Sun gear connecting structure, planetary reducer with sun gear connecting structure and motor with sun gear connecting structure

Abstract

The invention relates to the technical field of motors, in particular to a sun gear connecting structure, a planetary reducer with the sun gear connecting structure and a motor, and the sun gear connecting structure comprises a first mounting gear which is provided with an annular groove, and a plurality of inner teeth extending in the axial direction are arranged in the groove; the diameter of the second mounting wheel is smaller than that of the first mounting wheel, the outer circumferential surface of the second mounting wheel is provided with a plurality of outer teeth extending in the axial direction, and the inner teeth of the first mounting wheel are meshed with the outer teeth of the second mounting wheel; and the first mounting wheel and the second mounting wheel are respectively and coaxially connected with one of a sun wheel and an input shaft. The gear type floating connection between the sun gear and the input shaft is arranged, so that power is stably transmitted under the condition of multi-shaft centering; and by arranging the adjusting assembly, switching cooperation between the input shaft and the two sun gears is achieved.

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 the rapid development of economy, cars have become a necessary means of transportation in people's lives, and new energy vehicles are developing rapidly. New energy vehicles are generally driven by motors. For some new energy trucks that need to load heavy objects, due to their own weight and the weight of the goods, ordinary motor drive methods will cause the vehicle to feel powerless when starting.

[0003] The prior art has a solution to increase the output torque of the motor through a planetary reducer. The planetary reducer is a common planetary gear transmission structure, which transmits the original rotating shaft of the motor through the planetary reducer to output a large torque. In engineering, the planetary gear transmission has the advantages of compact layout, small mass, and large load capacity.

[0004] These are due to the fact that it adopts a transmission mode of multiple planetary gears in its layout, fully manipulates the space between the coaxial gears, uses multiple planetary gears to share the load, forms power flow, and reasonably adopts internal meshing transmission, which makes it have many of the above advantages. However, this is only the most ideal situation. In actual applications, due to the existence of processing errors and assembly errors, the load distribution on each planetary gear is uneven during the transmission process, resulting in the phenomenon that the load is 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 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 (it 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 present invention.

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

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

[0010] To achieve the above object, the present invention adopts the following technical solution: A sun gear connection structure includes, A first mounting wheel having an annular groove with a plurality of internal teeth extending axially therein; and, A second mounting wheel having a diameter smaller than that of the first mounting wheel, The second mounting wheel has a plurality of external teeth extending axially on its outer peripheral surface, The internal teeth of the first mounting wheel mesh with the external teeth of the second mounting wheel, The first mounting wheel and the second mounting wheel are respectively coaxially connected to one of the sun gear or the input shaft.

[0011] As a preferred embodiment of the sun gear connection structure of the present invention, wherein: There are two sun gears, Each of the sun gears coaxially houses a respective one of the first mounting wheels therein, The second mounting wheel is provided on the surface of the input shaft; The sun gear connection structure further includes, An adjustment assembly, and the second mounting wheel selectively meshes with at least one of the two first mounting wheels through the adjustment assembly.

[0012] As a preferred embodiment 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 their centers of rotation are coaxial, The multiple internal teeth located on the two first mounting wheels are axially aligned; The second mounting wheel is axially slidably connected to the surface of the input shaft, The adjustment assembly includes a pushing portion for driving the second mounting wheel to move axially along the input shaft.

[0013] As a preferred embodiment of the sun gear connection structure of the present invention, wherein: The pushing portion includes a magnetic member provided on one side of the second mounting wheel, an electromagnet fixedly provided outside the end of the input shaft and adapted to the magnetic member, and a non-magnetic spring provided between the magnetic member and the electromagnet.

[0014] As a preferred embodiment of the sun gear connection structure of the present invention, wherein: The adjustment assembly includes two limiting blocks spaced apart on the surface of the input shaft for limiting the maximum sliding distance of the second mounting wheel; When the second mounting wheel moves to any one of the limiting blocks, the second mounting wheel only meshes with one of the two first mounting wheels;

[0015] There is at least one position X between the two limiting blocks. When the second mounting wheel moves to position X, the second mounting wheel meshes with the two first mounting wheels simultaneously.

[0016] As a preferred solution of the sun gear connection structure of the present invention, wherein: 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.

[0017] As a preferred solution of the sun gear connection structure of the present invention, wherein: 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.

[0018] The beneficial effects of a sun gear connection structure of the present invention: By providing a tooth type floating connection between the sun gear and the input shaft, the power is stably transmitted under the condition of multi-axis alignment; and by providing an adjustment assembly, the switching cooperation between the input shaft and the two sun gears is realized.

[0019] In view of the fact that during the actual use process, there is also a problem that the load is easily concentrated on one planetary gear.

