally toothed ring 4, and a planetary gear 5 meshing between the sun gear 3 and the rotating internally toothed ring 4, the dual power source including an input shaft 14 connected to the sun gear 3 and arranged to drive the sun gear 3 to rotate in a first direction relative to its own rotation axis by the input shaft 14, the dual power source being connected to the rotating internally toothed ring 4 and driving the rotating internally toothed ring 4 to rotate in a second direction opposite to the first direction relative to its own rotation axis, in which the planetary gear 5 rotates in the second direction relative to its own rotation axis, and the direction of the rotational movement of the planetary gear 5 around the input shaft 14 is determined by a linear velocity V1 of the pitch motion of the rotating internally toothed ring 4 and a linear velocity V2 of the pitch motion of the sun gear 3.

[0067] According to one embodiment of the driving method described above, the dual power source includes a first power source 1 and a second power source 2, the first power source 1 is arranged to drive the sun gear 3 via the input shaft 14, and the second power source 2 is arranged to drive the rotating internal toothed ring 4.

[0068] According to each embodiment of the driving method described above, the planetary gears 5 are mounted in a planetary gear cage 6, an output shaft 7 is installed in the planetary gear cage 6, the sun gear 3 is coaxially installed in the rotating internal tooth ring 4, and the output shaft 7 is coaxially installed in the input shaft 14.

[0069] According to each embodiment of the driving method described above, when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, the second direction is a clockwise direction.

[0070] According to each embodiment of the driving method described above, when V1 > V2, the rotational movement directions of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 are opposite to the rotational direction of the input shaft 14, the rotational direction of the output shaft 7 itself is opposite to the rotational direction of the input shaft 14, and the tooth surface gap between the tooth surface of the planetary gear 5 and the tooth surface of the rotating internal gear ring 4 meshing therewith is located only on one side of the teeth of the planetary gear 5. When the input shaft 14 drives the sun gear 3 to rotate in the counterclockwise direction with respect to its own rotation axis (not shown), the output shaft 7 itself rotates in the clockwise direction, and the tooth surface gap is located only on the left side of the teeth of the planetary gear 5. However, it can be understood by those skilled in the art that the right side of the teeth of the planetary gear 5 is in contact with the tooth surface of the rotating internal gear ring 4.

[0071] When V1 < V2, the rotational movement directions of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 are the same as the rotational direction of the input shaft 14, the rotational direction of the output shaft 7 itself is the same as the rotational direction of the input shaft 14, and the tooth surface gap between the tooth surface of the planetary gear 5 and the tooth surface of the rotating internal gear ring 4 meshing therewith is held on the said one side of the teeth of the planetary gear 5. When the input shaft 14 drives the sun gear 3 to rotate in the counterclockwise direction with respect to its own rotation axis (not shown), the output shaft 7 itself rotates in the counterclockwise direction, and the tooth surface gap is still located only on the left side of the teeth of the planetary gear 5. However, it can be understood by those skilled in the art that the right side of the teeth of the planetary gear 5 is still in contact with the tooth surface of the rotating internal gear ring 4.

[0072] When V1 = V2, the rotational speed of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is zero, and the rotational speed of the output shaft 7 itself is zero.

[0073] According to each embodiment of the driving method described above, the first power source 1 is installed to output a constant power, the second power source 2 is installed to output a power with adjustable speed, and an electronic control device 11 is installed to process the rotational speed reduction or unstable error when the first power source 1 has different powers by the input control line 13.

[0074] According to each embodiment of the driving method described above, when the second power source 2 rolls with the rotating internal toothed ring 4, the motion data of the rotating internal toothed ring 4 is transmitted to the electronic control device 11 through a real-time data collection line 12 connected to the second power source 2, and the electronic control device 11 processes an internal program or an external command to control and adjust the power output of the second power source 2 through the real-time data collection line 12, so that the output shaft 7 can reach various speeds required under different working conditions.

[0075] According to each embodiment of the driving method described above, the first power source 1 is configured as a speed adjustable power output, and the electronic control device 11 controls the power output of the first power source 1 via an input control line 13 .

[0076] According to each embodiment of the driving method described above, a parallel gear 8 is installed on the rotating internal toothed ring 5, and the internal toothed ring driven by the second power source 2 is rotated. Drive A gear 9 meshes with the parallel gear 8 to drive the rotating internally toothed ring 4 .

