Linear high-speed planet module

Abstract

A linear type high-speed planet module comprises a motor installation base, a flange support and an installation base which are sequentially arranged in the axial direction and fixed through aligned threaded holes and screws, and the axis lines of the motor installation base, the flange support and the installation base coincide. The input shaft is connected with the motor mounting base and the output shaft through bearings, and the output shaft is fixed to the flange support and the mounting base through bearings and meshed with the outer gear. The outer gear is meshed with a plurality of gear shafts which are evenly distributed in the circumferential direction with the axis as the reference, the left ends of the gear shafts are connected with spline wheels through flat keys, the spline wheels are meshed with internal spline planet wheels, and the internal spline planet wheels are meshed with the input shaft section. During operation, motor power is transmitted to the input shaft to drive the internal spline planet wheel to drive the gear shaft, and then the power is transmitted to the right end of the output shaft through the external gear to be output. According to the design, the fixed gear shaft replaces a rotary planet carrier, double-end bearing supporting improves rigidity and relieves high-speed vibration, the elastic check ring and other structures reduce impact, traditional high-speed limitation is broken through, transmission efficiency is high, and stability is high.

Description

Technical Field

[0001] The present invention relates to a planetary gearbox module, belongs to the field of transmission machinery, and in particular to a linear high-speed planetary module. Background Art

[0002] Traditional lifting gearboxes generally utilize a linear structure with superimposed multi-stage NGW transmissions, which perform well in low-speed, heavy-load horizontal operating conditions. However, the planetary carrier of these gearboxes is a non-fixed structure and must rotate synchronously with the power. When the input speed increases above 1800 rpm, the centrifugal force generated by the eccentric mass of the planetary carrier assembly (including the planetary carrier, planetary pins, planetary gears, and bearings) can intensify vibration and even cause resonance. This phenomenon causes abnormal loads on the bearings, severely limiting their maximum allowable speed, making these gearboxes difficult to meet the requirements of high-speed input conditions.

[0003] The Chinese patent application with application number CN201420445424.4 and application date August 8, 2014 discloses a two-stage planetary transmission gearbox, wherein an input shaft with internal teeth at both ends is installed in the lower case body, a first-stage sun gear is connected to the upper end of the input shaft, a first-stage ring gear fixed above the lower case body is arranged outside the first-stage sun gear, a middle case body is fixed above the first-stage ring gear, and first-stage planetary gears are evenly distributed between the first-stage ring gear and the first-stage sun gear. The first-stage planetary gears are installed on the first-stage planetary carrier, and a second-stage sun gear is connected to the upper end of the first-stage planetary carrier. A second-stage ring gear fixed above the middle case body is arranged outside the second-stage sun gear, an upper case body is fixed above the secondary ring gear, and second-stage planetary gears are evenly distributed between the second-stage ring gear and the second-stage sun gear. The second-stage planetary gears are all installed on the second-stage planetary carrier, and the upper and lower ends of the secondary planetary carrier are respectively installed in the upper case body and the middle case body through bearings.

[0004] This design improves transmission efficiency and maintains a compact structure by including internal teeth on both ends of the input shaft to facilitate spline input, screwing the primary and secondary ring gears to the housing to create a coaxial transmission, and making the primary and secondary planetary carriers fully floating, with support plates abutting against the top surface of the sun gear for position control. However, the planetary carrier is still mounted on the housing via bearings and rotates synchronously with the power (i.e., the primary planetary carrier drives the secondary sun gear, while the secondary planetary carrier rotates via bearings). This non-fixed structure is susceptible to vibration and resonance during high-speed input due to mass eccentricity, making it difficult to meet the requirements of high-speed input conditions.

[0005] The information disclosed in this background technology section is only intended to increase understanding of the overall background of the application and should not be considered as an admission or any form of suggestion that the information constitutes the prior art already known to ordinary technicians in this field. Summary of the Invention

[0006] The purpose of the present invention is to overcome the defect that the existing planetary frame is not fixed and cannot meet the high-speed input working condition, and to provide a linear high-speed planetary module with a fixed planetary frame that can meet the high-speed input working condition.