[0020] Therefore, the second object of the present invention is to provide a planetary speed reducer.

[0021] To solve the above technical problems, the present invention provides the following technical solutions: A planetary speed reducer includes the sun gear connection structure as described above, and further includes, An input shaft, which rotates at a first speed before deceleration around its central axis; A sun gear, which is connected to the input shaft through the sun gear connection structure as described above; At least two planetary gears, which are meshed with the sun gear through helical teeth on the radial outside of the sun gear, An annular internal gear, which is meshed with each planetary gear on the radial outside of each planetary gear; A planetary carrier, including connecting rods coaxially connected to each planetary gear, and a connecting plate connected to each connecting rod; When the internal gear is fixed, the connecting plate rotates relative to the input shaft at a second speed after deceleration; and,

[0022] A calibration assembly, which is arranged between the planetary carrier and each planetary gear and is used to adjust the meshing clearance between the helical teeth of each planetary gear and the sun gear to be the same.

[0023] As a preferred solution of the planetary speed reducer of the present invention, wherein: the calibration assembly includes a driving part for pushing the planetary gear to move axially along the connecting rod.

[0024] As a preferred embodiment of the planetary reducer of the present invention, wherein: the tooth width D1 of the sun gear is greater than the tooth width D2 of the planetary gear, and 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.

[0025] As a preferred embodiment of the planetary reducer of the present invention, wherein: the calibration assembly further includes a pressure sensor disposed at the connection between the planetary gear and the connecting rod; The pressure acquisition point of the pressure sensor is set on the side against the moving direction of the planetary gear.

[0026] As a preferred embodiment of the planetary reducer of the present invention, wherein: the connecting rod is a telescopic rod, including a moving section supporting the planetary gear and a fixed section fixedly connected to the connecting plate; The driving part is used to drive the moving section to move axially relative to the fixed section along the connecting rod.

[0027] As a preferred embodiment of the planetary reducer of the present invention, wherein: there is no relative rotation between the moving section and the fixed section; The driving part includes a calibration rod rotatably connected to the fixed section, and the calibration rod is threadedly connected to the moving section.

[0028] The beneficial effect of a planetary reducer of the present invention: By the cooperation between the planetary reducer and the calibration assembly provided in the present invention, the problem that the load is easily concentrated on one planetary gear is solved, and by setting a pressure sensor, fine calibration is facilitated.

[0029] Based on the same inventive concept, the third object of the present invention is to provide an electric motor.

[0030] To solve the above technical problems, the present invention provides the following technical solutions: An electric motor includes the planetary reducer as described above, and further includes, A housing, which is provided with a first installation cavity and a second installation cavity separated from each other, and the first installation cavity is used to accommodate the planetary reducer; An electric motor main body, which is installed in the second installation cavity, includes a rotor assembly for driving the input shaft, and the input shaft extends from the second installation cavity to the first installation cavity and is connected to the sun gear as described above; and, An output shaft, which is coaxially connected to the connecting plate and extends outside the housing, and rotates relative to the input shaft at a reduced second rotational speed.

[0031] As a preferred embodiment of the electric motor of the present invention, wherein: there are two sets of the planetary reducers, The two sets of the planetary reducers have the same input shaft, The sun gears of the two sets of planetary reducers are connected to the input shaft through the sun gear connection structure described above. The number of planet gears of the two sets of planetary reducers is the same and they are coaxially connected in pairs. The two sets of planetary reducers share the same set of planet carriers.

[0032] The beneficial effects of an electric motor according to the present invention: By providing an electric motor with two sets of planetary reducers, large torque output is achieved, and the load of the planet gears is evenly distributed when the electric motor rotates forward and backward. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for the description of the embodiments will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0034] Figure 1 It is a schematic diagram of the prior art where the load is concentrated on a single planet gear.

[0035] Figure 2 It is a schematic diagram of the installed structure of one embodiment of the sun gear connection structure in Embodiment 1 of the present invention.

[0036] Figure 3 It is a schematic diagram of the structure of one embodiment of the sun gear connection structure in Embodiment 1 of the present invention before installation.

[0037] Figure 4 It is a schematic diagram of the structure of another embodiment of the sun gear connection structure in Embodiment 1 of the present invention before installation.

[0038] Figure 5 It is a three-dimensional structure schematic diagram of the sun gear connection structure in Embodiment 2 of the present invention.

[0039] Figure 6 It is a sectional structure schematic diagram of the sun gear connection structure in Embodiments 2 and 6 of the present invention when the input shaft rotates forward at low speed.

[0040] Figure 7 It is a sectional structure schematic diagram of the sun gear connection structure in Embodiments 2 and 6 of the present invention when the input shaft rotates backward at low speed.

[0041] Figure 8 It is a sectional structure schematic diagram of the sun gear connection structure in Embodiments 2 and 6 of the present invention when the input shaft rotates at high speed.

