Sun gear connection structure, planetary reducer and motor having the same

Abstract

The present invention relates to the field of motor technology, and in particular to a sun gear connection structure, a planetary reducer, and a motor having such a structure. The structure comprises a first mounting wheel having an annular groove with a plurality of internal teeth extending axially therein; and a second mounting wheel having a smaller diameter than the first mounting wheel, the second mounting wheel having a plurality of external teeth extending axially therein on its outer circumference, the internal teeth of the first mounting wheel meshing with the external teeth of the second mounting wheel, the first mounting wheel and the second mounting wheel being coaxially connected to either the sun gear or the input shaft, respectively. The present invention provides a toothed floating connection between the sun gear and the input shaft to achieve stable power transmission in the case of multi-axis alignment; and provides an adjustment assembly to achieve switching between the input shaft and the two sun gears.

Description

Technical Field

[0001] The present invention relates to the technical field of motors, in particular to a sun gear connection structure, a planetary reducer and a motor having the structure. Background Art

[0002] With rapid economic development, cars have become an essential means of transportation, leading to the rapid development of new energy vehicles. New energy vehicles are generally powered by electric motors. For new energy trucks that need to carry heavy loads, conventional electric motors can cause a sense of sluggishness when starting due to the vehicle's own weight and the weight of the cargo.

[0003] Existing technologies utilize planetary reducers to increase motor output torque. These are common planetary gear transmissions that transmit the motor's original shaft through the planetary reducer to generate high torque. In engineering, planetary gear transmissions offer advantages such as compact design, low mass, and high load capacity.

[0004] These advantages are achieved by utilizing multiple planetary gears in its layout, fully utilizing the space between coaxial gears, using multiple planetary gears to share the load and form power flow, and rationally adopting internal meshing transmission. However, this is only the ideal situation. In actual applications, due to machining and assembly errors, the load distribution on each planetary gear during the transmission process is uneven, resulting in the load being concentrated on one planetary gear.

[0005] This phenomenon can be referred to Figure 1 Explanation: Due to the processing and assembly process, there are errors in the tooth clearance at the meshing point between the sun gear and each set of planetary gears, and the clearance values ​​are different; when the sun gear is used as the power wheel input, the sun gear will first fully mesh with the teeth of at least one set of planetary gears (that is, the tooth clearance is 0), and the planetary carrier can be driven by pushing this set of planetary gears. At this time, the teeth of most other sets of planetary gears and the sun gear are still partially in contact or even not in contact at all (which can be regarded as the tooth clearance is greater than or equal to 0), that is, "the load will be concentrated on the planetary gear with a tooth clearance of 0".

[0006] In this way, the advantages of planetary gears cannot be brought into play, and they are even inferior to ordinary external transmission layouts. Summary of the Invention

[0007] Some simplifications or omissions may be made in this section and the abstract and title of the present application to avoid obscuring the purpose of this section, the abstract and the title of the invention, and such simplifications or omissions shall not be used to limit the scope of the invention.

[0008] The present invention is proposed in view of the problem of uneven load distribution caused by processing and assembly in the above or existing technologies.

[0009] Therefore, one of the objects of the present invention is to provide a sun gear connection structure.

[0010] In order to achieve the above objectives, the present invention adopts the following technical solutions: a sun gear connection structure, comprising:

[0011] a first mounting wheel having an annular groove with a plurality of internal teeth extending in the axial direction; and

[0012] a second mounting wheel having a diameter smaller than that of said first mounting wheel,

[0013] The second mounting wheel has a plurality of external teeth extending in the axial direction on the outer peripheral surface.

[0014] The inner teeth of the first mounting wheel mesh with the outer teeth of the second mounting wheel,

[0015] The first mounting wheel and the second mounting wheel are respectively coaxially connected to one of the sun wheel and the input shaft.

[0016] As a preferred solution of the sun gear connection structure of the present invention, wherein: the sun gear is provided with two,

[0017] Each of the sun gears is coaxially embedded with a first mounting wheel.

[0018] The second mounting wheel is provided on the surface of the input shaft;

[0019] The sun gear connection structure further includes:

[0020] An adjustment assembly, wherein the second mounting wheel selectively engages with at least one of the two first mounting wheels through the adjustment assembly.

[0021] As a preferred solution of the sun gear connection structure of the present invention, wherein: the radial cross-sectional dimensions of the two first mounting wheels are the same and the rotation centers are coaxial,

[0022] The multiple internal teeth located on the two first mounting wheels are kept aligned in the axial direction;

[0023] The second mounting wheel is connected to the surface of the input shaft in an axial sliding manner.

[0024] The adjustment assembly includes a pushing portion for driving the second mounting wheel to move along the axial direction of the input shaft.

[0025] As a preferred solution of the sun gear connection structure described in the present invention, the pushing part includes a magnetic part arranged on one side of the second mounting wheel, an electromagnet fixedly arranged outside the end of the input shaft and adapted to the magnetic part, and a non-magnetic spring arranged between the magnetic part and the electromagnet.

[0026] As a preferred solution of the sun gear connection structure of the present invention, wherein: the adjustment assembly includes two limit blocks spaced apart and distributed on the surface of the input shaft, for limiting the maximum slip distance of the second mounting wheel;

[0027] When the second mounting wheel moves to any limit block, the second mounting wheel only engages with one of the two first mounting wheels;

[0028] There is at least one position X between the two limit blocks. When the second mounting wheel moves to the position X, the second mounting wheel engages with the two first mounting wheels at the same time.

[0029] As a preferred solution of the sun gear connection structure of the present invention, the tooth width D3 of the external teeth is not less than the tooth width D4 of the internal teeth of any one of the first mounting wheels.

[0030] As a preferred solution of the sun gear connection structure of the present invention, the tooth width D3 of the external teeth is not less than the sum of the tooth widths D4 of the internal teeth of the two first mounting wheels.