[0007] To achieve the above objectives, the technical solution of the present invention is: A linear high-speed planetary module, the module comprising a motor mounting base, a flange support, and a mounting base arranged in sequence from left to right along the axial direction, wherein the upper and lower edges of the motor mounting base are each provided with a first threaded hole, the upper and lower edges of the flange support are each provided with a second threaded hole, and the upper and lower edges of the left end of the mounting base are each provided with a third threaded hole, the positions of the first threaded hole, the second threaded hole, and the third threaded hole are aligned, two screws respectively pass through the first threaded hole, the second threaded hole, and the third threaded hole in sequence from left to right along the axial direction to fix the motor mounting base, the flange support, and the mounting base, and the axis center lines of the motor mounting base, the flange support, and the mounting base coincide; An input shaft is provided between the motor mounting seat and the flange support, the input shaft being symmetrical up and down along the axis, the left end of the input shaft extending into the motor mounting seat, the middle portion of the input shaft being connected to the motor mounting seat via two first bearings, the two first bearings being symmetrically distributed on the upper and lower sides of the middle portion of the input shaft, the right end of the input shaft being inserted into the left end of the output shaft, and being connected to the left end of the output shaft via two second bearings, the two second bearings being symmetrically distributed on the upper and lower sides of the right end of the input shaft; The left end of the output shaft is connected to the flange support via two third bearings, the two third bearings being symmetrically distributed on the upper and lower sides of the left end of the output shaft. The middle portion of the output shaft is connected to the mounting seat via two fourth bearings, the two fourth bearings being symmetrically distributed on the upper and lower sides of the middle portion of the output shaft. The right end of the output shaft extends axially to the right to the outside of the mounting seat. The shaft section between the third bearing and the fourth bearing on the output shaft meshes with the internal teeth of the external gear, and the external teeth of the external gear mesh with a plurality of gear shafts uniformly distributed circumferentially with the shaft centerline as a reference; The left end of the gear shaft passes through the flange support, and the middle part of the gear shaft is connected to the flange support through the No. 1 fifth bearing and the No. 2 fifth bearing. The No. 1 fifth bearing and the No. 2 fifth bearing are symmetrically distributed on the upper and lower sides of the middle part of the gear shaft, and the No. 1 fifth bearing is located on the upper side of the middle part of the gear shaft. The right end of the gear shaft is connected to the mounting seat through the No. 3 fifth bearing and the No. 4 fifth bearing. The No. 3 fifth bearing and the No. 4 fifth bearing are symmetrically distributed on the upper and lower sides of the right end of the gear shaft, and the No. 3 fifth bearing is located on the upper side of the right end of the gear shaft; The left end of the gear shaft is connected to the spline wheel through a flat key, the spline wheel is engaged with the internal spline of the internal spline planetary wheel, and the external teeth of the internal spline planetary wheel are engaged with the shaft section between the first bearing and the second bearing on the input shaft.

[0008] The number of the gear shafts uniformly distributed circumferentially based on the axis center line is 3-4, and one of the gear shafts is arranged directly above the axis center line, and this gear shaft is the highest gear shaft.

[0009] The left and right sides of the meshing position between the inner spline planetary gear and the spline wheel are both axially fixed by elastic retaining rings through the first hole.

[0010] The left end portion of the gear shaft is sleeved with a first shaft elastic circlip, and the first shaft elastic circlip is fitted with the left end surface of the spline wheel.

[0011] An L-shaped washer is provided between the spline wheel and the flange support, the vertical side of the L-shaped washer is pressed against the right end face of the spline wheel, and the horizontal side of the L-shaped washer is pressed against the outer peripheral surface of the gear shaft.

[0012] A second shaft elastic circlip is sleeved on the output shaft, and the second shaft elastic circlip is in contact with the end face of the external gear.

[0013] A first oil hole is provided at the connection between the flange support and the No. 1 fifth bearing, and the first oil hole is connected to the first lubricating oil groove. A second oil hole is provided at the connection between the mounting seat and the No. 3 fifth bearing, and the second oil hole is connected to the second lubricating oil groove.

[0014] An oil guide plate is welded on the mounting seat, and the oil guide plate is located above the highest gear shaft. The oil guide plate includes an oil baffle plate, and oil guide grooves are provided on both sides of the oil baffle plate. The left end opening of the oil guide groove faces the first lubricating oil groove, and the right end opening of the oil guide groove faces the second lubricating oil groove.

[0015] The left end of the input shaft is an internal spline structure or a flat key shaft structure.

[0016] The right end of the output shaft is any one of an external gear structure, an external spline structure, an internal spline structure, and a flat key shaft structure.

