CN216242087U - Side-lead controlled multi-gear planetary transmission - Google Patents

Abstract

The utility model discloses a side-lead controlled multi-gear planetary transmission, and relates to the technical field of transmissions. Comprises an input shaft, an output shaft and a speed change mechanism arranged between the input shaft and the output shaft; the speed change mechanism at least comprises a sliding gear sleeve, a first sun gear, a first planet gear and a composite gear ring, and the composite gear ring is movably arranged to rotate by itself; the first planet wheel is meshed with the inner teeth of the composite gear ring, the first planet wheel is meshed with the second planet wheel, the second planet wheel is also meshed with the second sun wheel, the first planet wheel and the second planet wheel are movably arranged on a planet carrier, and the planet carrier is connected with the output shaft; the transmission mechanism further comprises a first brake and a second brake, the first brake is arranged at the periphery of the transmission mechanism and used for braking the compound gear ring, the second brake is used for braking the second sun gear, and control elements such as the sliding gear sleeve, the first brake and the second brake are used for executing control actions so as to realize speed change. The utility model can reduce the whole axial size of the transmission so as to adapt to wider vehicle power requirements.

Description

Side-lead controlled multi-gear planetary transmission

Technical Field

The utility model relates to the technical field of transmissions, in particular to a side-guiding controlled multi-gear planetary transmission capable of reducing the axial size of the transmission.

Background

Modern vehicles widely employ multi-speed transmissions. The conventional gear type multi-gear transmission includes two types, a fixed shaft type and a planetary gear type, wherein the fixed shaft type realizes speed change by arranging a plurality of gears on two parallel shafts and by meshing different gears on the two shafts to generate different transmission ratios, so as to realize different output torques. The fixed shaft type transmission is simple in structure, the more gears of the fixed shaft type transmission are, the more gears are, the length corresponding to a gear shaft is lengthened, the axial length of the transmission is increased, and the size of the transmission is enlarged.

The planetary gear type speed changer is driven by one or a plurality of planetary gear train combinations, the state of each planetary gear train is controlled by a series of clutches and brakes so as to control a power transmission path in the speed changer, and the output torque and the rotating speed of an output shaft are changed to realize gear shifting and speed changing. The rotation axis of the brake or the clutch of the existing planetary gear type transmission is also coaxial with the sun gear of each planetary gear train, and is arranged in the front and the back of the planetary row in the transmission along the axis direction, the planetary row arranged in the planetary gear type transmission is increased along with the increase of the gears, the brake and the clutch used for control are also increased, and the brake and the clutch are arranged in the front and the back of the planetary row along the axial direction, so the whole axial length of the transmission is increased, and the arrangement and the installation of the transmission on an automobile are not facilitated.

SUMMERY OF THE UTILITY MODEL

The utility model provides a side-guiding controlled multi-gear planetary transmission, which moves brakes and clutches out of the front and rear of a planetary row and arranges the brakes and the clutches on the periphery of the planetary row, so that the transverse dimension of the transmission is increased and the axial dimension of the transmission is reduced, and the main problems in many practical applications are solved.

The technical scheme for solving the problems is as follows: the side-guiding controlled multi-gear planetary transmission comprises an input shaft, an output shaft and a speed change mechanism, wherein the speed change mechanism is arranged between the input shaft and the output shaft and used for transmitting power; the speed change mechanism at least comprises a first sun gear, a first planet gear meshed with the first sun gear and a compound gear ring meshed with the first planet gear, the compound gear ring is movably mounted to rotate, and the first planet gear is a duplicate gear with a large gear and a small gear; the composite gear ring comprises an engaging internal gear and a braking external gear, the engaging internal gear belongs to a part of the composite gear ring and is internally engaged with a pinion of the first planet gear, the braking external gear belongs to a part of the composite gear ring and is externally engaged with a gear of a first brake, the first brake is arranged on the periphery of the speed change mechanism, and the composite gear ring of the same body can be controlled by controlling the braking external gear; the duplex big and small gears of the first planet gear are movably arranged on a shaft positioned on the planet carrier, and the planet carrier is connected with the output shaft. The planetary transmission also comprises a sliding gear sleeve, a first brake, a second brake and a clutch, wherein the sliding gear sleeve, the first brake, the second brake and the clutch are all gear shifting control elements, a power transmission path is determined under the condition that all the control elements are actively set, and different rotating speeds and torques are obtained at the output shaft end to realize speed change.