[0031] The beneficial effects of a sun gear connection structure of the present invention: the present invention stably transmits power in the case of multi-axis alignment by setting a toothed floating connection between the sun gear and the input shaft; and realizes switching coordination between the input shaft and the two sun gears by setting an adjustment component.

[0032] In actual use, there is still a problem that the load is easily concentrated on one planetary gear.

[0033] Therefore, a second object of the present invention is to provide a planetary reducer.

[0034] In order to solve the above technical problems, the present invention provides the following technical solutions: a planetary reducer, comprising the above sun gear connection structure, further comprising:

[0035] An input shaft rotates at a first speed before deceleration about a central axis;

[0036] a sun gear connected to the input shaft via the sun gear connection structure;

[0037] At least two planetary gears, which are radially outside the sun gear and mesh with the sun gear through helical teeth,

[0038] an annular internal gear meshing with each planet gear on a radially outer side of each planet gear;

[0039] A planet carrier, comprising connecting rods coaxially connected to the planetary gears, and connecting plates connected to the connecting rods;

[0040] When the internal gear is fixed, the connecting plate rotates relative to the input shaft at a second, reduced speed; and

[0041] The calibration component is arranged between the planet carrier and each planet gear, and is used to adjust the meshing clearance of the helical teeth between each planet gear and the sun gear to be the same.

[0042] As a preferred solution of the planetary reducer of the present invention, the calibration component includes a driving part for driving the planetary gear to move axially along the connecting rod.

[0043] As a preferred solution of the planetary reducer of the present invention, the tooth width D1 of the sun gear is greater than the tooth width D2 of the planet gear.

[0044] Furthermore, the difference between the tooth width D1 and the tooth width D2 is not less than the maximum meshing clearance of the helical teeth between the planetary gear and the sun gear.

[0045] As a preferred solution of the planetary reducer of the present invention, wherein: the calibration component further includes a pressure sensor provided at the connection between the planetary gear and the connecting rod;

[0046] The pressure collection point of the pressure sensor is arranged on a side opposite to the moving direction of the planetary gear.

[0047] As a preferred solution of the planetary reducer of the present invention, wherein: the connecting rod is a telescopic rod, comprising a movable section supporting the planetary gear, and a fixed section fixedly connected to the connecting plate;

[0048] The driving portion is used to drive the moving section to move relative to the fixed section along the axial direction of the connecting rod.

[0049] As a preferred solution of the planetary reducer of the present invention, wherein: the moving section and the fixed section do not rotate relative to each other;

[0050] The driving part includes a calibration rod rotatably connected to the fixed section, and the calibration rod is connected to the movable section via a thread.

[0051] Beneficial effects of a planetary reducer of the present invention: The present invention solves the problem that the load is easily concentrated on one planetary wheel by cooperating between the planetary reducer and the calibration component, and facilitates fine calibration by setting a pressure sensor.

[0052] Based on the same inventive concept, the third object of the present invention is to provide a motor.

[0053] In order to solve the technical problem, the present invention provides the following technical solution: a motor, comprising the planetary reducer, and further comprising:

[0054] A housing having a first mounting cavity and a second mounting cavity separated from each other, wherein the first mounting cavity is used to accommodate the planetary reducer;

[0055] a motor body mounted in the second mounting cavity, comprising a rotor assembly driving the input shaft, wherein the input shaft extends from the second mounting cavity into the first mounting cavity and is connected to the sun gear; and

[0056] The output shaft is coaxially connected to the connecting plate and extends outside the housing, and rotates at a second, reduced speed relative to the input shaft.

[0057] As a preferred solution of the motor of the present invention, the planetary reducer is provided with two groups,

[0058] The two sets of planetary reducers have the same input shaft.

[0059] The sun gears of the two sets of planetary reducers are connected to the input shaft via the sun gear connection structure.

[0060] The two sets of planetary reducers have the same number of planetary gears and are coaxially connected in pairs.

[0061] The two sets of planetary reducers have the same set of planet carriers.

[0062] The beneficial effect of the motor of the present invention is that by providing a motor with two sets of planetary reducers, a large torque output is achieved, and the load of the planetary gear is evenly distributed when the motor rotates forward and reverse. BRIEF DESCRIPTION OF THE DRAWINGS

[0063] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the description of the embodiments. 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 any creative work.

[0064] Figure 1 This is a schematic diagram of the prior art where load is concentrated on a single planetary gear.

[0065] Figure 2 This is a schematic structural diagram of one embodiment of the sun gear connection structure after installation in Example 1 of the present invention.

[0066] Figure 3 This is a structural diagram of one embodiment of the sun gear connection structure in Example 1 of the present invention before installation.

[0067] Figure 4 This is a structural diagram of another embodiment of the sun gear connection structure in Example 1 of the present invention before installation.

[0068] Figure 5 Schematic diagram of the three-dimensional structure of the sun gear connection structure in Example 2 of the present invention.

[0069] Figure 6 Schematic diagram of the cross-sectional structure of the sun gear connection structure in embodiments 2 and 6 of the present invention when the input shaft rotates in the forward direction at a low speed.

[0070] Figure 7 Schematic diagram of the cross-sectional structure of the sun gear connection structure in embodiments 2 and 6 of the present invention when the input shaft rotates in the reverse direction at a low speed.

[0071] Figure 8 Schematic diagram of the cross-sectional structure of the sun gear connection structure in embodiments 2 and 6 of the present invention when the input shaft rotates at high speed.

[0072] Figure 9 Schematic diagram of the internal structure of the sun gear connection structure in Example 2 of the present invention.

[0073] Figure 10 Schematic diagram of the three-dimensional structure of the planetary reducer in Examples 3 and 4 of the present invention.