[0077] According to each embodiment of the driving method described above, the front sun gear 10 is installed on the input shaft 14 and driven by the first power source 1. Sun gear drive The sun gear 3 is driven by a gear 15 meshing with the front sun gear 10 .

[0078] According to each embodiment of the driving method described above, the first power source and the second power source are arranged as a controllable, speed-adjustable power machine.

[0079] According to each embodiment of the drive method described above, the controllable, speed-adjustable power machine is an electric motor or an internal combustion engine. The invention as originally claimed in the present application is set forth below. [1] A transmission device having a dual power source, comprising a planetary gear assembly driven by the dual power sources, the planetary gear assembly comprising a sun gear (3), a rotating internal toothed ring (4), and a planetary gear (5) meshing between the sun gear (3) and the rotating internal toothed ring (4); the dual power source includes an input shaft (14) connected to the sun gear (3) and arranged to drive the sun gear (3) to rotate in a first direction relative to its own axis of rotation by means of the input shaft (14); the dual power sources are connected to the rotating internal toothed ring (4) and drive the rotating internal toothed ring (4) to rotate in a second direction opposite to the first direction about its own rotation axis, and at this time, the planetary gears (5) rotate in the second direction about their own rotation axis; A transmission device having dual power sources, wherein the direction of rotational movement of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch movement of the rotating internal tooth ring (4) and the linear velocity V2 of the pitch movement of the sun gear (3). [2] The dual power source includes a first power source (1) and a second power source (2); the first power source (1) is arranged to drive the sun gear (3) via the input shaft (14); The transmission device having dual power sources described in [1], wherein the second power source (2) is arranged to drive the rotating internal tooth ring (4). [3] The planetary gear (5) is attached to a planetary gear cage (6) on which an output shaft (7) is installed, The sun gear (3) is coaxially mounted on the rotating inner tooth ring (4), The transmission device having a dual power source according to [1], wherein the output shaft (7) is coaxially installed on the input shaft (14). [4] A transmission device having a dual power source as described in [3], wherein when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, the second direction is a clockwise direction. [5] When V1 > V2, the rotational movement directions of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) are opposite to the rotational direction of the input shaft (14), the rotational direction of the output shaft (7) itself is opposite to the rotational direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal gear ring (4) meshing therewith is located only on one side of the teeth of the planetary gear (5). [5] When V1 < V2, the rotational movement directions of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) are the same as the rotational direction of the input shaft (14), the rotational direction of the output shaft (7) itself is the same as the rotational direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal gear ring (4) meshing therewith is held on the said one side of the teeth of the planetary gear (5). [5] When V1 = V2, the rotational speeds of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) are zero, and the rotational speed of the output shaft (7) itself is zero. A transmission device having the dual power sources described in [3] or [4]. [6] A parallel gear (8) is installed on the rotating internal gear ring (4). The internal gear ring gear (9) driven by the second power source (2) meshes with the parallel gear (8), thereby driving the rotating internal gear ring (4). A transmission device having the dual power sources described in [5]. [7] A sun gear front gear (10) is installed on the input shaft (14). The input shaft gear (15) driven by the first power source (1) meshes with the sun gear front gear (10), thereby driving the sun gear (3). A transmission device having the dual power sources described in [5]. [8] The first power source (1) has a constant power output, and the second power source (2) has an adjustable speed power output. The electronic control device (11) processes the rotational speed reduction or instability error when the first power source (1) has different powers through the input control line (13). A transmission device having the dual power sources described in [5]. [9] When the second power source (2) rolls with the rotating internal gear ring (4), the motion data of the rotating internal gear ring (4) is transmitted to the electronic control device (11) by the real-time data acquisition line (12) connected to the second power source (2). The transmission device with dual power sources described in [8], wherein the electronic control device (11) processes an internal program or an external command to control and adjust the power output of the second power source power supply (2) through the real-time data collection line (12) so that the output shaft (7) can reach various speeds required under different working conditions.

[10] The first power source (1) has a speed-adjustable power output, and the electronic control device (11) controls the power output of the first power source (1) via an input control line (13).