Further, the transmission device also comprises a sliding gear sleeve, when the sliding gear sleeve moves rightwards to the right end position shown in the figure 1, the sliding gear sleeve is a forward gear, and the input power is transmitted to the first sun gear through the input shaft, the input gear, the sliding sleeve, the connecting gear and the first sun gear shaft.

Further, when the sliding gear sleeve is in the right end position, under the forward gear, the control element state is set: meanwhile, the overdrive clutch is in a separated state, the first brake is braked, the second brake is released, and the clutch is in a separated state. At the moment, the first overspeed gear and the second overspeed gear are separated and do not interfere with each other, the power transmitted to the first sun gear drives the first planet gear to rotate, the composite gear ring is braked by the first brake and cannot rotate, the first planet gear performs pure rolling rotation and revolution on an engaged internal gear of the composite gear ring, the revolution of the first planet gear pushes the planet carrier to rotate, and the planet carrier is connected with an output shaft to output power. This is the power transmission path for forward first gear.

Further, when the sliding gear sleeve is in the right end position, under the forward gear, the control element state is set: meanwhile, the overdrive clutch is in a separated state, the first brake is released, the second brake is braked, and the clutch is in a separated state. At the moment, the first overspeed gear and the second overspeed gear are separated and do not interfere with each other, the power transmitted to the first sun gear drives the first planet gear to rotate, the first planet gear is meshed to drive the second planet gear to rotate, the second sun gear is braked by the second brake and cannot rotate, the second planet gear performs pure rolling rotation and revolution on the second sun gear, the revolution of the second planet gear pushes the planet carrier to rotate, and the planet carrier is connected with an output shaft to output power. This is the power transmission path for the forward second gear.

Furthermore, when the sliding gear sleeve is at the right end position, the control element state is set under the forward gear, and simultaneously the overdrive clutch is in a separation state, the first brake is released, the second brake is released, and the clutch is in a combination state. At the moment, the first overspeed gear and the second overspeed gear are separated and do not interfere with each other, the shaft connected with the 2 brakes is completely and synchronously rotated due to the combination of the clutches, the braking external gear and the second braking gear are forced to synchronously rotate, namely, the second sun gear and the compound gear ring synchronously rotate, all the planet gears stop rotating, the whole planet gear is integrally revolved, namely, the planet carrier and the output shaft completely rotate at the same speed as the first sun gear and the input shaft, the input power is directly transmitted to the output shaft through the input shaft, the input gear, the sliding sleeve, the connecting gear and the whole planet gear, and the power transmission path is a power transmission path for advancing three gears, namely, a direct gear.

Further, when the sliding gear sleeve is in the right end position, under the forward gear, the control element state is set: meanwhile, the overdrive clutch is in a separation state, the first brake is released, the second brake is released, the clutch is in a separation state, the degree of freedom of the planetary gear is larger than 1, the planetary gear idles, power cannot be transmitted to the output shaft, the power is in a neutral gear, and the power is not transmitted.

Further, when the sliding gear sleeve is in the right end position, under the forward gear, the control element state is set: meanwhile, the overdrive clutch is in a combined state, the first brake is released, the second brake is released, and the clutch is in a separated state. At the moment, the planet row idles, power drives the overspeed gear through the input shaft, the first overspeed gear is driven in an engaged mode, power is transmitted to the second overspeed gear through the overspeed gear clutch, and the output gear is driven to drive the output shaft to rotate in an engaged mode. This is the power transmission path of the overdrive gear.

Further, the sliding gear sleeve is moved leftwards to be located at the leftmost end position, and the state of the control element is set as follows: meanwhile, the overdrive clutch is in a separated state, the first brake is braked, the second brake is released, and the clutch is in a separated state. At the moment, power drives the input gear through the input shaft and drives the second sun gear to rotate through the sliding gear sleeve, the second sun gear is meshed with and drives the second planet gear, the first planet gear is meshed and driven, pure rolling is carried out on the first sun gear braked by the first brake, the revolution of the first planet gear pushes the planet carrier to drive the output shaft to rotate, and the output rotation is reversed due to the fact that the planet carrier is transmitted through the 2 planet gears, so that the reverse gear power transmission path is formed.

