Electric drive assembly and vehicle

Abstract

The electric drive assembly comprises a drive motor, the periphery of a motor shaft is in transmission connection with a first gear set, the first gear set is in transmission connection with a planetary gear train so as to transmit torque to a sun gear in the planetary gear train, and one end of the sun gear is matched with a first-gear gear through a spline; one end of a planet carrier in the planetary gear train, which is in transmission fit with the sun gear, is fixedly connected with a second-gear gear; the synchronizer comprises a gear sleeve and a gear ring, the gear sleeve is arranged on the gear ring in a sliding mode in the axial direction, and the sliding path of the gear sleeve at least comprises three working positions which are the position engaged with the first-gear gear, the position engaged with the second-gear gear and the position disengaged from the two-gear gear; the gear sleeve is in transmission connection with a second gear set, and the second gear set is in transmission connection with the differential mechanism. The compact structure advantage of torque adjustment of the planetary gear train and the efficient advantage of gear adjustment of the synchronizer are combined, so that the driving assembly is high in structure integration degree, and the adjustment process is accurate and rapid.

Description

Technical Field

[0001] The present invention relates to the technical field of gearbox equipment, and in particular to an electric drive assembly and a vehicle. Background Art

[0002] The electric drive assembly of electric vehicles is generally a two-stage reduction single-speed structure. Among the commonly used two-speed electric drive assembly shift structures, one is the traditional two parallel shafts equipped with gears of different speed ratios, and the gear sets of different speed ratios are engaged through synchronizer sleeves to achieve shifting; the other is to use a planetary gear set, by directly transmitting torque from the sun gear, and adding a gear set reduction through the sun gear and the planet carrier to achieve the switching of high-speed and low-speed gears. The above structure of arranging multiple sets of gears on parallel shafts occupies a large space, and the corresponding chassis layout of the vehicle model is difficult. At the same time, the center of the motor deviates from the rotation center, and the drive system is prone to torsional imbalance vibration; and the switching of the planetary gears often requires the cooperation of a dual hydraulic clutch, resulting in a complex overall structure of the drive assembly and a long axial distance. When the gear clutch is working, it relies on the electric hydraulic pump to provide oil pressure to press the friction plate to transmit torque, and the loss of electrical energy is relatively large. When the hydraulic system does not work properly, the friction plate of the hydraulic clutch will burn out quickly, causing the electric drive assembly to fail.

[0003] Therefore, how to reduce the space occupied by the electric drive assembly and improve its operational reliability is a technical problem that needs to be urgently solved by technical personnel in this field. Summary of the invention

[0004] In view of this, an object of the present invention is to provide an electric drive assembly that occupies little space and has high operational reliability.

[0005] Another object of the present invention is to provide a vehicle comprising the above electric drive assembly.

[0006] To achieve the above object, the present invention provides the following technical solutions:

[0007] An electric drive assembly, comprising:

[0008] A drive motor, wherein the outer periphery of the motor shaft of the drive motor is transmission-connected with a first gear set, the first gear set is transmission-connected with a planetary gear train to transmit torque to a sun gear in the planetary gear train, one end of the sun gear is splined with a first gear; one end of a planet carrier in the planetary gear train that is transmission-connected with the sun gear is fixedly connected with a second gear;

[0009] A synchronizer includes a gear sleeve and a gear ring, wherein the gear sleeve is axially slidably arranged on the gear ring, and the sliding path of the gear sleeve includes at least three working positions, and the three working positions of the gear sleeve are respectively engaged with the first gear position gear, engaged with the second gear position gear, and disengaged from the first gear position gear and the second gear position gear; the gear sleeve is drivingly connected to the second gear set, and the second gear set is drivingly connected to the differential.

[0010] Preferably, in the above-mentioned electric drive assembly, the synchronizer also includes synchronous combining teeth, and the internal spline of the gear sleeve is arranged in a three-section structure along its axial direction, the first section is a complete internal spline and is meshed with the synchronous combining teeth gap, the second section is an inwardly concave avoidance structure, and the third section is an engaging tooth structure and is used to mesh with the combining teeth on the first gear position gear or the second gear position gear; the synchronizer is meshed with the second gear set for transmission through the synchronous combining teeth.

[0011] Preferably, in the above electric drive assembly, when the gear sleeve is disengaged from the first gear position gear and the second gear position gear, the third section is located between the first gear position gear and the second gear position gear in the axial direction.