[0074] Figure 11 This is a side structural schematic diagram of the planetary reducer in Examples 3 and 4 of the present invention.

[0075] Figure 12 For the present invention Figure 11 Schematic diagram of the cross-sectional structure in direction A is shown.

[0076] Figure 13 For the present invention Figure 12 An enlarged schematic diagram of the structure at point B is shown.

[0077] Figure 14 Schematic diagram of the three-dimensional structure of a single planetary gear and a sun gear in embodiments 3 and 4 of the present invention.

[0078] Figure 15 This is a side view structural diagram of the cooperation between multiple planetary gears and the sun gear in Examples 3 and 4 of the present invention.

[0079] Figure 16 For the present invention Figure 15 Schematic diagram of the cross-sectional structure from the perspective shown.

[0080] Figure 17 Schematic diagram of the three-dimensional structure of the motor in Examples 5 and 6 of the present invention.

[0081] Figure 18Schematic diagram of the side structure of the motor in Examples 5 and 6 of the present invention.

[0082] Figure 19 For the present invention Figure 18 Schematic diagram of the cross-sectional structure in the C direction is shown.

[0083] Figure 20 Schematic diagram of the installation structure of the planetary gear in Example 6 of the present invention.

[0084] Figure 21 For the present invention Figure 20 Schematic diagram of the front view structure.

[0085] Figure 22 For the present invention Figure 21 Schematic diagram of the cross-sectional structure in direction E is shown.

[0086] In the figure: 100, sun gear connection structure; 101, first mounting wheel; 101a, internal teeth; 102, second mounting wheel; 102a, external teeth; 200, planetary reducer; 201, input shaft; 202, sun gear; 203, planetary gear; 204, internal gear; 205, planetary carrier; 205a, connecting rod; 205a-1, moving section; 205a-2, fixed section; 205a-3, sliding rod; 205b, connecting plate; 300, calibration assembly; 301, driving part; 301a, calibration rod; 302, pressure sensor; 500, housing; 501, first mounting cavity; 502, second mounting cavity; 600, output shaft; 700, adjustment assembly; 701, pushing part; 701a, magnetic part; 701b, electromagnet; 701c, non-magnetic spring; 702, limit block. DETAILED DESCRIPTION

[0087] In order to make the objects, features and advantages of the present invention more obvious and easy to understand, the specific embodiments of the present invention are described in detail below with reference to the accompanying drawings.

[0088] In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Those skilled in the art may make similar generalizations without violating the connotation of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0089] Secondly, the term "one embodiment" or "embodiment" herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation of the present invention. The phrase "in one embodiment" appearing in various places throughout this specification does not necessarily refer to the same embodiment, nor does it refer to a separate or selective embodiment that is mutually exclusive of other embodiments.

[0090] Example 1

[0091] Reference Figure 2-Figure 4 , which is the first embodiment of the present invention, provides a sun gear connection structure 100, which can compensate for the comprehensive displacement through the tooth connection, realize the floating of the sun gear 202, and then evenly distribute the load on the planetary gear 203 during the transmission process, which includes: a first mounting wheel 101 and a second mounting wheel 102.

[0092] Specifically, the first mounting wheel 101 has an annular groove with a plurality of internal teeth 101a extending axially therein. The center of the groove is coaxial with the rotation center of the first mounting wheel 101. The groove may be formed by an inward depression in the side surface of the first mounting wheel 101. The plurality of internal teeth 101a are distributed in an annular array within the annular groove.

[0093] Furthermore, the diameter of the second mounting wheel 102 is smaller than that of the first mounting wheel 101. The second mounting wheel 102 has a plurality of external teeth 102a extending axially on its outer circumference. The plurality of external teeth 102a are arranged in a circular array around the rotation center of the second mounting wheel 102. The internal teeth 101a of the first mounting wheel 101 mesh with the external teeth 102a of the second mounting wheel 102. In other words, the smaller-diameter second mounting wheel 102 meshes with the internal teeth 101a of the larger-diameter first mounting wheel 101 via the external teeth 102a.

[0094] The first mounting wheel 101 and the second mounting wheel 102 are each coaxially connected to either the sun gear 202 or the input shaft 201. In one embodiment, the larger-diameter first mounting wheel 101 is coaxially connected to the input shaft 201, while the smaller-diameter second mounting wheel 102 is coaxially connected to the sun gear 202. When the input shaft 201 rotates, the sun gear 202 rotates along with the first mounting wheel 101 via the second mounting wheel 102. The sun gear 202 and the input shaft 201 are connected via a gear structure, allowing the sun gear 202 to float relative to the input shaft 201.

[0095] In another embodiment, a large-diameter first mounting wheel 101 is coaxially connected to the sun gear 202, and a small-diameter second mounting wheel 102 is coaxially connected to the input shaft 201, which can also achieve floating of the sun gear 202 relative to the input shaft 201. A groove is provided through the first mounting wheel 101, and both the input shaft 201 and the second mounting wheel 102 can pass through the groove.

[0096] In summary, by setting up a toothed connection structure between the sun gear 202 and the input shaft 201, it is not only convenient for docking and installation, but also has the characteristics of floating and compensating displacement, and can stably transmit power under multi-axis alignment, thereby solving the problem of uneven load distribution caused by the processing and assembly process.

[0097] Example 2

[0098] Reference Figure 5-Figure 9 , which is the second embodiment of the present invention. Different from the previous embodiment, this embodiment provides an adjustment component 700 to solve the problem of switching and matching between the input shaft 201 and the two sun gears 202.

[0099] Specifically, two sun gears 202 are provided, and each sun gear 202 has a first mounting wheel 101 coaxially embedded therein. The second mounting wheel 102 is provided on the surface of the input shaft 201. The second mounting wheel 102 can engage with any one of the two first mounting wheels 101, and thus the input shaft 201 can cooperate with different sun gears 202 for transmission.