[0042] Figure 9 It is an internal structure schematic diagram of the sun gear connection structure in Embodiment 2 of the present invention.

[0043] Figure 10 It is a schematic three - dimensional structure diagram of the planetary reducer in Embodiments 3 and 4 of the present invention.

[0044] Figure 11 It is a schematic side - view structure diagram of the planetary reducer in Embodiments 3 and 4 of the present invention.

[0045] Figure 12 For the present invention Figure 11 It is a schematic cross - sectional structure diagram in the A direction shown.

[0046] Figure 13 For the present invention Figure 12 It is an enlarged schematic structure diagram at position B shown.

[0047] Figure 14 It is a schematic three - dimensional structure diagram of the cooperation between a single planetary gear and the sun gear in Embodiments 3 and 4 of the present invention.

[0048] Figure 15 It is a schematic side - view structure diagram of the cooperation between multiple planetary gears and the sun gear in Embodiments 3 and 4 of the present invention.

[0049] Figure 16 For the present invention Figure 15 It is a schematic cross - sectional structure diagram in the perspective shown.

[0050] Figure 17 It is a schematic three - dimensional structure diagram of the motor in Embodiments 5 and 6 of the present invention.

[0051] Figure 18 It is a schematic side - view structure diagram of the motor in Embodiments 5 and 6 of the present invention.

[0052] Figure 19 For the present invention Figure 18 It is a schematic cross - sectional structure diagram in the C direction shown.

[0053] Figure 20 It is a schematic installation structure diagram of the planetary gear in Embodiment 6 of the present invention.

[0054] Figure 21 For the present invention Figure 20 It is a schematic front - view structure diagram.

[0055] Figure 22 For the present invention Figure 21 It is a schematic cross - sectional structure diagram in the E direction shown.

[0056] 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, planet 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, adjusting assembly; 701, pushing part; 701a, magnetic part; 701b, electromagnet; 701c, non-magnetic spring; 702, limiting block. Detailed implementation manners

[0057] In order to make the objectives, features, and advantages of the present invention more obvious and understandable, the following provides a detailed description of the specific implementation manners of the present invention with reference to the accompanying drawings of the specification.

[0058] In the following description, many specific details are set forth in order to fully understand the present invention. However, the present invention may also be implemented in other ways different from those described herein. Those skilled in the art can make similar generalizations without departing from the connotation of the present invention. Therefore, the present invention is not limited by the specific embodiments disclosed below.

[0059] Secondly, the so-called "one embodiment" or "embodiment" herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation manner of the present invention. The phrase "in one embodiment" appearing in different places in this specification does not necessarily refer to the same embodiment, nor is it an independent or selectively exclusive embodiment with other embodiments.

[0060] Embodiment 1

[0061] Referring to Figures 2 - 4 , this is the first embodiment of the present invention. This embodiment provides a sun gear connection structure 100, which can compensate for the comprehensive displacement through tooth connection, realize the floating of the sun gear 202, and further evenly distribute the load on the planetary gear 203 during the transmission process. It includes: a first mounting wheel 101 and a second mounting wheel 102.

[0062] Specifically, the first mounting wheel 101 has an annular groove, and a plurality of internal teeth 101a extending along the axial direction are provided in the groove. The center of the groove is coaxial with the rotation center of the first mounting wheel 101. The groove can be formed by inward depression from the side surface of the first mounting wheel 101, and the plurality of internal teeth 101a are distributed in an annular array in the annular groove.

[0063] Further, 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 peripheral surface. The plurality of external teeth 102a are annularly arrayed 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. That is, the second mounting wheel 102 with a smaller diameter meshes with the internal teeth 101a of the first mounting wheel 101 with a larger diameter through the external teeth 102a.

[0064] Among them, the first mounting wheel 101 and the second mounting wheel 102 are respectively coaxially connected to one of the sun gear 202 or the input shaft 201. In one embodiment, the first mounting wheel 101 with a larger diameter is coaxially connected to the input shaft 201, and the second mounting wheel 102 with a smaller diameter is coaxially connected to the sun gear 202. When the input shaft 201 rotates, the sun gear 202 rotates following the first mounting wheel 101 through the second mounting wheel 102. The sun gear 202 and the input shaft 201 are connected together by a toothed structure, thus realizing the floating of the sun gear 202 relative to the input shaft 201.

[0065] In another embodiment, the first mounting wheel 101 with a larger diameter is coaxially connected to the sun gear 202, and the second mounting wheel 102 with a smaller diameter is coaxially connected to the input shaft 201. Similarly, the floating of the sun gear 202 relative to the input shaft 201 can be realized. The 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.