[0012] Preferably, in the above electric drive assembly, the first gear set includes a first-stage driving gear and a first-stage passive gear that are meshed with each other, the first-stage driving gear is connected to the external spline of the motor shaft via an internal spline, and the first-stage passive gear is welded and fixed to the sun gear.

[0013] Preferably, in the above electric drive assembly, the second gear set includes a secondary driving gear and a secondary passive gear that are meshed with each other, the secondary driving gear is meshed with the synchronous combining gear, and the secondary passive gear is fixed on the differential to drive the differential to rotate.

[0014] Preferably, in the above electric drive assembly, the sun gear and the secondary driving gear are nested and arranged to rotate relative to each other via at least two sets of first bearings arranged at intervals.

[0015] Preferably, in the above-mentioned electric drive assembly, the planetary gear system also includes three planetary gears, the planetary gears are meshed with the sun gear and are evenly arranged along the circumference of the sun gear, the outer circumference of the planetary gear is meshed with an inner gear ring, and the planetary gears are connected to the planetary carrier through a second bearing.

[0016] Preferably, in the above electric drive assembly, the drive motor is a coaxial motor, and the motor shaft is a hollow structure.

[0017] Preferably, in the above electric drive assembly, the outer ring of the gear sleeve is designed with a groove, and the shift fork is inserted into the groove to push the gear sleeve to slide along its axial direction.

[0018] A vehicle comprises the electric drive assembly described in any one of the above embodiments.

[0019] It can be seen from the above technical solution that the electric drive assembly provided by the present invention, by setting a planetary gear train, can realize that when a single drive motor is in the starting state, the sun gear and the planet carrier in the planetary gear train can output different torques, so as to realize the different speed operation of the first gear and the second gear. On this basis, the electric drive assembly is also provided with a synchronizer, and the gear sleeve in the synchronizer is set to slide along the axial direction of the gear ring, so as to be able to combine with the first gear or the second gear, and receive the torque transmission of the first gear or the second gear. Similarly, by setting the sliding path of the gear sleeve, it can also design a neutral position, so that the torque of the first gear and the second gear cannot be transmitted to the synchronizer position. On this basis, the synchronizer is also connected to the second gear set in transmission, so as to drive the differential through the second gear set, so as to realize the adjustment of the wheel running state. The above structure not only avoids the eccentric two-speed electric drive assembly through the setting of the planetary gear train, but also improves the integration of the structure by avoiding the occupation of chassis space by the setting of multiple shafts and gear trains when providing different torque outputs. At the same time, the gear switching is completed by switching and adjusting the first gear gear or the second gear gear through the synchronizer, which solves the problem of complex structure and easy burning of friction plates in the planetary gear train when the torque is transmitted by pressing the friction plates through the dual hydraulic clutches, thereby making the electric drive assembly have higher integration and operation reliability. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0021] Figure 1 A schematic diagram of the structure of an electric drive assembly provided in an embodiment of the present invention;

[0022] Figure 2 The electric drive assembly is in high gear operation;

[0023] Figure 3 The electric drive assembly is in the low gear operating state.

[0024] Among them, 10-drive motor; 110-motor shaft; 210-first-stage driving gear; 220-first-stage passive gear; 310-sun gear; 320-planet carrier; 330-planet gear; 340-inner ring gear; 410-first gear; 420-second gear; 50-synchronizer; 510-gear sleeve; 520-gear ring; 530-synchronizing coupling gear; 610-secondary driving gear; 620-secondary passive gear; 70-differential; 80-first bearing; 90-second bearing. DETAILED DESCRIPTION

[0025] The core of the present invention is to disclose an electric drive assembly which occupies little space and has high operational reliability.

[0026] Another object of the present invention is to disclose a vehicle comprising the above electric drive assembly.

[0027] In order to make the technical personnel in this field better understand the scheme of the present invention, the embodiments of the present invention are described below with reference to the accompanying drawings. In addition, the embodiments shown below do not limit the content of the invention recorded in the claims. In addition, the entire contents of the structures represented by the following embodiments are not limited to those necessary for the solutions of the invention recorded in the claims.