[0100] Furthermore, the second mounting wheel 102 selectively engages with at least one of the two first mounting wheels 101 via an adjustment assembly 700. The adjustment assembly 700 has a control and adjustment function, which can move the second mounting wheel 102 to engage with one of the two first mounting wheels 101 or simultaneously engage the second mounting wheel 102 with both first mounting wheels 101.

[0101] Furthermore, the two first mounting wheels 101 have the same radial cross-sectional dimensions, meaning that the structures of the two first mounting wheels 101 are identical except for the tooth width D4 of the internal teeth 101a. The two first mounting wheels 101 are coaxially arranged about the center of rotation, and the multiple internal teeth 101a on the two first mounting wheels 101 are axially aligned. In other words, the axial deflection angle of the two first mounting wheels 101 is zero. The second mounting wheel 102 is axially slidably connected to the surface of the input shaft 201. When the external teeth 102a of the second mounting wheel 102 mesh with the internal teeth 101a of either first mounting wheel 101, since the two first mounting wheels 101 remain aligned, the second mounting wheel 102 will axially slide to the other first mounting wheel 101 and mesh with the internal teeth 101a of that first mounting wheel 101.

[0102] Among them, the adjustment component 700 includes a pushing part 701 for driving the second mounting wheel 102 to move axially along the input shaft 201. The movement of the second mounting wheel 102 is controlled by the pushing part 701. The pushing part 701 can be set as an electric telescopic rod, or other methods that can realize the axial displacement of the second mounting wheel 102.

[0103] In this embodiment, the pushing part 701 includes a magnetic part 701a arranged on one side of the second mounting wheel 102, an electromagnet 701b fixedly arranged outside the end of the input shaft 201 and adapted to the magnetic part 701a, and a non-magnetic spring 701c arranged between the magnetic part 701a and the electromagnet 701b. The electromagnet 701b is relatively fixed, the non-magnetic spring 701c and the electromagnet 701b do not rotate relative to each other, and the non-magnetic spring 701c and the magnetic part 701a are rotatably connected through a bearing (in order to facilitate the display of core details, the existing bearing and input shaft drive structure are simplified in the figure). In this way, the non-magnetic spring 701c does not rotate when the magnetic part 701a rotates. After the electromagnet 701b generates magnetic force, it only satisfies the movement of the magnetic part 701a toward the electromagnet 701b. The second mounting wheel 102 is fixedly connected to the magnetic part 701a. After the electromagnet 701b is energized, it can generate magnetic attraction to the magnetic part 701a. The magnitude of the magnetic force can be adjusted by controlling the voltage applied to the electromagnet 701b.

[0104] When the magnetic force of the electromagnet 701b on the magnetic part 701a is 0, the second mounting wheel 102 and the magnetic part 701a remain away from the side of the electromagnet 701b under the elastic force of the non-magnetic spring 701c, so that the second mounting wheel 102 can engage with a first mounting wheel 101 away from the electromagnet 701b; and after the voltage applied to the electromagnet 701b is increased, the magnetic force of the electromagnet 701b on the magnetic part 701a is increased, and the magnetic part 701a is attracted by the magnetic force and drives the second mounting wheel 102 to move axially toward the electromagnet 701b until the elastic force of the non-magnetic spring 701c is increased after deformation to offset the magnetic force given by the electromagnet 701b, and a new equilibrium position is reached; similarly, after the magnetic force of the electromagnet 701b is weakened, the second mounting wheel 102 can move in the opposite direction under the elastic force of the non-magnetic spring 701c. By controlling the magnitude of the magnetic force generated by the electromagnet 701 b , the axial displacement of the second mounting wheel 102 can be precisely controlled, thereby achieving the matching mode of the second mounting wheel 102 with the two first mounting wheels 101 .

[0105] The rest of the structure is the same as that of Example 1.

[0106] In summary, by providing the adjustment assembly 700 , the switching and coordination between the input shaft 201 and the two sun gears 202 can be controlled.

[0107] Example 3

[0108] Reference Figures 10-16 , which is the third embodiment of the present invention. Different from the previous embodiment, this embodiment provides a planetary reducer 200, which solves the problem that the load is easily concentrated on one planetary gear.

[0109] Specifically, the planetary reducer 200 includes an input shaft 201, a sun gear 202, planetary gears 203, an internal gear 204, and a planet carrier 205. Planetary transmission systems are flexible and diverse, with six possible combinations of motion modes, three of which are specifically designed to achieve speed reduction. For example, the sun gear 202 is fixed, the internal gear 204 is the active element, and the planet carrier 205 is the passive element. In this case, the speed is reduced and the direction of rotation is the same. Alternatively, the internal gear 204 is fixed, the sun gear 202 is the active element, and the planet carrier 205 is the passive element. In this case, the speed is reduced and the direction of rotation is the same. Furthermore, the planet carrier 205 is fixed, the sun gear 202 is the active element, and the internal gear 204 is the passive element. In this case, the speed is reduced and the direction of rotation is the opposite.

[0110] In this embodiment, the internal gear 204 is fixed and set to a circular ring shape, which is engaged with each planet gear 203 on the radial outside of each planet gear 203. The sun gear 202 is connected to the input shaft 201 through the sun gear connection structure 100. The input shaft 201 rotates at a first speed before deceleration with the central axis as the center. At least two planet gears 203 are provided, which are engaged with the sun gear 202 through helical teeth on the radial outside of the sun gear 202. Compared with straight teeth, helical teeth with the same tooth width have a larger contact area during engagement, which is beneficial for sharing the load.