[11] The transmission device having dual power sources described in [1], wherein the first power source and the second power source are controllable, speed-adjustable power machines.

[12] The transmission device with dual power sources described in

[10] , wherein the controllable, speed-adjustable power machine is an electric motor or an internal combustion engine.

[13] An electric vehicle comprising a transmission device having a dual power source according to any one of [1] to

[12] .

[14] A method for driving a transmission device according to any one of [1] to

[12] , the transmission device including a dual power source for driving a planetary gear assembly, the planetary gear assembly including a sun gear (3), a rotating internal tooth ring (4), and a planetary gear (5) meshing between the sun gear (3) and the rotating internal tooth ring (4); the dual power source includes an input shaft (14) connected to the sun gear (3) and arranged to drive the sun gear (3) to rotate in a first direction relative to its own axis of rotation by means of the input shaft (14); the dual power sources are connected to the rotating internal toothed ring (4) and drive the rotating internal toothed ring (4) to rotate in a second direction opposite to the first direction about its own rotation axis, and at this time, the planetary gears (5) rotate in the second direction about their own rotation axis; A driving method in which the direction of rotational movement of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch movement of the rotating internal toothed ring (4) and the linear velocity V2 of the pitch movement of the sun gear (3).

[15] The dual power source includes a first power source (1) and a second power source (2); The first power source (1) is arranged to drive the sun gear (3) by the input shaft (14). The drive method according to

[14] , wherein the second power source (2) is arranged to drive the rotating internal gear ring (4).

[16] Mount the planet gear (5) on the planet gear cage (6), install the output shaft (7) on the planet gear cage (6). Coaxially install the sun gear (3) with the rotating internal gear ring (4). The drive method according to

[14] , wherein the output shaft (7) is coaxially installed with the input shaft (14).

[17] When the first direction is the clockwise direction, the second direction is the counterclockwise direction, and when the first direction is the counterclockwise direction, the second direction is the clockwise direction. The drive method according to

[16] .

[18] When V1 > V2, the rotational movement direction of the planet gear (5) and the planet gear cage (6) around the input shaft (14) is opposite to the rotational direction of the input shaft (14), the rotational direction of the output shaft (7) itself is opposite to the rotational direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planet gear (5) and the tooth surface of the rotating internal gear ring (4) meshing therewith is located only on one side of the teeth of the planet gear (5). When V1 < V2, the rotational movement direction of the planet gear (5) and the planet gear cage (6) around the input shaft (14) is the same as the rotational direction of the input shaft (14), the rotational direction of the output shaft (7) itself is the same as the rotational direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planet gear (5) and the tooth surface of the rotating internal gear ring (4) meshing therewith is held on the said one side of the teeth of the planet gear (5). When V1 = V2, the rotational speed of the planet gear (5) and the planet gear cage (6) around the input shaft (14) is zero, and the rotational speed of the output shaft (7) itself is zero. The drive method according to

[17] .

[19] Install the first power source (1) to output a constant power, and install the second power source (2) to output a power with adjustable speed. Install an electronic control device (11) that processes the error of rotational speed reduction or instability when the first power source (1) has different powers by the input control line (13). The drive method according to

[18] .

[20] The second power source (2) rolls with the rotating internally toothed ring (4), and motion data of the rotating internally toothed ring (4) is transmitted to the electronic control device (11) by a real-time data collection line (12) connected to the second power source (2); The driving method described in

[19] , wherein the electronic control device (11) processes an internal program or an external command to control and adjust the power output of the second power source (2) through the real-time data collection line (12) so that the output shaft (7) can reach various speeds required under different working conditions.

[21] The driving method according to

[18] , wherein the first power source (1) is installed as a speed-adjustable power output, and the electronic control device (11) controls the power output of the first power source (1) via an input control line (13).

[22] The driving method according to

[14] , wherein the first power source and the second power source are arranged as controllable, speed-adjustable power machines.

[23] The driving method according to

[22] , wherein the controllable, speed-adjustable power machine is an electric motor or an internal combustion engine.

[24] The driving method described in

[18] , in which a parallel gear (8) is installed on the rotating internally toothed ring (5), and an internally toothed ring gear (9) driven by the second power source (2) meshes with the parallel gear (8), thereby driving the rotating internally toothed ring (4).