[0066] In summary, by setting 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, can stably transmit power in the case of multi-axis alignment, and further solves the problem of uneven load distribution caused during the processing and assembly process.

[0067] Embodiment 2

[0068] Referring to Figures 5 - 9 , this is the second embodiment of the present invention. Different from the previous embodiment, this embodiment provides an adjustment assembly 700, which solves the problem of switching cooperation between the input shaft 201 and the two sun gears 202.

[0069] Specifically, there are two sun gears 202. Each sun gear 202 coaxially houses a first mounting wheel 101 therein. The second mounting wheel 102 is disposed on the surface of the input shaft 201. The second mounting wheel 102 can mesh with any one of the two first mounting wheels 101. Thus, the input shaft 201 can cooperate with different sun gears 202 for transmission.

[0070] Further, the second mounting wheel 102 is selectively engaged with at least one of the two first mounting wheels 101 through the adjusting assembly 700. The adjusting assembly 700 has a control and adjustment function, and can move the second mounting wheel 102 to engage with one of the two first mounting wheels 101 respectively; or the second mounting wheel 102 can be engaged with the two first mounting wheels 101 simultaneously.

[0071] Furthermore, the radial cross-sectional dimensions of the two first mounting wheels 101 are the same, that is, the structures of the two first mounting wheels 101 are the same except for the tooth width D4 of the internal teeth 101a. The two first mounting wheels 101 are coaxially arranged along the rotation center, and a plurality of internal teeth 101a located on the two first mounting wheels 101 are kept aligned axially, that is, the axial deflection angle of the two first mounting wheels 101 is 0, and the second mounting wheel 102 is slidably connected to the surface of the input shaft 201 axially. When the external teeth 102a of the second mounting wheel 102 are engaged with the internal teeth 101a of any one of the first mounting wheels 101, since the two first mounting wheels 101 are kept aligned, when the second mounting wheel 102 slides axially to the other first mounting wheel 101, it will be engaged with the internal teeth 101a of this first mounting wheel 101.

[0072] Among them, the adjusting assembly 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 means that can realize the axial displacement of the second mounting wheel 102.

[0073] In this embodiment, the pushing part 701 includes a magnetic part 701a provided 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 fixedly arranged, and there is no relative rotation between the non-magnetic spring 701c and the electromagnet 701b. The non-magnetic spring 701c and the magnetic part 701a are rotationally connected through a bearing (for the convenience of showing the core details, the existing bearing and the input shaft drive structure are simplified in the figure). In this way, when the magnetic part 701a rotates, the non-magnetic spring 701c does not rotate. After the electromagnet 701b generates a magnetic force, only the magnetic part 701a moves towards 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 a magnetic attraction force on the magnetic part 701a, and the magnetic force size is adjusted by controlling the voltage of the electromagnet 701b being energized.

[0074] When the magnetic force of the electromagnet 701b on the magnetic member 701a is 0, the second mounting wheel 102 and the magnetic member 701a are kept 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 one of the first mounting wheels 101 away from the electromagnet 701b; after increasing the voltage of the electromagnet 701b, the magnetic force of the electromagnet 701b on the magnetic member 701a is increased. After being attracted by the magnetic force, the magnetic member 701a will drive the second mounting wheel 102 to move axially towards the side of the electromagnet 701b until the elastic force of the non-magnetic spring 701c increases after deformation to offset the magnetic force given by the electromagnet 701b and reach a new equilibrium position; similarly, after the magnetic force of the electromagnet 701b weakens, the second mounting wheel 102 can move in the reverse direction under the elastic force of the non-magnetic spring 701c. By controlling the magnitude of the magnetic force generated by the electromagnet 701b, the axial displacement distance of the second mounting wheel 102 can be accurately controlled, and thus the cooperation mode of the second mounting wheel 102 with the two first mounting wheels 101 can be realized.

[0075] The remaining structures are the same as those in Embodiment 1.

[0076] In summary, by providing the adjusting assembly 700, the control of the switching cooperation between the input shaft 201 and the two sun gears 202 is realized.

[0077] Embodiment 3

[0078] Referring to Figures 10 - 16 , this 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.

[0079] Specifically, the planetary reducer 200 includes an input shaft 201, a sun gear 202, a planetary gear 203, an internal gear 204, and a planetary carrier 205. The planetary transmission system has flexibility and diversity, and there are six combinable motion modes. Among them, there are three motion modes combined for the purpose of speed reduction. For example, when the sun gear 202 is fixed, the internal gear 204 is the driving member, and the planetary carrier 205 is the driven member: in this case, the rotational speed is reduced and the direction is the same; or when the internal gear 204 is fixed, the sun gear 202 is the driving member, and the planetary carrier 205 is the driven member: in this case, the rotational speed is reduced and the direction is the same; and when the planetary carrier 205 is fixed, the sun gear 202 is the driving member, and the internal gear 204 is the driven member: in this case, the rotational speed is reduced and the direction is opposite.