[0111] Among them, the planet carrier 205 includes a connecting rod 205a coaxially connected to each planet gear 203, and a connecting plate 205b connected to each connecting rod 205a. Each planet gear 203 is connected to the connecting plate 205b through each connecting rod 205a. Since the internal gear 204 is fixed, the sun gear 202 is connected to the input shaft 201 through the sun gear connecting structure 100. When the input shaft 201 rotates at the first speed before deceleration, the sun gear 202 rotates accordingly. The sun gear 202 drives the planet gears 203 to rotate through meshing. While the planet gears 203 rotate, they revolve around the rotation center of the sun gear 202 under the action of the internal gear 204, and then the connecting plate 205b connected to the planet gears 203 rotates at the second speed after deceleration relative to the input shaft 201.

[0112] Furthermore, a calibration assembly 300 is provided between the planet carrier 205 and each planet gear 203 to ensure that the meshing clearance between each planet gear 203 and the sun gear 202 is uniform. When multiple planet gears 203 are meshed with the sun gear 202, the tooth gaps at the meshing locations are typically slightly larger than the tooth thickness during machining or assembly to facilitate assembly. However, due to errors during machining or assembly, the meshing clearances between the planet gears 203 and the sun gear 202 often vary in size after the multiple planet gears 203 are assembled and meshed. This can easily cause the planet gears 203 with smaller tooth gaps to receive greater load, leading to uneven load distribution. Therefore, by setting up the calibration component 300, in the direction of rotation of the sun gear 202, there is a surface of the teeth of the planetary gears 203 that is thrusted by the teeth of the sun gear 202, and the tooth clearance difference of the force-bearing surface at the meshing point between each planetary gear 203 and the sun gear 202 is adjusted to 0. Since the gear teeth are distributed in an annular array, when the planetary gears 203 and the sun gear 202 rotate and mesh, the tooth clearance of each planetary gear 203 and the sun gear 202 will remain relatively consistent at any angle, thereby solving the problem of uneven load distribution on each planetary gear 203, which causes the load to be easily concentrated on one planetary gear 203. Figure 13 、 14 , 16, the rotation direction of the sun gear 202 is L, then the planet gear 203 is calibrated and adjusted in the direction of M, so that the helical teeth of the planet gear 203 are close to the helical tooth surface N of the sun gear 202 to generate contact pressure,

[0113] The calibration assembly 300 includes a drive unit 301 for driving the planetary gears 203 to move axially along the connecting rod 205a. In this embodiment, the planetary gears 203 and the sun gear 202 are engaged by helical teeth. The teeth of the helical gears are spirally arranged relative to the center of rotation. The meshing helical gears have the same helix angle, thus allowing the tooth clearance of the two helical gears to be adjusted by axial movement. In this embodiment, the sun gear 202 is fixed in position. The drive unit 301 drives the planetary gears 203 to move axially along the connecting rod 205a, thereby causing the planetary gears 203 and sun gear 202 to move relative to each other in the axial direction, achieving the desired tooth clearance between them. The drive unit 301 can be automatically controlled, such as with an electric telescopic rod, which has the advantage of being easily adjustable at any time after assembly. Alternatively, it can be manually controlled, requiring only calibration of the tooth clearance between each planetary gear 203 and sun gear 202 during assembly. The calibration values ​​at the time of assembly are maintained during subsequent use, with disassembly and recalibration only required when necessary.

[0114] Preferably, the tooth width D1 of sun gear 202 is larger than the tooth width D2 of planet gear 203. During assembly, the teeth of planet gear 203 are assembled until they fully contact the teeth of sun gear 202. That is, the overlap range of the tooth widths at the meshing point between planet gear 203 and sun gear 202 is the tooth width D2 of planet gear 203. This allows the teeth of planet gear 203 to fully withstand the force applied by sun gear 202, facilitating even load distribution. In one rotational direction of sun gear 202, the clearance between the force-bearing surfaces at the meshing point between planet gear 203 and sun gear 202 can be reduced simply by moving planet gear 203 in the specified direction. Therefore, the difference between tooth width D1 and tooth width D2 can be set to be no less than the maximum meshing clearance of the helical teeth between planet gear 203 and sun gear 202, ensuring that the teeth of planet gear 203 can fully withstand the force applied by sun gear 202 throughout the entire adjustment range.

[0115] The rest of the structure is the same as that of Example 2.

[0116] In summary, by setting up the planetary reducer 200 and the calibration component 300 for use in conjunction, the tooth clearance difference at the meshing point of each planetary gear 203 and the sun gear 202 is uniformly calibrated, which solves the problem that the load is easily concentrated on one planetary gear 203.

[0117] Example 4

[0118] Reference Figures 10-16 , which is the fourth embodiment of the present invention. Unlike the previous embodiment, this embodiment provides a pressure sensor 302, which facilitates adjusting the tooth clearance at the meshing point between each planetary gear 203 and the sun gear 202 to the same value. The pressure sensor 302 is a sensor in the prior art that can sense pressure and convert it into an electrical signal output. It is widely used in industrial automation, automotive electronics, medical equipment, aerospace and other fields. It converts pressure changes into electrical signals through pressure sensing elements, and then converts them into readable pressure values. According to the working principle or structure, it can be divided into resistive, capacitive, piezoelectric pressure sensors, etc. By setting the pressure sensing element at the pressure collection point, the force at the collection point can be read.

[0119] In this embodiment, the pressure sensor 302 is used to detect the contact pressure between each planetary gear 203 and the sun gear 202. Since it is difficult to visually distinguish the size of the tooth gap at the meshing point of the planetary gear 203 and the sun gear 202 during calibration, in this embodiment, the tooth gap value of each planetary gear 203 is uniformly set to 0 during calibration, that is, the teeth of the planetary gear 203 are pushed to contact the teeth of the sun gear 202; however, although the naked eye can distinguish that the two are in contact, there may be differences in the contact pressure value between the two depending on the degree of compression, which will also cause uneven load distribution on each planetary gear 203 when the sun gear 202 rotates at high speed. The contact pressure value of each planetary gear 203 and the sun gear 202 is measured by the pressure sensor 302 and adjusted to a uniform value. The specific contact pressure value needs to be determined according to the specific application scenario, gear material, lubrication conditions and gear geometric parameters.