Further, specifically stated: the second planet wheels do not directly interfere with the compound ring gear to cause movement.

The utility model has the beneficial effects that: the utility model provides a side-guiding controlled multi-gear planetary transmission, wherein a brake or a clutch is no longer arranged at the front or the rear of a planetary row as a control element, but is guided to a position at the side periphery of the planetary row through a gear. On the premise that the power transmission path of the planetary gear train can be controlled, the circumferential (transverse) size of the transmission is increased from the side circumference control to the front and rear coaxial control, but the axial (longitudinal) size is obviously reduced, the whole size of the transmission is reduced, the adaptability of the vehicle type is higher, and the power transmission device is suitable for wider vehicle power requirements.

After the scheme of side guiding arrangement is adopted, the power transmission path can be transmitted along the central axis, and a path which is firstly transmitted to a parallel shaft on the side periphery through external meshing of gears and then transmitted back to the central axis is added, and the scheme with an overdrive gear can be matched through the addition of the circuitous transmission. The traditional planetary gear transmission with a non-side-guide structure cannot have an overdrive gear.

The method for realizing the reverse gear is unique, utilizes the characteristic that the Ravigneaux train has two sun gears with opposite rotating directions, switches the sun gear obtaining power by control, leads the rotating directions of the input shaft and the output shaft to be opposite, and realizes the function of the reverse gear. On the premise of realizing the reverse gear function, the scheme is simpler than the traditional scheme, and the number of configured parts is less.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate embodiments of the utility model and together with the description, serve to explain the principles of the utility model. In the drawings, like reference numerals are used to indicate like elements. The drawings in the following description are directed to some, but not all embodiments of the utility model. For a person skilled in the art, other figures can be derived from these figures without inventive effort.

FIG. 1 is a schematic structural diagram of a side-lead controlled multi-speed planetary transmission in accordance with an embodiment of the present invention;

fig. 2 is a schematic diagram of a transmission engagement relationship of a ravigneaux planetary row having a 2-sun gear structure in a side-pulling controlled multi-gear planetary transmission according to an embodiment of the present invention.

1-input shaft, 2-output shaft, 3-first sun gear, 4-first planet gear, 5-compound gear ring, 6-meshing internal gear, 7-braking external gear, 8-planet carrier, 9-first brake, 10-second sun gear, 11-second planet gear, 12-input gear, 13-connecting gear, 14-first sun gear shaft, 15-sliding gear sleeve, 16-sleeve shaft, 17-second braking gear, 18-second brake, 19-clutch, 20-overdrive gear, 21-first overdrive gear, 22-second overdrive gear, 23-output gear, 24-overdrive clutch, 25-reverse gear internal gear, 26-external gear.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention. It should be noted that the embodiments and features of the embodiments in the present application may be arbitrarily combined with each other without conflict.

It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.

Referring to fig. 1 and fig. 2, a side-guiding controlled multi-gear planetary transmission according to an embodiment of the present invention is a planetary transmission with 4 forward gears, and the device of the present invention is explained in detail by taking each gear transmission path as a clue:

embodiment 4 a 4-speed planetary transmission includes an input shaft 1 and an output shaft 2, and a speed change mechanism provided between the input shaft 1 and the output shaft 2 and configured to transmit power; the input shaft 1 can be regarded as the rotating shaft of the internal-combustion engine, the output shaft 2 can be regarded as the rotating shaft of the driving wheel, the power is transmitted to the speed change mechanism from the input shaft 1 of the internal-combustion engine, and then transmitted to the output shaft 2 from the speed change mechanism, the input power is shunted and transmitted to different structures in the speed change mechanism, the power transmission path of the power in the speed change mechanism is guided and adjusted through the brake and the clutch, the torque and the rotating speed of the power output by the output shaft 2 of the speed change mechanism are adjusted and changed, and the gear shifting and speed changing are achieved.