[0017] Compared with the prior art, the present invention has the following beneficial effects: 1. In a linear high-speed planetary module of the present invention, the module includes a motor mounting seat, a flange support and a mounting seat arranged in sequence from left to right along the axial direction. The three are fixedly connected by a first threaded hole, a second threaded hole, a third threaded hole and two screws, and the axis lines coincide with each other; the input shaft is connected to the motor mounting seat and the output shaft respectively through multiple groups of first bearings and second bearings, and the output shaft is connected to the flange support and the mounting seat respectively through multiple groups of third bearings and fourth bearings; the output shaft is meshed with an external gear, the external gear is meshed with multiple groups of gear shafts, and the gear shaft is connected to the flange support and the mounting seat respectively through multiple groups of fifth bearings. The left end of the gear shaft is connected to the spline wheel through a flat key, the spline wheel is meshed with the internal spline planetary gear, and the internal spline planetary gear is meshed with a specific shaft section of the input shaft. During use, the motor mounting base is fixed to the motor via the screw holes on the left end face. The motor output power shaft is connected to the input shaft. After the motor is started, power is transmitted to the input shaft, which drives the internal spline planetary gear to rotate. The internal spline planetary gear then drives the spline gear and the gear shaft. The gear shaft then drives the external gear, ultimately rotating the output shaft and outputting power from the right end. The advantages of this invention include: First, the use of evenly distributed fixed gear shafts replaces the traditional non-fixed planetary carrier structure, eliminating the need to rely on the planetary carrier's rotation to transmit power. This structurally eliminates the hidden danger of mass eccentricity during high-speed rotation of the planetary carrier, breaking through the speed limit imposed by the unbalanced centrifugal force generated by the rotation of the planetary carrier in traditional planetary gearboxes, and can meet high-speed input conditions of 1800 rpm and above. Second point: All shafts adopt a double-end support structure. The input shaft and the internal spline planetary gear, and the gear shaft and the external gear all form a transmission pair through external tooth meshing, which improves the structural rigidity and transmission efficiency, and ensures stable operation at an input speed of 1800rpm and above.

[0018] Therefore, the present invention breaks through the input speed bottleneck caused by the rotation of the planetary carrier of the traditional planetary gearbox by fixing the planetary carrier structure, can meet the high-speed input conditions of 1800rpm and above, and achieve stable operation under high-speed input conditions.

[0019] 2. In a linear high-speed planetary module of the present invention, the left and right sides of the meshing point between the internal spline planetary gear and the spline wheel are axially fixed by elastic circlips through the first hole; the left end portion of the gear shaft is sleeved with a first shaft elastic circlip, and the first shaft elastic circlip is in contact with the left end face of the spline wheel; an L-shaped washer is provided between the spline wheel and the flange support, the vertical side of the L-shaped washer is in contact with the right end face of the spline wheel, and the horizontal side of the L-shaped washer is in contact with the outer peripheral surface of the gear shaft; the output shaft is sleeved with a second shaft elastic circlip, and the second shaft elastic circlip is in contact with the end face of the external gear. During application, when power is transmitted from the input shaft to the internal spline planetary gear, the holes on the left and right sides use elastic circlips to fix the internal spline planetary gear axially on the spline wheel. The spline of the internal spline planetary gear and the spline wheel reserve clearance to allow the planetary gear to be slightly adjusted in the diameter direction, so that the load of multiple sets of gear shafts is balanced. When encountering impact, the spline pair consumes energy through deformation, reducing the impact transmitted to the gear shaft; after the spline wheel is connected to the gear shaft through a flat key, the first shaft uses an elastic circlip and an L-shaped washer to match. The first shaft uses an elastic circlip to match the left and right sides of the spline wheel. The end faces are tightly attached, with the vertical edge of the L-shaped washer pressing against its right end face, and its horizontal edge enclosing the outer circumference of the gear shaft to achieve axial positioning of the spline wheel. Under this structure, the axial vibration of the internal spline planetary gear is absorbed by the elastic circumferential ring of the first shaft, and the spline clearance isolates the vibration of the internal spline planetary gear from that of the gear shaft, avoiding resonance superposition. When power is transmitted to the output shaft, the elastic circumferential ring of the second shaft constrains the axial displacement of the external gear through double-end limiters, and the elastic deformation of the elastic circumferential ring of the second shaft absorbs the vibration energy generated by the high-speed meshing of the gear pair, reducing output shaft vibration. Therefore, the present invention can effectively reduce vibration under high-speed operating conditions and improve transmission stability and reliability.

[0020] 3. In a linear high-speed planetary module of the present invention, a first oil hole is provided at the connection between the flange support and the No. 1 fifth bearing, and the first oil hole is communicated with the first lubricating oil groove; a second oil hole is provided at the connection between the mounting seat and the No. 3 fifth bearing, and the second oil hole is communicated with the second lubricating oil groove; an oil guide plate is welded on the mounting seat, and the oil guide plate is located above the highest gear shaft. The oil guide plate includes an oil baffle plate, and oil guide grooves are provided on both sides of the oil baffle plate. The left end opening of the oil guide groove faces the first lubricating oil groove, and the right end opening of the oil guide groove faces the second lubricating oil groove. During use, the lubricating oil generated by the swinging of the teeth of multiple gear shafts, external gears and output shafts will be collected by the oil guide plate installed on the mounting seat. The oil baffle plate of the oil guide plate acts as a barrier to block the lubricating oil splashing upwards, and the oil guide grooves symmetrically distributed on both sides of the oil baffle plate form a collection channel. As the operation continues, the lubricating oil will be continuously collected into the oil guide groove. Under the action of gravity and centrifugal force, the lubricating oil will flow into the first oil groove and the second oil groove through the diversion of the oil guide groove, and through the corresponding first oil hole and second oil hole, it will be introduced into the installation position of the No. 1 fifth bearing and the No. 3 fifth bearing. The overflowing lubricating oil will also flow naturally along the bearing seat, providing immersion lubrication for the gear shaft and the flange support and other bearings between the mounting seat, effectively reducing friction loss, extending the service life of the bearings, and ensuring the stable operation of this design under high-speed and heavy-load conditions. Therefore, the present invention realizes precise lubrication of bearings and shaft systems under high-speed operation through the oil guide plate, oil holes and oil grooves, effectively reducing friction loss and improving the stability of high-speed operation.