[0120] Specifically, when the planetary gear 203 is blocked by the sun gear 202, the planetary gear 203 is subjected to a reaction force, which in turn applies a force to the connecting rod 205a. This force value can be regarded as the contact pressure value. Therefore, it is necessary to set the pressure collection point of the pressure sensor 302 at the connection between the planetary gear 203 and the connecting rod 205a.

[0121] The pressure sensor 302's pressure collection point is located opposite the direction of movement of the planetary gear 203. According to force analysis, as the planetary gear 203 moves from its starting point toward its end point, generating contact pressure with the sun gear 202, the force exerted by the planetary gear 203 on the connecting rod 205a is directed toward the starting point. In this embodiment, the planetary gear 203 is mounted on the surface of the connecting rod 205a via a bearing. The connecting rod 205a has at least two retaining spring grooves, and the bearing is mounted between the two retaining spring grooves and secured by the retaining spring. The pressure sensor 302 collects the force applied to the retaining spring on the corresponding side.

[0122] Furthermore, the connecting rod 205a is a telescopic rod, comprising a movable section 205a-1 that supports the planetary gear 203, and a fixed section 205a-2 fixedly connected to the connecting plate 205b. The driving unit 301 is used to drive the movable section 205a-1 to move axially relative to the fixed section 205a-2 along the connecting rod 205a. Similarly, the telescopic rod can be configured as an electric telescopic rod, with the displacement of the movable section 205a-1 relative to the fixed section 205a-2 controlled by a program.

[0123] Preferably, in this embodiment, the movable segment 205a-1 and the fixed segment 205a-2 are arranged so as not to rotate relative to each other. For example, an axial guide groove is provided on one side of the movable segment 205a-1, and a guide block is provided on one side of the fixed segment 205a-2 to match the guide groove. The guide groove and the guide block can also be arranged in opposite directions. The driving unit 301 includes a calibration rod 301a rotatably connected to the fixed segment 205a-2. The calibration rod 301a is connected to the movable segment 205a-1 via a threaded connection. When calibration is required, the calibration rod 301a is rotated. Since there is no axial displacement between the calibration rod 301a and the fixed section 205a-2, and the moving section 205a-1 and the fixed section 205a-2 do not rotate relative to each other, the rotation of the calibration rod 301a will cause the threaded sliding between the moving section 205a-1, thereby driving the moving section 205a-1 to move axially, and the planetary gear 203 moves with the moving section 205a-1. As the planetary gear 203 moves relative to the sun gear 202, the contact pressure value between the two can be obtained in real time through the pressure sensor 302 until the numerical values ​​of each pressure sensor 302 are the same and meet the set contact pressure value, and the adjustment process is completed.

[0124] The rest of the structure is the same as that of Example 3.

[0125] Example 5

[0126] Reference Figure 17-18 , which is the fifth embodiment of the present invention. Different from the previous embodiment, this embodiment provides a motor, which includes a planetary reducer 200, a housing 500, a motor body and an output shaft 600. The motor body is used to drive the input shaft 201, and includes a stator, a rotor assembly, corresponding bearings and a control module, etc. The housing 500 is used to accommodate the planetary reducer 200 and the motor body. The motor body drives the input shaft 201 to rotate, passes through the planetary reducer 200, and is finally output to the outside through the output shaft 600.

[0127] Specifically, the housing 500 is provided with a first installation cavity 501 and a second installation cavity 502, which are separated from each other. The first installation cavity 501 is used to accommodate the planetary reducer 200. It is worth noting that the first installation cavity 501 and the second installation cavity 502 are formed relative to each other. In this embodiment, the housing 500 is divided into a first housing with an end cover, and a second housing. The second housing is detachably connected to the first housing on a side away from the end cover to facilitate disassembly and maintenance. The first installation cavity 501 for accommodating the planetary reducer 200 is formed between the second housing and the first housing, and the second installation cavity 502 is formed between the first housing and the end cover.

[0128] The motor body is mounted within the second mounting cavity 502 and includes a rotor assembly that drives the input shaft 201. The input shaft 201 extends from the second mounting cavity 502 into the first mounting cavity 501 and connects to the sun gear 202. The output shaft 600 is coaxially connected to the connecting plate 205b and extends outside the housing 500. It rotates at a reduced second speed relative to the input shaft 201.

[0129] Furthermore, the internal gear 204 of the planetary reducer 200 is fixed on the housing 500, and the sun gear 202 and the planetary gear 203 are correspondingly arranged in the inner ring of the internal gear 204. The first and second housings are cast separately through the flange-type housing 500. The internal gear 204 and the housing 500 are separated and fixed together with the first and second housings by bolts and conical pins. The spatial distribution is reasonable and it is convenient to disassemble and repair.

[0130] The rest of the structure is the same as that of Example 4.

[0131] Example 6

[0132] Reference Figures 17-22 , which is the sixth embodiment of the present invention. Unlike the previous embodiment, this embodiment provides two sets of planetary reducers 200, solving the problem of reverse motor drive. Considering that the vehicle's motor needs to rotate in the reverse direction to achieve the reversing requirement, and because the aforementioned calibration component 300 can only ensure that the sun gear 202 and each planet gear 203 maintain the same load in one rotation direction, when the sun gear 202 rotates in the reverse direction, the tooth clearance between the other contact surface of the sun gear 202 and each planet gear 203 can still be guaranteed to be equal if the machining accuracy is high; however, if the machining accuracy is low, the tooth clearance at the meshing point of the sun gear 202 and each planet gear 203 may differ again, and calibration is still required.