[25] The driving method described in

[18] , in which a front sun gear (10) is installed on the input shaft (14), and the sun gear (3) is driven by an input shaft gear (15) driven by the first power source (1) meshing with the front sun gear (10).

Claims

1. A transmission device having dual power sources, comprising a planetary gear assembly driven by said dual power sources, said planetary gear assembly comprising a sun gear (3), a rotating internal toothed ring (4), and a planetary gear (5) meshing between said sun gear (3) and said rotating internal toothed ring (4); the dual power source includes an input shaft (14) connected to the sun gear (3) and arranged to drive the sun gear (3) to rotate in a first direction relative to its own axis of rotation by means of the input shaft (14); the dual power sources are connected to the rotating internal toothed ring (4) and drive the rotating internal toothed ring (4) to rotate in a second direction opposite to the first direction about its axis of rotation, while the planetary gears (5) rotate in the second direction about their axis of rotation; The direction of rotational motion of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch motion of the rotating internal toothed ring (4) and the linear velocity V2 of the pitch motion of the sun gear (3), The dual power source includes a first power source (1) and a second power source (2); the first power source (1) is arranged to drive the sun gear (3) via the input shaft (14); The second power source (2) is arranged to drive the rotating internal toothed ring (4); the first power source (1) and the second power source (2) are installed on the same side of the planetary gear assembly; A parallel gear (8) is mounted on the rotating internal toothed ring (4), The rotating internal toothed ring (4) is driven by an internal toothed ring drive gear (9) driven by the second power source (2) meshing with the parallel gear (8). A front sun gear (10) is installed on the input shaft (14), The sun gear (3) is driven by a sun gear driving gear (15) driven by the first power source (1) meshing with the front sun gear (10), The sun gear (3) and the front sun gear (10) are disposed on both sides of the parallel gear (8) along the axial direction of the input shaft (14), It has dual power sources, The first power source (1) has a constant power output and the second power source (2) has an adjustable speed power output; The electronic control device (11) processes errors such as a drop in rotation speed or instability when the first power source (1) has a different power output through an input control line (13).

2. The planetary gears (5) are mounted in a planetary gear cage (6) on which an output shaft (7) is mounted; The sun gear (3) is coaxially mounted on the rotating inner tooth ring (4), 2. The transmission device with dual power sources as claimed in claim 1, wherein said output shaft (7) is coaxially mounted to said input shaft (14).

3. when the first direction is a clockwise direction, the second direction is a counterclockwise direction; 3. The dual power source transmission apparatus of claim 2, wherein said second direction is a clockwise direction when said first direction is a counterclockwise direction.

4. When V1>V2, the direction of rotation of the planetary gears (5) and the planetary gear cage (6) around the input shaft (14) is opposite to the rotation direction of the input shaft (14), the rotation direction of the output shaft (7) itself is opposite to the rotation direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal tooth ring (4) meshing therewith is located only on one side of the teeth of the planetary gear (5); When V1<V2, the direction of rotational movement of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is the same as the rotational direction of the input shaft (14), the rotational direction of the output shaft (7) itself is the same as the rotational direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal tooth ring (4) meshing therewith is maintained on the one side of the teeth of the planetary gear (5); 4. A transmission device with dual power sources as claimed in claim 2 or 3, wherein when V1=V2, the planetary gears (5) and the planetary gear cage (6) have zero rotational speed about the input shaft (14) and the output shaft (7) itself has zero rotational speed.

5. When the second power source (2) rolls with the rotating internal toothed ring (4), motion data of the rotating internal toothed ring (4) is transmitted to the electronic control device (11) through a real-time data collection line (12) connected to the second power source (2); 3. The transmission device with dual power sources as claimed in claim 2, wherein the electronic control device (11) processes an internal program or an external command to control and adjust the power output of the second power source (2) through the real-time data collection line (12) so that the output shaft (7) can reach various speeds required under different working conditions.

6. 2. The transmission device with dual power sources as claimed in claim 1, wherein the first power source (1) is a speed adjustable power output, and the electronic control device (11) controls the power output of the first power source (1) through an input control line (13).

7. 2. The dual power source transmission apparatus of claim 1, wherein said first power source and said second power source are controllable, speed adjustable power machines.