[0080] In this embodiment, the internal gear 204 is fixed and arranged in a circular ring shape, which meshes 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 around the central axis at the first rotational speed before deceleration. At least two planet gears 203 are provided. They mesh with the sun gear 202 through helical teeth on the radial outside of the sun gear 202. Compared with straight teeth of the same tooth width, the helical teeth have a larger contact area during meshing, which is beneficial for sharing the load.

[0081] 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 and the sun gear 202 is connected to the input shaft 201 through the sun gear connection structure 100, when the input shaft 201 rotates at the first rotational speed before deceleration, the sun gear 202 rotates accordingly. The sun gear 202 drives the planet gears 203 to rotate self. While the planet gears 203 rotate self, under the action of the internal gear 204, they revolve around the rotation center of the sun gear 202. Furthermore, the connecting plate 205b connected to the planet gears 203 rotates relative to the input shaft 201 at the second rotational speed after deceleration.

[0082] Furthermore, a calibration assembly 300 is provided between the planet carrier 205 and each planet gear 203 for adjusting the meshing clearance between the teeth of each planet gear 203 and the sun gear 202 to be the same. When multiple planet gears 203 mesh with the sun gear 202, the tooth spaces at the meshing positions during machining or assembly are generally slightly larger than the tooth thickness for convenient assembly. Due to the errors during machining or assembly, after the multiple planet gears 203 are assembled and meshed with the sun gear 202, the tooth clearances at the meshing positions between each planet gear 203 and the sun gear 202 are often different in size. As a result, the planet gears 203 with smaller tooth clearances are likely to bear more loads, leading to the problem of uneven load distribution. Therefore, by setting the calibration assembly 300, on the rotation direction of the sun gear 202, there is a surface of the tooth of the planet gear 203 that receives the thrust of the tooth of the sun gear 202, and the difference in tooth clearances of the force-receiving surfaces at the meshing positions between each planet gear 203 and the sun gear 202 is adjusted to 0. Since the teeth are distributed in a circular array, when the planet gears 203 and the sun gear 202 rotate and mesh, the tooth clearances at any angle of rotation between each planet gear 203 and the sun gear 202 will remain relatively consistent. Furthermore, the problem of uneven load distribution on each planet gear 203, resulting in the load being easily concentrated on one planet gear 203, is solved. For example Figure 13 、 14 、16, if the rotation direction of the sun gear 202 is L, the planet gears 203 are calibrated and adjusted along the direction of M, so that the helical teeth of the planet gears 203 approach the helical tooth surface N of the sun gear 202 to generate contact pressure. Among them, the calibration component 300 includes a driving part 301 for pushing the planet gear 203 to axially move along the connecting rod 205a. In this embodiment, the planet gear 203 and the sun gear 202 are meshed by helical teeth. The teeth of the helical gear are helically arranged relative to the rotation center, and the meshing helical gears have the same helix angle. Therefore, the tooth clearance between the two helical gears can be adjusted by axially moving. In this embodiment, the position of the sun gear 202 is fixed, and the driving part 301 is used to push the planet gear 203 to axially move along the connecting rod 205a, so that the relative axial displacement between the planet gear 203 and the sun gear 202 is realized, and the tooth clearance condition between the two is achieved. The driving part 301 can adopt an automatic control mode such as an electric telescopic rod, and the advantage is that it is convenient to adjust at any time after the assembly is completed; it can also adopt a manual control mode. Only the tooth clearance between each planet gear 203 and the sun gear 202 needs to be calibrated during assembly, and the calibration value during assembly is maintained during subsequent use, and only disassembled and recalibrated when necessary.

[0083] Preferably, the tooth width D1 of the sun gear 202 is greater than the tooth width D2 of the planet gear 203. During assembly, the teeth of the planet gear 203 are assembled to be completely in contact with the teeth of the sun gear 202, that is, the overlapping range of the tooth width at the meshing part of the planet gear 203 and the sun gear 202 is the tooth width D2 of the planet gear 203, so that the teeth of the planet gear 203 can completely bear the force exerted by the sun gear 202, which is beneficial to the average distribution of the load. In one rotation direction of the sun gear 202, to reduce the clearance of the force-bearing surface at the meshing part between the planet gear 203 and the sun gear 202, only the planet gear 203 needs to be moved in the specified direction. Therefore, the difference between the tooth width D1 and the tooth width D2 can also be not less than the maximum meshing clearance of the helical teeth between the planet gear 203 and the sun gear 202, so that the teeth of the planet gear 203 can completely bear the force exerted by the sun gear 202 within the entire adjustment range.

[0084] The remaining structures are the same as those in Embodiment 2.