[0021] 4. In a linear high-speed planetary module of the present invention, the right end of the output shaft is any one of an external gear structure, an external spline structure, an internal spline structure, and a flat key shaft structure. In application, when a rigid connection with a low-speed gearbox is required to transmit a large torque, an external gear structure can be selected to achieve efficient power transmission through gear meshing; if the input component of the low-speed gearbox is in the form of a spline hole, the external spline structure or the internal spline structure can rely on a tight spline fit to ensure the stability and coaxiality of power transmission; and the flat key shaft structure is suitable for scenes with relatively low requirements for installation accuracy and the need for rapid disassembly and assembly. Through the circumferential positioning of the flat key and the fit of the keyway, the docking with the low-speed gearbox can be quickly completed. According to the interface form, load characteristics and working conditions of the low-speed gearbox, the corresponding output shaft structure is selected, breaking the limitation of the traditional single output form. Therefore, the present invention realizes flexible adaptation to different low-speed gearboxes through the diversified structural design of the right end of the output shaft, with a wide range of applications and strong practicality. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 It is a structural schematic diagram of the present invention.

[0023] Figure 2 yes Figure 1 Schematic diagram of the structure of the oil guide plate.

[0024] Figure 3 yes Figure 2 Side view of the center oil guide pan.

[0025] Figure 4 yes Figure 1 The right end of the middle output shaft is a schematic diagram of the internal spline structure.

[0026] Figure 5 yes Figure 1 The right end of the middle output shaft is a structural diagram of the flat key shaft.

[0027] Figure 6 yes Figure 1 Application diagram of the right end of the middle output shaft installed with the low-speed gearbox.

[0028] Figure 7 yes Figure 1 Application diagram of the left end of the input shaft and the motor installation.

[0029] In the figure: motor mounting base 1, spline wheel 10, elastic ring for first hole 11, first threaded hole 111, L-shaped washer 12, internal spline planetary gear 13, flange support 14, second threaded hole 141, first oil hole 142, first lubricating oil groove 143, No. 1 fifth bearing 151, No. 2 fifth bearing 152, No. 3 fifth bearing 153, No. 4 fifth bearing 154, oil guide plate 16, oil baffle plate 161, oil guide groove 162, fourth shaft Bearing 17, second oil seal 18, output shaft 19, first bearing 2, mounting seat 20, third threaded hole 201, second oil hole 202, second oil groove 203, external gear 21, elastic ring for second shaft 22, third bearing 23, screw 24, second bearing 3, axis 30, input shaft 4, motor 40, first oil seal 5, low-speed gearbox 50, elastic ring for second hole 6, gear shaft 7, elastic ring for first shaft 8, flat key 9. DETAILED DESCRIPTION