[0028] like Figure 1 As shown, the electric drive assembly provided by the embodiment of the present invention includes a drive motor 10 and a synchronizer 50, wherein the drive motor 10 is used to provide power input, and includes a motor shaft 110 for power transmission, and a first gear set is connected to the outer periphery of the motor shaft 110 to receive the power output of the motor shaft 110 through the first gear set. At the same time, a planetary gear train is also provided in the electric drive assembly, and the first gear set is connected to the planetary gear train to transmit torque to the sun gear 310 in the planetary gear train, and one end of the sun gear 310 is connected to the first gear gear 410 to transmit torque to the first gear gear 410. Combined with the structural basis, it is preferred that one end of the sun gear 310 cooperates with the inner spline of the first gear gear 410 through its tail spline. In the above structure, the power output of the motor shaft 110 can be transmitted to the sun gear 310 through the first gear set, and then transmitted to the first gear gear 410 and drives the first gear gear 410 to rotate.

[0029] On the basis of the above structure, the planetary gear system also includes a planet carrier 320 that cooperates with the sun gear 310 through the planetary gear 330. The rotation speed and transmission ratio of the planet carrier 320 and the sun gear 310 are different. At the same time, one end of the planet carrier 320 is fixedly connected to the second gear 420 to drive the second gear 420 to rotate during the rotation of the planet carrier 320. In some embodiments of the present invention, one end of the planet carrier 320 is fixed to the second gear 420 by laser welding to directly transmit torque to the second gear 420 when the planet carrier 320 rotates. In the above structure, the power output of the motor shaft 110 can be transmitted to the sun gear 310 through the first gear set, and then transmitted to the planet carrier 320 through the sun gear 310, thereby driving the second gear 420 fixedly connected to the planet carrier 320 to achieve rotation.

[0030] In the above embodiment, due to the setting of the planetary gear train, the drive motor 10 can simultaneously transmit torque to the first gear 410 and the second gear 420 during the start input process, that is, the first gear 410 and the second gear 420 are driven to rotate at the same time. Specifically, the transmission path of the drive motor 10 to the first gear 410 is that the output torque of the motor shaft 110 passes through the first gear set and the sun gear 310, and then drives the first gear 410 to rotate. The transmission path of the drive motor 10 to the second gear 420 is that the output torque of the motor shaft 110 passes through the first gear set, the sun gear 310, and the planet carrier 320, and then drives the second gear 420 to rotate. On the basis of the above structure, the electric drive assembly also includes a synchronizer 50, which includes a gear sleeve 510 and a gear ring 520 structure. Specifically, the gear sleeve 510 is slidably arranged on the gear ring 520 along its axial direction. At the same time, the gear sleeve 510 includes at least three working positions on its sliding path. The three working positions of the gear sleeve 510 specifically include a working position in which the gear sleeve 510 is meshed with the first gear gear 410 to transmit the torque of the first gear gear 410; a working position in which the gear sleeve 510 is meshed with the second gear gear 420 to transmit the torque of the second gear gear 420; and a working position in which the gear sleeve 510 is disengaged from the first gear gear 410 and the second gear gear 420 at the same time and no torque transmission is performed.

[0031] It should be noted that the electric drive assembly provided in the embodiment of the present invention realizes gear shifting adjustment through the synchronizer 50. When the drive motor 10 is started, the first gear gear 410 and the second gear gear 420 realize different speeds of operation in different transmission paths, and the synchronizer sleeve slides left and right on the gear ring 520 to select to combine with different gears to realize torque transmission of different gears. At the same time, the gear sleeve 510 is also transmission-connected to the second gear set, and the second gear set is used for transmission connection to the differential 70. On this basis, the gear sleeve 510 can choose to transmit the first gear gear 410, the second gear gear 420, or the neutral torque to the differential 70, and drive the differential 70 to rotate, and distribute the torque to the left and right drive shafts of the vehicle through the differential 70. The left and right drive shafts can rotate at different speeds to achieve the purpose of straight-line travel or turning of the vehicle.