Further, when the sliding gear sleeve 15 moves to the rightmost end position according to the control intention, the power is transmitted to the input gear 12 from the input shaft 1, the connecting gear 13 is driven by the sliding gear sleeve 15, and the first sun gear 3 is driven by the first sun gear shaft 14; selecting a set of control element states according to the control intent: that is, the first brake 9 is braked, the second brake 18 is released, the clutch 19 is disengaged, and the overdrive clutch 24 is disengaged; the power transmitted to the first sun gear 3 drives the first planet gear 4 to rotate, at this time, the first brake 9 is braked, so that the compound ring gear 5 is also braked, the first planet gear 4 performs pure rolling on the meshed internal gear 6 of the compound ring gear 5, and the shaft of the first planet gear 4 is positioned on the planet carrier 8 and pushes the planet carrier 8 to rotate by the revolution of the first planet gear. The second planet gears 11 and the second sun gear 10 are driven by the first planet gears to rotate in a idling mode without interfering with the movement of other parts, the first overdrive gear 21 and the second overdrive gear 22 which are normally meshed with the overdrive gear 20 are separated by separating the overdrive clutch 24, and the movement of gears of the parallel overdrive passages does not interfere with the power transmission of the planetary gear train; the planetary gear train state belongs to an NW planetary gear train, and the principle is known as follows: the rotation of the carrier 8 is in the same direction as the rotation of the first sun gear 3, but the rotational speed is slow and the torque is much larger than the input torque of the first sun gear 3, so that the lowest speed and maximum torque power is obtained at the output shaft 2. This is forward first gear.

Further, when the sliding gear sleeve 15 moves to the rightmost end position according to the control intention, the power is transmitted to the input gear 12 from the input shaft 1, the connecting gear 13 is driven by the sliding gear sleeve 15, and the first sun gear 3 is driven by the first sun gear shaft 14; selecting a set of control element states according to the control intent: i.e. the first brake 9 is released, the second brake 18 is braked, the clutch 19 is disengaged, and the overdrive clutch 24 is disengaged; the power transmitted to the first sun gear 3 drives the first planet gear 4 to rotate, the first planet gear 4 is meshed to drive the second planet gear 11 to rotate, at the moment, the first brake 9 is released, the compound gear ring 5 rotates idly without interfering any planet gear, the first overdrive gear 21 and the second overdrive gear 22 which are normally meshed with the overdrive gear 20 are separated by the separation of the overdrive clutch 24, and the motion of the gears of the parallel overdrive passages does not interfere with the power transmission of the planetary gear train; the second planet wheel 11 is meshed with the second sun wheel 10, but at this time, the second sun wheel 10 is braked due to the second brake 18, so that the second sun wheel 10 is also braked, the second planet wheel 11 rolls on the second sun wheel 10, the axis of the second planet wheel is located on the planet carrier 8, and the planet carrier 8 is pushed to rotate by the revolution of the second planet wheel. The state of the planetary gear train belongs to the variation of the NGW planetary gear train, and the principle is known as follows: the rotation of the carrier 8 is in the same direction as the rotation of the first sun gear 3, but the rotation speed is slower and the torque is larger than the input torque of the first sun gear 3, so that the output shaft 2 receives the power of the next lower speed and the next larger torque. This is going forward by two.

Further, when the sliding gear sleeve 15 moves to the rightmost end position according to the control intention, the power is transmitted to the input gear 12 from the input shaft 1, the connecting gear 13 is driven by the sliding gear sleeve 15, and the first sun gear 3 is driven by the first sun gear shaft 14; selecting a set of control element states according to the control intent: i.e. first brake 9 released, second brake 18 released, clutch 19 engaged, overdrive clutch 24 disengaged; since the combination of the clutch 19 makes the shafts connected with the 2 brakes rotate completely synchronously, the braking external gear 7 and the second braking gear 17 are forced to rotate synchronously, namely the second sun gear 10 and the compound gear ring 5 rotate synchronously, all the planet gears stop rotating automatically, and the whole planet gear row revolves integrally, namely the planet carrier 8, the output shaft 2, the first sun gear 3 and the input shaft 1 rotate at the same speed and torque completely. The separation of the overdrive clutch 24 separates the first overdrive gear 21 and the second overdrive gear 22, which are constantly engaged with the overdrive gear 20, so that the motion of the gears of the parallel overdrive passages does not interfere with the power transmission of the planetary gear train; this provides the output shaft 2 with the same rotational speed and the same torque as the input shaft 1, which is the direct gear, i.e., the forward third gear. It is higher and lower than the forward two speeds.