[0133] Specifically, two sets of planetary reducers 200 are provided, each responsible for forward and reverse rotation, respectively. The two sets of planetary reducers 200 are calibrated for the corresponding directions. The two sets of planetary reducers 200 share a common input shaft 201. The sun gears 202 of the two sets of planetary reducers 200 are connected to the same input shaft 201 via a sun gear connection structure 100. The input shafts 201 are driven by a common motor body, and the input shafts 201 cooperate with the sun gears 202 of the corresponding set of planetary reducers 200 to drive the rotation.

[0134] The two sets of planetary reducers 200 have the same number of planetary gears 203 and are coaxially connected in pairs. The two sets of planetary reducers 200 have the same set of planet carriers 205 to ensure that they rotate synchronously. The two first mounting wheels 101 are always aligned so that the second mounting wheel 102 can smoothly transition between the two first mounting wheels 101, ensuring that the input shaft 201 can cooperate with different sun gears 202 to achieve output through the same planet carrier 205 and output shaft 600. In this embodiment, Figure 22 The calibration adjustment directions M of the planetary gears 203 on both sides are opposite, and they can be calibrated independently during assembly. The fixed section 205a-2 and the movable section 205a-1 of the connecting rod 205a are each provided with two groups. The two groups of fixed sections 205a-2 are respectively fixed to the connecting plates 205b on both sides by bolts. The two groups of movable sections 205a-1 respectively support the planetary gears 203 of the two groups of planetary reducers 200. The two groups of movable sections 205a-1 are connected by a sliding rod 205a-3, and the two groups of movable sections 205a-1 can slide axially relative to the sliding rod 205a-3.

[0135] Furthermore, the adjustment assembly 700 includes two spaced-apart stoppers 702 disposed on the surface of the input shaft 201, which are used to limit the maximum slippage distance of the second mounting wheel 102. The distance between the two stoppers 702 represents the maximum slippage range of the second mounting wheel 102. To facilitate control, in this embodiment, when the second mounting wheel 102 moves to any of the stoppers 702, the second mounting wheel 102 only engages with one of the two first mounting wheels 101. That is, when the second mounting wheel 102 is at the stoppers 702, the input shaft 201 only drives one of the sun gears 202 to rotate, corresponding to forward and reverse rotation, respectively.

[0136] Furthermore, there is at least one position X between the two stoppers 702. When the second mounting wheel 102 moves to position X, it simultaneously engages with both first mounting wheels 101. That is, when the second mounting wheel 102 is at position X, the input shaft 201 can simultaneously drive both sets of sun gears 202 to rotate, further sharing the load and enabling the corresponding motors to operate at high speeds when the vehicle requires high torque output.

[0137] Among them, the tooth width D3 of the outer teeth 102a is not less than the tooth width D4 of the inner teeth 101a of any first mounting wheel 101, so as to ensure that when the second mounting wheel 102 moves to the position of the limit block 702, the entire inner teeth 101a of the first mounting wheel 101 are kept engaged with the outer teeth 102a of the second mounting wheel 102, thereby maximizing the sharing of the driving load of the sun gear 202 under this condition.

[0138] Preferably, the tooth width D3 of the outer teeth 102a is not less than the sum of the tooth widths D4 of the inner teeth 101a of the two first mounting wheels 101, so as to ensure that when the second mounting wheel 102 moves to position X, the entire inner teeth 101a of the two first mounting wheels 101 are simultaneously engaged with the outer teeth 102a of the second mounting wheel 102, thereby maximizing the sharing of the driving load on the sun gear 202 under this condition, and both sets of sun gears 202 and the corresponding planetary gears 203 participate in load distribution.

[0139] The rest of the structure is the same as that of Example 5.

[0140] Working Principle: The control module of the motor body controls the input shaft 201 to rotate forward and reverse, and at the same time controls the speed of the input shaft 201. The control module of the motor body also adjusts the power supply voltage of the electromagnet 701b. The specific control logic is as follows:

[0141] A speed threshold is set. When the input shaft 201 rotates in the forward direction at a speed lower than the threshold, the magnetic strength of the electromagnet 701b is zero, and the second mounting wheel 102 is stabilized at the limit block 702 away from the electromagnet 701b. At this time, the outer teeth 102a of the second mounting wheel 102 only mesh with the sun gear 202 away from the electromagnet 701b.

[0142] When the input shaft 201 rotates in the reverse direction at a speed lower than the threshold, the magnetic strength of the electromagnet 701b is at its maximum, and the second mounting wheel 102 is stably close to the stopper 702 of the electromagnet 701b. At this time, the outer teeth 102a of the second mounting wheel 102 only mesh with the sun gear 202 close to the electromagnet 701b.

[0143] When the input shaft 201 rotates at a speed not lower than the threshold, the magnetic strength of the electromagnet 701b increases to half, and the second mounting wheel 102 stabilizes at the X position between the two limit blocks 702. At this time, the outer teeth 102a of the second mounting wheel 102 are simultaneously engaged with the sun gear 202.

[0144] In summary, by providing a motor with two sets of planetary reducers 200, a large torque output is achieved, and the load of the planetary gear is evenly distributed when the motor rotates forward and reverse by control.