[0032] The electric drive assembly provided in the embodiment of the present invention is provided with a planetary gear train to realize that when a single drive motor 10 is in the starting state, the sun gear 310 and the planet carrier 320 in the planetary gear train can output different torques, so as to realize the different speed operation of the first gear 410 and the second gear 420. On this basis, the electric drive assembly is also provided with a synchronizer 50, and the gear sleeve 510 in the synchronizer 50 is slidably arranged along the axial direction of the gear ring 520, so as to be able to be combined with the first gear 410 or the second gear 420, and receive the torque transmission of the first gear 410 or the second gear 420. Similarly, by setting the sliding path of the gear sleeve 510, it can also design a neutral position, so that the torque of the first gear 410 and the second gear 420 cannot be transmitted to the synchronizer 50 position. On this basis, the synchronizer 50 is also connected to the second gear set in transmission, so as to drive the differential 70 through the second gear set, so as to realize the adjustment of the wheel running state. The above structure not only avoids the eccentric two-speed electric drive assembly through the setting of the planetary gear train, but also improves the integration of the structure by avoiding the occupation of chassis space by the setting of multiple shafts and gear trains when providing different torque outputs. At the same time, the first gear gear 410 or the second gear gear 420 is switched and adjusted through the synchronizer 50 to complete the gear switching, solving the problem of complex structure and easy burning of friction plates in the planetary gear train when the torque is transmitted by pressing the friction plates through the dual hydraulic clutches, thereby making the electric drive assembly have higher integration and operation reliability.

[0033] Further, in some embodiments of the present invention, the synchronizer 50 also includes a synchronous coupling tooth 530 for torque transmission, and the structure of the gear sleeve 510 is specifically that the inner ring of the gear sleeve 510 is provided with an internal spline, and the internal spline is a three-section structure along the axial direction of the gear sleeve 510, specifically, the first section is a complete internal spline structure, and the first section is gap-engaged with the synchronous coupling tooth 530. It should be noted that the gap engagement here specifically refers to that the internal spline structure of the first section can transmit torque to the synchronous coupling tooth 530 through the combination during circumferential rotation to achieve power transmission, and the gap fit refers to the gap between the internal spline of the first section and the synchronous coupling tooth 530, which can enable the gear sleeve 510 to slide smoothly along the axial direction. The second section is a concave avoidance structure, so as to be able to make room and avoid rotational collision between the spline teeth on both sides thereof. The third section is a meshing tooth structure for meshing with the coupling teeth on the first gear gear 410 or the second gear gear 420. When the third section meshes with the coupling teeth on the gear, the gear sleeve 510 can rotate and drive the synchronous coupling rotation through its first section; on this basis, the synchronizer 50 meshes with the second gear set through the synchronous coupling teeth 530 to transmit torque to the second gear set when the synchronous coupling teeth 530 rotate.

[0034] It should be noted that bidirectional meshing teeth are preferably arranged on the third section of the gear sleeve 510, and both ends of the meshing teeth are designed to have a cone angle structure of 62° to ensure the success rate of meshing and shifting gears; and a chamfer structure of 2°-3° is designed in the axial tooth profile direction to match the axial tooth profile chamfer of the engaging teeth on the first gear gear 410 or the second gear gear 420, so as to form an axial biting force when the two are meshed to transmit torque, thereby preventing axial relative movement and gear disengagement.

[0035] It should be further explained that the toothed end of the second gear position gear 420 is also designed with a cone angle structure to ensure the success rate of shifting, and the axial tooth profile has a 2°-3° chamfered structure to match the tooth profile of the gear sleeve 510 to form an axial locking force to ensure that the gear does not shift out of gear. In addition, the second gear position gear 420 is laser welded to the planetary carrier 320 to transmit the torque of the planetary carrier 320, and a bearing hole is designed and a deep groove ball bearing is installed to support the rotation of the planetary carrier 320.

[0036] As for the synchronizer 50, it is also provided with a spring glass ball assembly, which is composed of a small spring, a spring bracket and a glass ball bracket. After the spring glass ball assembly is assembled, the convex point of the glass ball bracket has sufficient elasticity through the spring. The spring glass ball assembly is arranged on the gear ring 520 and squeezes the groove of the gear sleeve 510 to form an axial resistance, and prevents the gear sleeve 510 from continuing to slide when the gear sleeve 510 is in the required gear position. In order to maintain the uniformity of force, the gear ring 520 is designed as an integral double cone friction surface structure, and three spring glass ball structures are arranged on its outer ring. The three spring glass balls squeeze the high speed, low speed and neutral gear grooves of the gear ring 520 in the radial direction, so that the gear ring 520 has a certain axial resistance and stays in these three gears. The double cone friction surface contacts the friction cone surface of the first gear gear 410 and the second gear gear 420 respectively, so as to output torque in advance, so that the two have similar speeds and rotate synchronously, and achieve the purpose of no impact when shifting.