Further, when the sliding sleeve gear 15 is moved to the rightmost end position according to the control intention, a set of control element states is selected according to the control intention: i.e. first brake 9 released, second brake 18 released, clutch 19 disengaged, overdrive clutch 24 engaged; at this time, all control elements of the planetary gear train, namely 2 brakes and 1 clutch, are in a releasing and separating state, the degree of freedom of the planetary gear train is greater than 1 and cannot transmit torque, but the input shaft 1 drives the overdrive gear 20 to mesh with the first overdrive gear 21 to rotate, the first overdrive gear 21 can transmit power to the second overdrive gear 22 due to the combination of the overdrive clutch 24, so that the second overdrive gear 22 can mesh with the output gear 23 to drive the output shaft 2 to rotate, the power is transmitted through the path and undergoes one-stage large acceleration and one-stage small deceleration, the comprehensive effect is acceleration transmission, and the power with higher rotating speed and lower torque is obtained on the output shaft 2, which is an overdrive gear.

Further, when the sliding sleeve gear 15 is moved to the rightmost end position according to the control intention, a set of control element states is selected according to the control intention: i.e. the first brake 9 is released, the second brake 18 is released, the clutch 19 is disengaged, the overdrive clutch 24 is disengaged; at the moment, all control elements of the planet row, namely 2 brakes and 1 clutch are in a loosening and separating state, the degree of freedom of the planet row is more than 1, and the planet row can not transmit torque; and the overdrive clutch is separated, so that an overdrive power channel is also isolated and cannot transmit power, and the power of any channel cannot be obtained on the output shaft 2, which is neutral.

Further, when the sliding sleeve gear 15 is moved to the leftmost position according to the control intention, a set of control element states is selected according to the control intention: that is, the first brake 9 is braked, the second brake 18 is released, the clutch 19 is disengaged, and the overdrive clutch 24 is disengaged; the power is transmitted to the second sun gear 10 through the second brake gear 17 by the embedding of the input gear 12, the sliding gear sleeve 15, the external gear 26 and the reverse gear internal gear 25, and then is meshed with the first planet gear 4 through the second planet gear 11, when the first brake 9 is braked, the first planet gear 4 rolls on the meshed internal gear 6 of the compound gear ring 5, the shaft of the first planet gear 4 is positioned on the planet carrier 8, and the planet carrier 8 is pushed to rotate by the revolution of the first planet gear, because the transmission chain passes through one more planet gear and has the function of changing the rotating direction, the output shaft 2 is driven to rotate in the direction opposite to the input shaft, but the rotating speed is slow, and the torque is much larger than the torque input by the second sun gear 10, so that the power with reverse direction, low speed and large torque is obtained on the output shaft 2. This is the reverse gear.

Further, the second planet gears 11 are not in the same plane as the compound ring gear 5, and there is no meshing connection relationship between them.

The main consideration in this embodiment is the overall structural arrangement of the transmission and the transmission shift principle based on this structure, so the specific structural forms of the brake, the clutch, the sliding gear sleeve, etc. for external control are not described in detail, and the control structures thereof are mainly the conventional common structural types.

Where not mentioned above, all are applicable to the prior art.

Finally, it should be noted that: the above examples are only for illustrating the technical solutions of the present invention, and are not limited thereto. Although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.

Claims (9)

1. The utility model provides a side draws many grades of planetary transmission of control which characterized in that: the power transmission device comprises an input shaft (1), an output shaft (2) and a speed change mechanism which is arranged between the input shaft (1) and the output shaft (2) and is used for transmitting power; the speed change mechanism at least comprises a first sun gear (3), a first planet gear (4) meshed with the first sun gear (3) and a composite gear ring (5) meshed with the first planet gear (4), wherein the composite gear ring (5) is movably arranged to rotate, and the first planet gear (4) is a duplicate gear with a large gear and a small gear; the compound gear ring (5) comprises an internal meshing gear (6) and an external braking gear (7), the internal meshing gear (6) belongs to a part of the compound gear ring (5) and is internally meshed with a pinion of the first planetary gear (4), the external braking gear (7) belongs to a part of the compound gear ring (5) and is externally meshed with a gear of a first brake (9), the first brake (9) is arranged on the periphery of the speed change mechanism, and the compound gear ring (5) in the same body can be controlled by controlling the external braking gear (7); the duplex big and small gears of the first planet gear (4) are movably arranged on a shaft positioned on the planet carrier (8), and the planet carrier (8) is connected with the output shaft (2); the first brake (9) can brake the compound gear ring (5) to enable the output torque of the output shaft (2) to be increased and the rotating speed to be lowered so as to realize speed change.