[0030] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0031] See also Figure 1 — Figure 5, a linear high-speed planetary module, the module includes a motor mounting base 1, a flange support 14 and a mounting base 20 arranged in sequence from left to right along the axial direction, the upper and lower edges of the motor mounting base 1 are each provided with a first threaded hole 111, the upper and lower edges of the flange support 14 are each provided with a second threaded hole 141, and the upper and lower edges of the left end of the mounting base 20 are each provided with a third threaded hole 201, the positions of the first threaded hole 111, the second threaded hole 141, and the third threaded hole 201 are aligned, two screws 24 respectively pass through the first threaded hole 111, the second threaded hole 141, and the third threaded hole 201 in sequence from left to right along the axial direction to fix the motor mounting base 1, the flange support 14 and the mounting base 20, and the axis center lines 30 of the motor mounting base 1, the flange support 14 and the mounting base 20 coincide; An input shaft 4 is provided between the motor mounting seat 1 and the flange support 14. The input shaft 4 is symmetrical up and down along the axis 30. The left end of the input shaft 4 extends into the motor mounting seat 1. The middle part of the input shaft is connected to the motor mounting seat 1 through two first bearings 2. The two first bearings 2 are symmetrically distributed on the upper and lower sides of the middle part of the input shaft 4. The right end of the input shaft 4 is inserted into the left end of the output shaft 19 and is connected to the left end of the output shaft 19 through two second bearings 3. The two second bearings 3 are symmetrically distributed on the upper and lower sides of the right end of the input shaft 4. The left end of the output shaft 19 is connected to the flange support 14 via two third bearings 23, which are symmetrically located above and below the left end of the output shaft 19. The middle of the output shaft 19 is connected to the mounting seat 20 via two fourth bearings 17, which are symmetrically located above and below the middle of the output shaft 19. The right end of the output shaft 19 extends axially to the right to the outside of the mounting seat 20. The shaft section of the output shaft 19 between the third bearing 23 and the fourth bearing 17 meshes with the internal teeth of the external gear 21, and the external teeth of the external gear 21 mesh with a plurality of gear shafts 7 uniformly distributed circumferentially with respect to the axis 30; The left end of the gear shaft 7 passes through the flange support 14, and the middle part of the gear shaft 7 is connected to the flange support 14 through the No. 1 fifth bearing 151 and the No. 2 fifth bearing 152. The No. 1 fifth bearing 151 and the No. 2 fifth bearing 152 are symmetrically distributed on the upper and lower sides of the middle part of the gear shaft 7. The No. 1 fifth bearing 151 is located on the upper side of the middle part of the gear shaft 7. The right end of the gear shaft 7 is connected to the mounting seat 20 through the No. 3 fifth bearing 153 and the No. 4 fifth bearing 154. The No. 3 fifth bearing 153 and the No. 4 fifth bearing 154 are symmetrically distributed on the upper and lower sides of the right end of the gear shaft 7. The No. 3 fifth bearing 153 is located on the upper side of the right end of the gear shaft 7. The left end of the gear shaft 7 is connected to the spline wheel 10 through a flat key 9. The spline wheel 10 meshes with the internal splines of the internal spline planetary wheel 13. The external teeth of the internal spline planetary wheel 13 mesh with the shaft section on the input shaft 4 located between the first bearing 2 and the second bearing 3.

[0032] The number of the gear shafts 7 uniformly distributed circumferentially based on the axis 30 is 3-4, and one of the gear shafts 7 is arranged directly above the axis 30, and this gear shaft 7 is the highest gear shaft 7.

[0033] The left and right sides of the meshing portion between the internal spline planetary gear 13 and the spline wheel 10 are both axially fixed by elastic retaining rings 11 through the first hole.

[0034] The left end portion of the gear shaft 7 is sleeved with a first shaft circlip 8 , which is in contact with the left end face of the spline wheel 10 .

[0035] An L-shaped washer 12 is provided between the spline wheel 10 and the flange support 14 , wherein the vertical side of the L-shaped washer 12 is in close contact with the right end face of the spline wheel 10 , and the horizontal side of the L-shaped washer 12 is in close contact with the outer circumference of the gear shaft 7 .

[0036] The output shaft 19 is sleeved with a second shaft circlip 22 , which is in contact with the end face of the external gear.

[0037] A first oil hole 142 is provided at the connection between the flange support 14 and the No. 1 fifth bearing 151, and the first oil hole 142 is connected to the first lubricating oil groove 143. A second oil hole 202 is provided at the connection between the mounting seat 20 and the No. 3 fifth bearing 153, and the second oil hole 202 is connected to the second lubricating oil groove 203.

[0038] An oil guide plate 16 is welded on the mounting seat 20, and the oil guide plate 16 is located above the highest gear shaft 7. The oil guide plate 16 includes an oil baffle plate 161, and oil guide grooves 162 are provided on both sides of the oil baffle plate. The left end opening of the oil guide groove 162 faces the first lubricating oil groove 143, and the right end opening of the oil guide groove 162 faces the second lubricating oil groove 203.

[0039] The left end of the input shaft 4 is an internal spline structure or a flat key shaft structure.

[0040] The right end of the output shaft 19 is any one of an external gear structure, an external spline structure, an internal spline structure, and a flat key shaft structure.

[0041] The supplementary technical features of the present invention are as follows: In this design, it is preferred to provide a first oil seal 5 between the shaft section on the left side of the first bearing 2 on the input shaft 4 and the motor mounting seat 1, and at the same time, a second hole elastic retaining ring 6 is sleeved on the left end of the input shaft 4 for axial limitation. The first oil seal 5 is installed on the motor mounting seat 1, which can effectively prevent the lubricating oil from leaking from the connection between the input shaft 4 and the motor mounting seat 1, and at the same time block external dust and impurities from entering the interior, thereby ensuring a clean and lubricated environment for the bearings and transmission components on the input shaft 4.