[0037] Furthermore, considering the smoothness of the gear sleeve 510 when performing the gear shifting action and the rationality of the structural setting, in some embodiments of the present invention, when the gear sleeve 510 is disengaged from the first gear gear 410 and the second gear gear 420, the third section is located between the first gear gear 410 and the second gear gear 420 in the axial direction, that is, in the axial direction of the gear sleeve 510, the gear sleeve 510 moves in the opposite direction to achieve engagement with the first gear gear 410 and the second gear gear 420, so that when the electric drive assembly is in the neutral state, the gear can be quickly selected to achieve engagement with the first gear gear 410 or the second gear gear 420, thereby improving the speed of gear adjustment and the operating stability of the electric drive assembly.

[0038] Specifically, as for the first gear set for transmitting the torque of the motor shaft 110, it can select several gears for matching according to the transmission requirements of the vehicle and the design requirements of the electric drive assembly to meet the transmission ratio requirements. In order to increase the transmission speed, in some embodiments of the present invention, the first gear set includes a meshing primary driving gear 210 and a primary passive gear 220, that is, the torque is quickly transmitted through two gears. On this basis, the primary driving gear 210 is connected to the external spline of the motor shaft 110 through an internal spline. When the motor shaft 110 is transmitting, the torque is transmitted to the primary driving gear 210 through the spline matching to drive the primary driving gear 210 to rotate, and the primary driving gear 210 drives the primary passive gear 220 to rotate through the meshing action with the primary passive gear 220, and the primary passive gear 220 is welded and fixed to the sun gear 310 to achieve the torque transmission to the sun gear 310. It should also be noted that in order to improve the compactness of the structure and the integration of the electric drive assembly, a bearing of the planet carrier 320 is installed on the cylindrical step at one end of the first-stage passive gear 220 to support the rotational movement of the planet carrier 320 .

[0039] Furthermore, for the second gear set connected to the gear sleeve 510, it also preferably includes a secondary driving gear 610 and a secondary passive gear 620, wherein the secondary driving gear 610 meshes with the synchronous combination gear 530 to receive the rotation torque of the synchronous combination gear 530 when the gear sleeve 510 transmits torque, and drives the secondary passive gear 620 to rotate through meshing, and the secondary passive gear 620 is fixed on the differential 70 to drive the differential 70 to rotate, and transmits it to the wheels through the drive shaft; specifically, the differential 70 distributes the torque of the secondary passive gear 620 to the left and right drive shafts, and the left and right drive shafts can rotate at different speeds to achieve the vehicle to walk in a straight line or turn. That is, the torque transmitted by the secondary driving gear 610 is sequentially transmitted to the differential 70, the drive shaft and the wheel system to achieve the forward or backward movement of the vehicle.

[0040] Similarly, in order to improve the structural integration of the electric drive assembly, the sun gear 310 and the secondary driving gear 610 are nested, specifically, the axle of the secondary driving gear 610 passes through the middle hole of the sun gear 310 and fits with the inner wall of the middle hole of the sun gear 310, so as to minimize the space occupied by the electric drive assembly and reduce the torque transmission path from the drive motor 10 to the differential 70. On this basis, the base surface of the sun gear 310 and the secondary driving gear 610 is arranged to achieve relative rotation through at least two sets of first bearings 80 arranged at intervals. It should be noted that the first bearing 80 is preferably a needle bearing to have a higher load-bearing capacity and smooth operation ability, and at the same time, the structure is more compact.

[0041] Furthermore, in the electric drive assembly provided in an embodiment of the present invention, the planetary gear system also includes a planetary gear 330 and an inner ring gear 340, wherein the inner ring gear 340 is fixedly disposed in the reducer housing and is internally meshed with the planetary gear 330 to support the planetary gear 330 to rotate around the sun gear 310. At the same time, three planetary gears 330 are provided, and each planetary gear 330 is meshed with the sun gear 310. The three planetary gears 330 are evenly arranged along the circumference of the sun gear 310 and are connected and supported by the planetary carrier 320. Specifically, the planetary gears 330 are connected to the planetary carrier 320 through the second bearing 90 so that the planetary gears 330 can rotate relative to the planetary carrier 320. The planetary gears 330 realize torque transmission from the sun gear 310 to the planetary carrier 320 through self-rotation and revolution around the sun gear 310, and realize speed reduction at the same time, so that there is a speed difference between the first gear 410 directly connected to the sun gear 310 and the second gear 420 fixedly connected to the planetary carrier 320, thereby meeting the subsequent gear shifting drive requirements.