8. 7. The transmission apparatus with dual power sources as claimed in claim 6, wherein said controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

9. An electric vehicle comprising a transmission device having a dual power source according to any one of claims 1 to 8.

10. A method of driving a transmission device according to any one of claims 1 to 8, comprising: a dual power source driving a planetary gear assembly, the planetary gear assembly comprising a sun gear (3), a rotating internal toothed ring (4) and a planetary gear (5) meshing between the sun gear (3) and the rotating internal toothed ring (4); the dual power source comprising an input shaft (14) connected to the sun gear (3) and arranged to drive the sun gear (3) to rotate in a first direction relative to its own axis of rotation by means of the input shaft (14); the dual power sources are connected to the rotating internal toothed ring (4) and drive the rotating internal toothed ring (4) to rotate in a second direction opposite to the first direction about its axis of rotation, while the planetary gears (5) rotate in the second direction about their axis of rotation; The direction of rotational motion of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch motion of the rotating internal toothed ring (4) and the linear velocity V2 of the pitch motion of the sun gear (3), The dual power source includes a first power source (1) and a second power source (2); the first power source (1) is arranged to drive the sun gear (3) via the input shaft (14); The second power source (2) is arranged to drive the rotating internal toothed ring (4); the first power source (1) and the second power source (2) are installed on the same side of the planetary gear assembly; A parallel gear (8) is installed on the rotating internally toothed ring (4), and an internally toothed ring drive gear (9) driven by the second power source (2) meshes with the parallel gear (8), thereby driving the rotating internally toothed ring (4); A front sun gear (10) is installed on the input shaft (14), and a sun gear drive gear (15) driven by the first power source (1) meshes with the front sun gear (10), thereby driving the sun gear (3); The sun gear (3) and the front sun gear (10) are disposed on both sides of the parallel gear (8) along the axial direction of the input shaft (14), The first power source (1) is configured as a constant power output, and the second power source (2) is configured as a speed-adjustable power output; The driving method further comprises providing an electronic control device (11) for processing errors of rotational speed drop or instability when the first power source (1) has different power levels through an input control line (13).

11. The planetary gear (5) is mounted on a planetary gear cage (6), and an output shaft (7) is placed on the planetary gear cage (6); The sun gear (3) is coaxially mounted on the rotating inner tooth ring (4); 11. The method according to claim 10, wherein the output shaft (7) is arranged coaxially with the input shaft (14).

12. when the first direction is a clockwise direction, the second direction is a counterclockwise direction; The driving method according to claim 11 , wherein the second direction is a clockwise direction when the first direction is a counterclockwise direction.

13. When V1>V2, the direction of rotation of the planetary gears (5) and the planetary gear cage (6) around the input shaft (14) is opposite to the rotation direction of the input shaft (14), the rotation direction of the output shaft (7) itself is opposite to the rotation direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal tooth ring (4) meshing therewith is located only on one side of the teeth of the planetary gear (5); When V1<V2, the direction of rotational movement of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is the same as the rotational direction of the input shaft (14), the rotational direction of the output shaft (7) itself is the same as the rotational direction of the input shaft (14), and the tooth surface gap between the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal tooth ring (4) meshing therewith is maintained on the one side of the teeth of the planetary gear (5); 13. A method according to claim 12, wherein when V1=V2, the planetary gear (5) and the planetary gear cage (6) have a zero rotational speed about said input shaft (14) and the output shaft (7) itself has a zero rotational speed.

14. The second power source (2) rolls with the rotating internal toothed ring (4), and the motion data of the rotating internal toothed ring (4) is transmitted to the electronic control device (11) through a real-time data collection line (12) connected to the second power source (2); The driving method according to claim 11, wherein the electronic control device (11) processes an internal program or an external command to control and adjust the power output of the second power source (2) through the real-time data collection line (12) so that the output shaft (7) can reach various speeds required under different working conditions.

15. 11. The method of claim 10, wherein the first power source (1) is arranged as a speed adjustable power output, and the electronic control device (11) controls the power output of the first power source (1) via an input control line (13).

16. 11. The method of claim 10, further comprising providing the first and second power sources as a controllable, speed adjustable power machine.

17. 17. The method of claim 16, wherein the controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

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