[0145] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit the present invention. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the spirit and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. A sun gear connection structure (100), characterized in that: include, A first mounting wheel (101) has an annular groove with a plurality of inner teeth (101a) extending in the axial direction; and The second mounting wheel (102) has a diameter smaller than that of the first mounting wheel (101), The second mounting wheel (102) has a plurality of external teeth (102a) extending in the axial direction on its outer peripheral surface. The inner teeth (101a) of the first mounting wheel (101) mesh with the outer teeth (102a) of the second mounting wheel (102), and the tooth width D3 of the outer teeth (102a) is not less than the sum of the tooth widths D4 of the inner teeth (101a) of the two first mounting wheels (101); The first mounting wheel (101) and the second mounting wheel (102) are respectively coaxially connected to one of the sun wheel (202) or the input shaft (201); There are two sun gears (202). Each of the sun wheels (202) is coaxially embedded with a first mounting wheel (101). The second mounting wheel (102) is provided on the surface of the input shaft (201); The sun gear connection structure (100) further includes: an adjustment assembly (700), wherein the second mounting wheel (102) selectively engages with at least one of the two first mounting wheels (101) through the adjustment assembly (700); The adjustment assembly (700) comprises a pushing portion (701) for driving the second mounting wheel (102) to move axially along the input shaft (201), the pushing portion (701) comprising a magnetic member (701a) provided on one side of the second mounting wheel (102), an electromagnet (701b) fixedly provided outside the end of the input shaft (201) and adapted to the magnetic member (701a), and a non-magnetic spring (701c) provided between the magnetic member (701a) and the electromagnet (701b); The adjustment assembly (700) comprises two limit blocks (702) spaced apart and distributed on the surface of the input shaft (201), and is used to limit the maximum sliding distance of the second mounting wheel (102); When the second mounting wheel (102) moves to any one of the limit blocks (702), the second mounting wheel (102) only engages with one of the two first mounting wheels (101); There is at least one position X between the two limit blocks (702), and when the second mounting wheel (102) moves to the position X, the second mounting wheel (102) engages with the two first mounting wheels (101) at the same time.

2. The sun gear connection structure (100) according to claim 1, characterized in that: The two first mounting wheels (101) have the same radial cross-sectional dimensions and coaxial rotation centers. The plurality of internal teeth (101a) located on the two first mounting wheels (101) are all kept aligned in the axial direction; The second mounting wheel (102) is axially slidably connected to the surface of the input shaft (201).

3. The sun gear connection structure (100) according to claim 2, characterized in that: The tooth width D3 of the external teeth (102a) is not less than the tooth width D4 of the internal teeth (101a) of any one of the first mounting wheels (101).

4. A planetary reducer (200), characterized in that: The sun gear connection structure (100) according to any one of claims 1 to 3 further comprises: An input shaft (201) rotates at a first speed before deceleration, with the central axis as the center; A sun gear (202) connected to the input shaft (201) via the sun gear connection structure (100); At least two planetary gears (203) meshing with the sun gear (202) via helical teeth on the radially outer side of the sun gear (202); an annular internal gear (204) meshing with each planetary gear (203) on the radially outer side of each planetary gear (203); The planet carrier (205) includes a connecting rod (205a) coaxially connected to each planet gear (203), and a connecting plate (205b) connected to each connecting rod (205a). When the internal gear (204) is fixed, the connecting plate (205b) rotates at a second, reduced speed relative to the input shaft (201); and The calibration component (300) is provided between the planet carrier (205) and each planet gear (203) and is used to adjust the meshing clearance of the helical teeth between each planet gear (203) and the sun gear (202) to be the same.

5. The planetary reducer (200) according to claim 4, characterized in that: The calibration assembly (300) comprises a driving portion (301) for driving the planetary gear (203) to move axially along the connecting rod (205a).

6. The planetary reducer (200) according to claim 4 or 5, characterized in that: The tooth width D1 of the sun gear (202) is greater than the tooth width D2 of the planet gear (203). Furthermore, the difference between the tooth width D1 and the tooth width D2 is not less than the maximum meshing clearance of the helical teeth between the planetary gear (203) and the sun gear (202).

7. The planetary reducer (200) according to claim 6, characterized in that: The calibration assembly (300) further includes a pressure sensor (302) provided at the connection between the planetary gear (203) and the connecting rod (205a); The pressure collection point of the pressure sensor (302) is arranged on a side opposite to the moving direction of the planetary gear (203).

8. The planetary reducer (200) according to claim 5, characterized in that: The connecting rod (205a) is a telescopic rod, comprising a movable section (205a-1) supporting the planetary gear (203), and a fixed section (205a-2) fixedly connected to the connecting plate (205b); The driving portion (301) is used to drive the moving section (205a-1) to move relative to the fixed section (205a-2) along the axial direction of the connecting rod (205a).

9. The planetary reducer (200) according to claim 8, characterized in that: The movable section (205a-1) and the fixed section (205a-2) do not rotate relative to each other; The driving portion (301) comprises a calibration rod (301a) rotatably connected to the fixed section (205a-2), and the calibration rod (301a) is connected to the movable section (205a-1) via a threaded connection.

10. A motor, characterized in that: The planetary reducer (200) according to any one of claims 4 to 9 further comprises: A housing (500) having a first installation cavity (501) and a second installation cavity (502) separated from each other, wherein the first installation cavity (501) is used to accommodate the planetary reducer (200); a motor body, which is mounted in the second mounting cavity (502), and includes a rotor assembly driving the input shaft (201), wherein the input shaft (201) extends from the second mounting cavity (502) into the first mounting cavity (501) and is connected to the sun gear (202); and An output shaft (600) is coaxially connected to the connecting plate (205b) and extends outside the housing (500), and rotates at a second, decelerated speed relative to the input shaft (201).

11. The motor according to claim 10, wherein: The planetary reducer (200) is provided with two groups, The two sets of planetary reducers (200) have the same input shaft (201). The sun gears (202) of the two sets of planetary reducers (200) are connected to the input shaft (201) via the sun gear connection structure (100). The two sets of planetary reducers (200) have the same number of planetary gears (203) and are coaxially connected in pairs. The two sets of planetary reducers (200) have the same set of planet carriers (205).

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