[0042] In this design, it is preferred to provide a second oil seal 18 between the shaft section on the right side of the fourth bearing 17 on the output shaft 19 and the mounting seat 20. The second oil seal 18 seals the right end of the output shaft 19. The second oil seal 18 can prevent lubricating oil from overflowing from the gap between the output shaft 19 and the mounting seat 20, while isolating external pollutants, ensuring the stable operation of the output shaft 19 and related bearings, and extending the service life of the transmission system.

[0043] Example 1: See also Figure 1A linear high-speed planetary module, the module includes a motor mounting base 1, a flange support 14 and a mounting base 20 arranged in sequence from left to right along the axial direction, the upper and lower edges of the motor mounting base 1 are each provided with a first threaded hole 111, the upper and lower edges of the flange support 14 are each provided with a second threaded hole 141, and the upper and lower edges of the left end of the mounting base 20 are each provided with a third threaded hole 201. The positions of the first threaded hole 111, the second threaded hole 141, and the third threaded hole 201 are aligned, and two screws 24 pass through the first threaded hole 111, the second threaded hole 141, and the third threaded hole 201 in sequence from left to right along the axial direction to fix the motor mounting base 1, the flange support 14 and the mounting base 20. , the motor mounting base 1, the flange support 14 and the mounting base 20, the axis center lines 30 of the three coincide; an input shaft 4 is provided between the motor mounting base 1 and the flange support 14, the input shaft 4 is symmetrical along the axis center line 30, the left end of the input shaft 4 extends into the motor mounting base 1, the middle part of the input shaft is connected to the motor mounting base 1 through two first bearings 2, the two first bearings 2 are symmetrically distributed on the upper and lower sides of the middle part of the input shaft 4, the right end of the input shaft 4 is inserted into the left end of the output shaft 19, and is connected to the left end of the output shaft 19 through two second bearings 3, the two second bearings 3 are symmetrically distributed on the upper and lower sides of the right end of the input shaft 4; the left end of the output shaft 19 is connected to the flange support 14 through two third bearings 23, The two third bearings 23 are symmetrically distributed on the upper and lower sides of the left end of the output shaft 19. The middle part of the output shaft 19 is connected to the mounting seat 20 through two fourth bearings 17. The two fourth bearings 17 are symmetrically distributed on the upper and lower sides of the middle part of the output shaft 19. The right end of the output shaft 19 extends axially to the right to the outside of the mounting seat 20; the shaft section between the third bearing 23 and the fourth bearing 17 on the output shaft 19 is meshed with the internal teeth of the external gear 21, and the external teeth of the external gear 21 are meshed with a number of gear shafts 7 that are uniformly distributed circumferentially with the axis 30 as the reference; the left end of the gear shaft 7 passes through the flange support 14, and the middle part of the gear shaft 7 is connected to the flange support 14 through the No. 1 fifth bearing 151 and the No. 2 fifth bearing 152. The fifth bearing No. 151 and the fifth bearing No. 2 152 are symmetrically distributed on the upper and lower sides of the middle part of the gear shaft 7, the fifth bearing No. 1 151 is located on the upper side of the middle part of the gear shaft 7, and the right end of the gear shaft 7 is connected to the mounting seat 20 through the fifth bearing No. 3 153 and the fifth bearing No. 4 154. The fifth bearing No. 3 153 and the fifth bearing No. 4 154 are symmetrically distributed on the upper and lower sides of the right end of the gear shaft 7, and the fifth bearing No. 3 153 is located on the upper side of the right end of the gear shaft 7; the left end of the gear shaft 7 is connected to the spline wheel 10 through the flat key 9, the spline wheel 10 is meshed with the inner spline of the inner spline planetary wheel 13, and the outer teeth of the inner spline planetary wheel 13 are meshed with the shaft section on the input shaft 4 located between the first bearing 2 and the second bearing 3.

[0044] When in use, the power is transmitted to the input shaft 4 through the power shaft of the motor installed at the left end of the motor mounting base 1. After the left end of the input shaft 4 receives the power, it relies on the two first bearings 2 symmetrically distributed on the upper and lower sides of the middle part, and the two second bearings 3 at the right end to maintain stable support. Then the external teeth of the shaft section of the input shaft 4 located between the first bearing 2 and the second bearing 3 are engaged with the external teeth of the internal spline planetary gear 13 installed at the left end of the multiple gear shafts 7, driving the internal spline planetary gear 13 to rotate. The internal spline planetary gear 13 is engaged with the spline wheel 10 through the internal spline, and the spline wheel 10 is then connected to the left end of the gear shaft 7 through the flat key 9, thereby the input shaft 4 It drives multiple gear shafts 7 to rotate. The middle parts of these gear shafts 7 are installed on the flange support 14 with the help of the No. 1 fifth bearing 151 and the No. 2 fifth bearing 152, and the right ends are connected to the mounting seat 20 through the No. 3 fifth bearing 153 and the No. 4 fifth bearing 154. The external teeth on the multiple gear shafts 7 are engaged with the external gear 21, and the external gear 21 is engaged with the shaft section between the third bearing 23 and the fourth bearing 17 on the output shaft 19. The left end of the output shaft 19 is connected to the flange support 14 through two third bearings 23, and the middle part is fixed to the mounting seat 20 through two fourth bearings 17. Finally, the power is stably output from the right end of the output shaft 19.