[0085] In summary, by setting the combined use of the planetary reducer 200 and the calibration component 300, the difference in tooth clearance at the meshing part of each planet gear 203 and the sun gear 202 is uniformly calibrated, and the problem that the load is easily concentrated on one planet gear 203 is solved.

[0086] Embodiment 4

[0087] Refer to Figures 10 - 16, which is the fourth embodiment of the present invention. Different from the previous embodiment, this embodiment provides a pressure sensor 302 to facilitate adjusting the tooth clearance at the meshing position between each planet 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 for output, and is widely used in industrial automation, automotive electronics, medical devices, aerospace and other fields. It converts the pressure change into an electrical signal through a pressure sensing element, and then converts it into a readable pressure value. 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 acquisition point, the force magnitude at this acquisition point can be read.

[0088] In this embodiment, the pressure sensor 302 is used to detect the contact pressure between each planet gear 203 and the sun gear 202. Since it is difficult to distinguish the tooth clearance size at the meshing position between the planet gear 203 and the sun gear 202 by the naked eye during calibration, in this embodiment, the tooth clearance values of each planet gear 203 are uniformly set to 0 during calibration, that is, the teeth of the planet gear 203 are pushed to contact with the teeth of the sun gear 202; however, although it can be visually distinguished that the two are in contact, according to the pressing degree, the contact pressure values between the two may be different, which will also cause uneven load distribution on each planet gear 203 when the sun gear 202 rotates at high speed. The contact pressure values between each planet gear 203 and the sun gear 202 are measured by the pressure sensor 302 and adjusted to a unified value. The specific contact pressure value needs to be determined according to the specific application scenario, gear material, lubrication conditions, and geometric parameters of the gear.

[0089] Specifically, after the planet gear 203 is blocked by the sun gear 202, the planet gear 203 will receive a reaction force, and then exert a force on the connecting rod 205a. This force value can be regarded as the contact pressure value. Therefore, the pressure acquisition point of the pressure sensor 302 needs to be set at the connection between the planet gear 203 and the connecting rod 205a.

[0090] Among them, the pressure acquisition point of the pressure sensor 302 is set on the side opposite to the moving direction of the planet gear 203. According to the force analysis, when the planet gear 203 moves from the starting point to the end point side until it contacts the sun gear 202 to generate contact pressure, the force exerted by the planet gear 203 on the connecting rod 205a is towards the starting point side at this time. In this embodiment, the planet gear 203 is installed on the surface of the connecting rod 205a through a bearing. There are no less than two snap ring grooves on the surface of the connecting rod 205a. The bearing is installed between the two snap ring grooves and is fixed by snap rings. The pressure sensor 302 collects the force magnitude of the corresponding side snap ring.

[0091] Further, the connecting rod 205a is a telescopic rod, including a moving section 205a-1 that supports the planetary gear 203 and a fixed section 205a-2 fixedly connected to the connecting plate 205b. The driving part 301 is used to drive the moving section 205a-1 to move axially relative to the fixed section 205a-2 along the connecting rod 205a. Similarly, the telescopic rod can be an electric telescopic rod, and the distance of the displacement of the moving section 205a-1 relative to the fixed section 205a-2 is controlled by a program.

[0092] Preferably, in this embodiment, the moving section 205a-1 and the fixed section 205a-2 are not relatively rotated. For example, a guiding groove is arranged axially on one side of the moving section 205a-1, and a guiding block adapted to the guiding groove is arranged on one side of the fixed section 205a-2. The guiding groove and the guiding block can also be arranged in the reverse direction. The driving part 301 includes a calibration rod 301a rotatably connected to the fixed section 205a-2, and the calibration rod 301a is threadedly connected to the moving section 205a-1. 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 are not relatively rotated, the rotation of the calibration rod 301a will cause threaded sliding with the moving section 205a-1, thereby driving the moving section 205a-1 to move axially. 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 values of each pressure sensor 302 are the same and meet the set contact pressure value, and the adjustment process is completed.

[0093] The remaining structures are the same as those in Embodiment 3.

[0094] Embodiment 5

[0095] Referring to Figures 17 - 18 , this 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 main body, and an output shaft 600. The motor main body is used to drive the input shaft 201, including 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 main body. After the motor main body drives the input shaft 201 to rotate, it passes through the planetary reducer 200 and is finally output outward through the output shaft 600.

[0096] Specifically, a first installation cavity 501 and a second installation cavity 502 are provided inside the housing 500 and are separated from each other. The first installation cavity 501 is used to accommodate the planetary reducer 200. It should be noted that the first installation cavity 501 and the second installation cavity 502 are formed relatively. 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 side of the first housing away from the end cover, which is convenient for 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.