[0042] It should be specifically explained that in the electric drive assembly provided in the embodiment of the present invention, according to the meshing relationship of the gear train, Figure 2As shown, when the gear sleeve 510 is in the working position meshing with the first gear 410, the electric drive assembly is in a high gear state. At this time, the torque transmission path is that the motor shaft 110 transmits the torque to the primary driving gear 210, and the primary driving gear 210 transmits the torque to the primary passive gear 220 through meshing, and the primary passive gear 220 can drive the sun gear 310 fixedly connected thereto to rotate, and the sun gear 310 transmits the torque to the first gear 410 through the spline, and the first gear 410 drives the synchronous combination tooth 530 to rotate under the meshing action of the synchronizer 50, and then drives the secondary driving gear 610 to rotate, and the secondary driving gear 610 drives the secondary passive gear 620 to rotate through meshing, and transmits the torque to the differential 70, and the differential 70 drives the wheels to rotate through the left and right drive shafts.

[0043] Furthermore, when the gear sleeve 510 is in the working position meshing with the second gear 420, as shown in FIG. Figure 3 As shown, the electric drive assembly is in a low-speed gear state. At this time, the torque transmission path is that the motor shaft 110 transmits torque to the primary driving gear 210, and the primary driving gear 210 transmits torque to the primary passive gear 220 through meshing, and the primary passive gear 220 can drive the sun gear 310 fixedly connected thereto to rotate, and the sun gear 310 drives the planetary carrier 320 to rotate through the planetary gear 330, and the planetary carrier 320 can drive the second gear gear 420 fixedly connected thereto to operate, and the second gear gear 420 drives the synchronous coupling tooth 530 to rotate under the meshing action of the synchronizer 50, thereby driving the secondary driving gear 610 to rotate, and the secondary driving gear 610 drives the secondary passive gear 620 to rotate through meshing, and transmits the torque to the differential 70 to achieve low-speed operation.

[0044] Furthermore, when the gear sleeve 510 is in a working position disengaged from the first gear position gear 410 and the second gear position gear 420 , the electric drive assembly operates in neutral, and the motor is completely disengaged from the wheels.

[0045] It should be noted that bearing holes are machined at both ends of the sun gear 310, and the first bearing 80 is assembled in the bearing hole to realize the relative rotation of the sun gear 310 and the secondary driving gear 610. As a core component, the sun gear 310 can not only mesh the planetary gear 330 through the middle gear after receiving the torque of the primary passive gear 220, but also drive the planetary carrier 320 through the planetary gear 330 to transmit the torque to the second gear 420. It can also directly drive the first gear 410 through the spline at one end to transmit the torque to the gear sleeve 510. That is, in the electric drive assembly provided in the embodiment of the present invention, the sun gear 310 can be used as a torque transmission component in the transmission system, and can also be used as a speed reduction adjustment component in the gear system, thereby improving the compactness of the overall structure.

[0046] In addition, in the electric drive assembly provided in the embodiment of the present invention, the drive motor 10 is a coaxial motor, the motor shaft 110 is a hollow structure, and the drive shaft can coaxially pass through the motor shaft 110 and be connected to the wheel. The coaxial motor can integrate the motor shaft 110 of the motor and the drive shaft of the reducer on the same axis, which can reduce the radial and axial dimensions, making the entire electric drive assembly more compact, which is conducive to layout in a limited space, and is particularly suitable for electric vehicle design with limited space.

[0047] It should be noted that in the electric drive assembly provided in the embodiment of the present invention, the outer ring of the gear sleeve 510 is also designed with a groove, and the shift fork is inserted into the groove for assembly, so that the shift fork can push the gear sleeve 510 to slide along its axial direction and realize the engagement of the gear sleeve 510 with gears of different gear positions to achieve shift adjustment.

[0048] It should be further explained that an embodiment of the present invention further provides a vehicle, which includes the electric drive assembly provided by any of the above embodiments. Since the electric drive assembly has the above technical effects, the vehicle provided by the embodiment of the present invention also has the above technical effects, which will not be repeated herein.