2. A side-piloted, multi-speed planetary transmission as in claim 1, wherein: the planetary gear set further comprises a second sun gear (10) and a second planetary gear (11), wherein the second sun gear (10) is coaxial with the first sun gear (3), the second planetary gear (10) is meshed with the second planetary gear (11), and the second planetary gear (11) is movably mounted on the planet carrier (8) and is meshed with the first planetary gear (4).

3. A side-piloted, multi-speed planetary transmission as in claim 2 wherein: the first sun wheel (3), the first sun wheel shaft (14) and the connecting gear (13) are connected into a whole; the second sun gear (10) is connected with the sleeve shaft (16), the second brake gear (17) and the reverse gear inner gear (25) into a whole and is coaxially arranged with the first sun gear (3), but the second sun gear (10) is sleeved on the first sun gear shaft (14) of the first sun gear (3) by the sleeve shaft (16) and can rotate independently.

4. A side-piloted, multi-speed planetary transmission as in claim 3 wherein: the input shaft (1) is provided with an input gear (12), the input gear (12) is sleeved with a sliding gear sleeve (15), the sliding gear sleeve (15) slides on the input gear (12) forever and keeps synchronous rotation with the input gear (12), and the sliding gear sleeve (15) is provided with external teeth (26) besides internal teeth.

5. A side-piloted, multi-speed planetary transmission as in claim 4 wherein: the sliding gear sleeve (15) can slide coaxially along the input gear (12); the sliding gear sleeve (15) slides to be separated from the connecting gear (13) and simultaneously causes the external teeth (26) on the periphery of the sliding gear sleeve (15) to be meshed with the reverse gear internal gear (25) on the second brake gear (17); the sliding gear sleeve (15) can also slide to be connected with the connecting gear (13) and simultaneously enable the external teeth (26) on the periphery of the sliding gear sleeve (15) to be disengaged from the reverse gear internal gear (25) on the second brake gear (17), so that the sliding gear sleeve (15) rotates along with the input shaft (1) and slides controllably to transmit the power of the input shaft (1) to the second sun gear (10) or the first sun gear (3).

6. A side-piloted, multi-speed planetary transmission as in claim 5 wherein: the second sun gear (10) is meshed with the second planet gear (11), the second sun gear (10) is integrally connected with a second brake gear (17) through a sleeve shaft (16), and the second brake gear (17) is meshed with a gear on a second brake (18) arranged on the periphery of the speed change mechanism.

7. A side-piloted, multi-speed planetary transmission as in claim 6 wherein: the brake further comprises a clutch (19) for coupling the first brake (9) and the second brake (18), wherein one component of the clutch (19) and the second brake (18) are arranged on the same brake shaft; the other component of the clutch (19) and the first brake (9) are arranged on the same brake sleeve shaft, and the brake sleeve shaft is movably arranged on the brake shaft.

8. A side-piloted, multi-speed planetary transmission as in claim 1, wherein: the input shaft is characterized by further comprising an over speed gear (20) arranged on the input shaft (1), a first over speed gear (21) meshed with the over speed gear (20), and a second over speed gear (22) coaxially arranged with the first over speed gear (21), wherein the second over speed gear (22) is movably sleeved on the shaft of the first over speed gear (21) and can freely rotate; the output gear (23) is arranged on the output shaft (2), and the output gear (23) is meshed with a second overspeed gear (22); also included is an overdrive clutch (24) for engaging the first and second overdrive gears (21, 22) to transmit or separate power.

9. A side-piloted, multi-speed planetary transmission as in claim 2 wherein: the second planet wheel (11) is not in meshed connection with the compound gear ring (5).

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