[0097] Among them, the motor main body is installed in the second installation cavity 502 and includes a rotor assembly that drives the input shaft 201. The input shaft 201 extends from the second installation cavity 502 into the first installation cavity 501 and is connected to the sun gear 202. The output shaft 600 is coaxially connected to the connecting plate 205b and extends outside the housing 500, and rotates relative to the input shaft 201 at a reduced second rotational speed.

[0098] Furthermore, the internal gear 204 of the planetary reducer 200 is fixed to the housing 500. The sun gear 202 and the planetary gears 203 are correspondingly arranged inside the inner ring of the internal gear 204. Through the flange-type housing 500, the first and second housings are respectively cast. The internal gear 204 is separated from the housing 500 and is fixed to the first and second housings through bolts and taper pins. The spatial distribution is reasonable and it is convenient for disassembly and maintenance.

[0099] The remaining structures are the same as those in Embodiment 4.

[0100] Embodiment 6

[0101] Referring to Figures 17 - 22 , this is the sixth embodiment of the present invention. Different from the previous embodiment, this embodiment provides two sets of planetary reducers 200, which solves the problems existing during the reverse drive of the motor. Considering that the motor of the vehicle needs to meet the reverse rotation to achieve the reverse driving requirement, and since the aforementioned calibration assembly 300 can only ensure that the sun gear 202 maintains the same load as each planetary gear 203 in one rotation direction, when the sun gear 202 rotates in the reverse direction, in the case of relatively high machining accuracy, it can still ensure that the tooth clearances of the other contact surfaces between the sun gear 202 and each planetary gear 203 are equal; while in the case of relatively low machining accuracy, the tooth clearances at the meshing positions between the sun gear 202 and each planetary gear 203 may still have differences and calibration is still required.

[0102] Specifically, there are two sets of planetary reducers 200. The two sets of planetary reducers 200 can be respectively responsible for forward rotation and reverse rotation, and calibration in the corresponding directions is carried out for the two sets of planetary reducers 200. 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 same input shaft 201 through the sun gear connection structure 100. The input shaft 201 is driven to rotate by the same motor body, and the input shaft 201 can cooperate with the sun gear 202 of the corresponding set of planetary reducers 200 for driving.

[0103] The number of planet gears 203 of the two sets of planetary reducers 200 is the same and they are coaxially connected in pairs. The two sets of planetary reducers 200 have the same set of planet carriers 205 to ensure synchronous rotation. 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 drive the same planet carrier 205 and output shaft 600 for output. In this embodiment, as Figure 22 , the adjustment directions M of the planet gears 203 on both sides are opposite, and independent calibration can be carried out during assembly. Both the fixed sections 205a-2 and the moving sections 205a-1 of the connecting rod 205a are provided in two sets. The two fixed sections 205a-2 are respectively fixed to the connecting plates 205b on both sides by bolts. The two moving sections 205a-1 respectively support the planet gears 203 of the two sets of planetary reducers 200. The two moving sections 205a-1 are connected by a slide rod 205a-3, and both moving sections 205a-1 can axially slide relative to the slide rod 205a-3.

[0104] Further, the adjustment assembly 700 includes two limit blocks 702 spaced apart on the surface of the input shaft 201 for limiting the maximum sliding distance of the second mounting wheel 102. The distance between the two limit blocks 702 is the maximum range of the sliding of the second mounting wheel 102. For the convenience of control, in this embodiment, when the second mounting wheel 102 moves to any one of the limit blocks 702, the second mounting wheel 102 only meshes with one of the two first mounting wheels 101, that is, when the second mounting wheel 102 is at the limit block 702 position, the input shaft 201 only drives one set of sun gears 202 to rotate, corresponding to forward and reverse rotations respectively.

[0105] Furthermore, there is at least one position X between the two limit blocks 702. When the second mounting wheel 102 moves to the position X, the second mounting wheel 102 meshes with the two first mounting wheels 101 at the same time. That is, when the second mounting wheel 102 is at the position X, the input shaft 201 can drive the two sets of sun gears 202 to rotate at the same time, further sharing the load, and can meet the high-speed operation of the corresponding motor when the vehicle has certain large torque output requirements.

[0106] Among them, 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, so as to ensure that when the second mounting wheel 102 moves to the position of the limiting block 702, the entire internal teeth 101a of the first mounting wheel 101 are engaged with the external teeth 102a of the second mounting wheel 102, and the driving load of the sun gear 202 under this condition is shared to the greatest extent.

[0107] Preferably, the tooth width D3 of the external teeth 102a is not less than the sum of the tooth widths D4 of the internal 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 internal teeth 101a of the two first mounting wheels 101 are simultaneously engaged with the external teeth 102a of the second mounting wheel 102, and the driving load borne by the sun gear 202 under this condition is shared to the greatest extent. The two sets of sun gears 202 and the corresponding planet gears 203 are all involved in the load distribution.