[0045] Example 2: The basic content is the same as Example 1, except that: The number of gear shafts 7 uniformly distributed circumferentially with the axis center line 30 as a reference is 3-4, and one of the gear shafts 7 is arranged directly above the axis center line 30, and this gear shaft 7 is the highest gear shaft 7.

[0046] In application, if the number of gear shafts 7 is 3, then except for the highest gear shaft 7 located directly above the axis centerline 30, the other two gear shafts 7 are symmetrically distributed below the axis centerline 30 with the axis centerline 30 as the reference, forming a regular triangle layout with the highest gear shaft 7; if the number of gear shafts 7 is 4, then except for the highest gear shaft 7, the other three gear shafts 7 are evenly distributed every 90 degrees in the circumferential direction with the axis centerline 30 as the reference, forming a square layout.

[0047] Example 3: The basic content is the same as Example 1, except that: The left and right sides of the meshing point between the inner spline planetary gear 13 and the spline wheel 10 are axially fixed by elastic circlips 11 through the first hole; the left end of the gear shaft 7 is sleeved with a first shaft elastic circlip 8, and the first shaft elastic circlip 8 is in contact with the left end face of the spline wheel 10; an L-shaped washer 12 is provided between the spline wheel 10 and the flange support 14, the vertical edge of the L-shaped washer 12 is in contact with the right end face of the spline wheel 10, and the horizontal edge of the L-shaped washer 12 is in contact with the outer circumferential surface of the gear shaft 7; the output shaft 19 is sleeved with a second shaft elastic circlip 22, and the second shaft elastic circlip 22 is in contact with the end face of the external gear.

[0048] During application, when power is transmitted from the input shaft 4 to the internal spline planetary gear 13, the internal spline planetary gear 13 is axially positioned with the spline wheel 10 using elastic circlips 11 through the first holes on the left and right sides. After the power is transmitted to the spline wheel 10 through the internal spline planetary gear 13, the spline wheel 10 drives the gear shaft 7 to rotate through the flat key 9. At this time, the first shaft elastic circlip 8 and the L-shaped washer 12 jointly limit the axial displacement of the spline wheel 10 on the gear shaft 7. As the gear shaft 7 rotates, its external teeth engage with the external gear 21, driving the output shaft 19 to rotate, while the second shaft elastic circlip 22 on the output shaft 19 ensures that the axial position of the external gear 21 on the output shaft 19 is fixed.

[0049] Example 4: The basic content is the same as Example 1, except that: See also Figure 1 and Figure 2 A first oil hole 142 is provided at the connection between the flange support 14 and the No. 1 fifth bearing 151, and the first oil hole 142 is communicated with the first lubricating oil groove 143. A second oil hole 202 is provided at the connection between the mounting seat 20 and the No. 3 fifth bearing 153, and the second oil hole 202 is communicated with the second lubricating oil groove 203; an oil guide plate 16 is welded on the mounting seat 20, and the oil guide plate 16 is located above the highest gear shaft 7. The oil guide plate 16 includes an oil baffle plate 161, and oil guide grooves 162 are provided on both sides of the oil baffle plate. The left end opening of the oil guide groove 162 faces the first lubricating oil groove 143, and the right end opening of the oil guide groove 162 faces the second lubricating oil groove 203.

[0050] During use, the lubricating oil generated by the swinging of the teeth of the high-speed running gear shaft 7, the external gear 21 and the output shaft 19 is intercepted by the oil baffle plate 161 of the oil guide plate 16, and the oil guide grooves 162 on both sides collect the lubricating oil respectively. The opening on the left side of the oil guide groove 162 is aligned with the first lubricating oil groove 143 of the flange support 14, and the lubricating oil flows into the installation position of the No. 1 fifth bearing 151 through the first oil hole 142; the opening on the right side of the oil guide groove 162 is aligned with the second lubricating oil groove 203 of the mounting seat 20, and the lubricating oil flows into the installation position of the No. 3 fifth bearing 153 through the second oil hole 202.