[0049] It should be noted that, for the convenience of description, only the parts related to the invention are shown in the drawings. In the absence of conflict, the embodiments of the present invention and the features in the embodiments can be combined with each other.

[0050] As shown in the present invention and claims, unless the context clearly indicates an exception, the words "a", "an", "a kind" and / or "the" do not specifically refer to the singular, but may also include the plural. Generally speaking, the terms "include" and "comprise" only indicate the inclusion of clearly identified steps and elements, and these steps and elements do not constitute an exclusive list, and the method or device may also include other steps or elements. The elements defined by the sentence "includes a..." do not exclude the existence of other identical elements in the process, method, commodity or device that includes the elements.

[0051] In the following, the terms "first", "second", "third", etc. are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features.

[0052] The above description is only a preferred embodiment of the present invention and an explanation of the technical principles used, and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. The scope of the invention involved in the present invention is not limited to the technical solution formed by a specific combination of the above-mentioned technical features, but also should cover other technical solutions formed by any combination of the above-mentioned technical features or their equivalent features without departing from the above-mentioned inventive concept. For example, the above-mentioned features are replaced with the technical features with similar functions disclosed in the present invention (but not limited to) to form a technical solution.

Claims

1. An electric drive assembly, characterized in that: include: A drive motor, wherein the outer periphery of the motor shaft of the drive motor is transmission-connected with a first gear set, the first gear set is transmission-connected with a planetary gear train to transmit torque to a sun gear in the planetary gear train, one end of the sun gear is splined with a first gear; one end of a planet carrier in the planetary gear train that is transmission-connected with the sun gear is fixedly connected with a second gear; A synchronizer includes a gear sleeve and a gear ring, wherein the gear sleeve is axially slidably arranged on the gear ring, and the sliding path of the gear sleeve includes at least three working positions, and the three working positions of the gear sleeve are respectively engaged with the first gear position gear, engaged with the second gear position gear, and disengaged from the first gear position gear and the second gear position gear; the gear sleeve is drivingly connected to the second gear set, and the second gear set is drivingly connected to the differential.

2. The electric drive assembly according to claim 1, characterized in that: The synchronizer also includes synchronous coupling teeth. The internal spline of the gear sleeve is arranged in three sections along its axial direction. The first section is a complete internal spline and meshes with the synchronous coupling teeth gap. The second section is a concave avoidance structure. The third section is an engaging tooth structure and is used to mesh with the coupling teeth on the first gear position gear or the second gear position gear. The synchronizer is meshed with the second gear set for transmission through the synchronous coupling teeth.

3. The electric drive assembly according to claim 2, characterized in that: When the gear sleeve is disengaged from the first gear gear and the second gear gear, the third section is located between the first gear gear and the second gear gear in the axial direction.

4. The electric drive assembly according to claim 1, characterized in that: The first gear set includes a first-stage driving gear and a first-stage passive gear that are meshed with each other. The first-stage driving gear is connected to the external splines of the motor shaft via internal splines, and the first-stage passive gear is fixed to the sun gear by welding.

5. The electric drive assembly according to claim 2, characterized in that: The second gear set includes a secondary driving gear and a secondary driven gear that are meshed with each other. The secondary driving gear is meshed with the synchronous combination gear, and the secondary driven gear is fixed on the differential to drive the differential to rotate.

6. The electric drive assembly according to claim 5, characterized in that: The sun gear and the secondary driving gear are nested and arranged to rotate relative to each other through at least two sets of first bearings arranged at intervals.

7. The electric drive assembly according to claim 1, characterized in that: The planetary gear system also includes three planetary gears, which are meshed with the sun gear and evenly arranged along the circumference of the sun gear. The outer circumference of the planetary gear is meshed with an inner gear ring, and the planetary gear is connected to the planet carrier through a second bearing.

8. The electric drive assembly according to claim 1, characterized in that: The driving motor is a coaxial motor, and the motor shaft is a hollow structure.

9. The electric drive assembly according to claim 1, characterized in that: The outer ring of the gear sleeve is designed with a groove, and the shift fork is inserted into the groove to push the gear sleeve to slide along its axial direction.

10. A vehicle, characterized in that: The invention comprises the electric drive assembly as claimed in any one of claims 1 to 9.

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