[0108] The rest of the structure is the same as that of Embodiment 5.

[0109] Working principle: The control module of the motor body controls the input shaft 201 to rotate forward and backward, and at the same time controls the rotation speed of the input shaft 201. The control module of the motor body also adjusts the energization voltage of the electromagnet 701b. The specific control logic is as follows: Set a speed threshold. When the input shaft 201 rotates forward at a speed lower than the threshold, the magnetic force intensity of the electromagnet 701b is 0, and the second mounting wheel 102 is stable at the limiting block 702 away from the electromagnet 701b. At this time, the external teeth 102a of the second mounting wheel 102 are only engaged with the sun gear 202 away from the electromagnet 701b. When the input shaft 201 rotates backward at a speed lower than the threshold, the magnetic force intensity of the electromagnet 701b is the maximum, and the second mounting wheel 102 is stable at the limiting block 702 close to the electromagnet 701b. At this time, the external teeth 102a of the second mounting wheel 102 are only engaged with the sun gear 202 close to the electromagnet 701b. When the input shaft 201 rotates at a speed not lower than the threshold, the magnetic force intensity of the electromagnet 701b is increased to half, and the second mounting wheel 102 is stable at position X in the middle of the two limiting blocks 702. At this time, the external teeth 102a of the second mounting wheel 102 are simultaneously engaged with the sun gear 202.

[0110] In summary, by setting a motor with two sets of planetary reducers 200, high torque output is achieved, and by controlling, the load of the planet gears is evenly distributed when the motor rotates forward and backward.

[0111] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be modified or equivalently replaced without departing from the spirit and scope of the technical solutions of the present invention, and they should all be covered within 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, wherein the groove has a plurality of internal 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). The first mounting wheel (101) and the second mounting wheel (102) are respectively coaxially connected to one of the sun wheel (202) and the input shaft (201); The sun gears (202) are provided with two. Each of the sun wheels (202) is coaxially embedded with a first mounting wheel (101). The second mounting wheel (102) is arranged on the surface of the input shaft (201); The sun gear connection structure (100) further comprises: An adjustment component (700), wherein the second mounting wheel (102) selectively engages with at least one of the two first mounting wheels (101) through the adjustment component (700).

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). The adjustment assembly (700) comprises a pushing portion (701) for driving the second mounting wheel (102) to move axially along the input shaft (201).

3. The sun gear connection structure (100) according to claim 2, characterized in that: The pushing part (701) comprises a magnetic member (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 member (701a), and a non-magnetic spring (701c) arranged between the magnetic member (701a) and the electromagnet (701b).

4. The sun gear connection structure (100) according to any one of claims 1 to 3, characterized in that: The adjustment component (700) comprises two limit blocks (702) spaced apart and distributed on the surface of the input shaft (201), and 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 meshes 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.

5. The sun gear connection structure (100) according to any one of claims 1 to 3, 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).

6. The sun gear connection structure (100) according to any one of claims 1 to 3, characterized in that: The tooth width D3 of the external teeth (102a) is not less than the sum of the tooth widths D4 of the internal teeth (101a) of the two first mounting wheels (101).

7. A planetary reducer (200), characterized in that: The sun gear connection structure (100) 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), which are meshed 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) comprises a connecting rod (205a) coaxially connected to each planetary 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 speed after deceleration relative to the input shaft (201); and The calibration component (300) is arranged between the planet carrier (205) and each planetary gear (203), and is used to adjust the meshing clearance of the helical teeth between each planetary gear (203) and the sun gear (202) to be the same.

8. The planetary reducer (200) according to claim 7, 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).

9. The planetary reducer (200) according to claim 7 or 8, 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).

10. The planetary reducer (200) according to claim 9, characterized in that: The calibration component (300) further comprises 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).

11. The planetary reducer (200) according to claim 7, 8 or 10, characterized in that: The connecting rod (205a) is a telescopic rod, comprising a moving section (205a-1) supporting the planetary gear (203), and a fixed section (205a-2) fixedly connected to the connecting plate (205b); The driving part (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).

12. The planetary reducer (200) according to claim 11, characterized in that: The movable section (205a-1) and the fixed section (205a-2) do not rotate relative to each other; The driving part (301) comprises a calibration rod (301a) rotatably connected to the fixed section (205a-2); the calibration rod (301a) is connected to the movable section (205a-1) via a threaded connection.

13. A motor, characterized in that: The planetary reducer (200) 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 installed in the second installation cavity (502), and comprises a rotor assembly driving the input shaft (201), wherein the input shaft (201) extends from the second installation cavity (502) to the first installation 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, reduced speed relative to the input shaft (201).

14. The motor according to claim 13, characterized in that: 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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