[0051] Example 5: The basic content is the same as Example 1, except that: See also Figure 3 —5. The right end of the output shaft 19 is any one of an external gear structure, an external spline structure, an internal spline structure, and a flat key shaft structure.

[0052] During application, when the right end of the output shaft 19 is an external gear structure, power transmission can be achieved by directly engaging with the internal gear of the low-speed gearbox 50, which is suitable for scenarios requiring a larger torque output; if it is an external spline structure, it can be combined with a coupling or transmission component with a corresponding internal spline to achieve efficient torque transmission, and can adapt to a certain degree of axial displacement and angular deviation; when an internal spline structure is adopted, it can be directly mounted on the external spline input shaft of the low-speed gearbox 50, providing a compact and stable connection method; and the flat key shaft structure can be circumferentially positioned with the transmission component of the low-speed gearbox 50 through the keyway, which is convenient for quick installation and disassembly, and is suitable for transmission systems that require frequent replacement or adjustment.

[0053] The above description is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above embodiment. Any equivalent modifications or changes made by ordinary technicians in this field based on the contents disclosed in the present invention should be included in the protection scope recorded in the claims.

Claims

1. A linear high-speed planetary module, characterized by: The module comprises a motor mounting base (1), a flange support (14) and a mounting base (20) which are arranged in sequence from left to right along the axial direction, wherein the upper and lower edges of the motor mounting base (1) are provided with a first threaded hole (111), the upper and lower edges of the flange support (14) are provided with a second threaded hole (141), and the upper and lower edges of the left end of the mounting base (20) are provided with a third threaded hole (201), the positions of the first threaded hole (111), the second threaded hole (141) and the third threaded hole (201) are aligned, and two screws (24) pass through the first threaded hole (111), the second threaded hole (141) and the third threaded hole (201) in sequence from left to right along the axial direction to fix the motor mounting base (1), the flange support (14) and the mounting base (20), and the axis center lines (30) of the motor mounting base (1), the flange support (14) and the mounting base (20) coincide with each other; An input shaft (4) is provided between the motor mounting seat (1) and the flange support (14), the input shaft (4) being symmetrical in the upper and lower directions along the axis (30), the left end of the input shaft (4) extending into the motor mounting seat (1), the middle portion of the input shaft being connected to the motor mounting seat (1) via two first bearings (2), the two first bearings (2) being symmetrically distributed on the upper and lower sides of the middle portion of the input shaft (4), the right end of the input shaft (4) being inserted into the left end of the output shaft (19), and being connected to the left end of the output shaft (19) via two second bearings (3), the two second bearings (3) being symmetrically distributed on the upper and lower sides of the right end of the input shaft (4); The left end of the output shaft (19) is connected to the flange support (14) through two third bearings (23), and the two third bearings (23) are symmetrically distributed on the upper and lower sides of the left end of the output shaft (19). The middle part of the output shaft (19) is connected to the mounting seat (20) through two fourth bearings (17), and the two fourth bearings (17) are symmetrically distributed on the upper and lower sides of the middle part of the output shaft (19). The right end of the output shaft (19) extends axially to the right to the outside of the mounting seat (20); The shaft section on the output shaft (19) between the third bearing (23) and the fourth bearing (17) meshes with the internal teeth of the external gear (21), and the external teeth of the external gear (21) mesh with a plurality of gear shafts (7) uniformly distributed in the circumferential direction with the axis (30) as a reference; The left end of the gear shaft (7) passes through the flange support (14), and the middle of the gear shaft (7) is connected to the flange support (14) through the No. 1 fifth bearing (151) and the No. 2 fifth bearing (152), and the No. 1 fifth bearing (151) and the No. 2 fifth bearing (152) are symmetrically distributed on the upper and lower sides of the middle of the gear shaft (7), and the No. 1 fifth bearing (151) is located on the upper side of the middle of the gear shaft (7). The right end of the gear shaft (7) is connected to the mounting seat (20) through the No. 3 fifth bearing (153) and the No. 4 fifth bearing (154), and the No. 3 fifth bearing (153) and the No. 4 fifth bearing (154) are symmetrically distributed on the upper and lower sides of the right end of the gear shaft (7), and the No. 3 fifth bearing (153) is located on the upper side of the right end of the gear shaft (7); The left end of the gear shaft (7) is connected to the spline wheel (10) via a flat key (9), the spline wheel (10) meshes with the internal splines of the internal spline planetary wheel (13), and the external teeth of the internal spline planetary wheel (13) mesh with the shaft section on the input shaft (4) located between the first bearing (2) and the second bearing (3).

2. A linear high-speed planetary module according to claim 1, characterized in that: The number of the gear shafts (7) uniformly distributed in the circumferential direction based on the axis center line (30) is 3-4, and one of the gear shafts (7) is arranged directly above the axis center line (30), and this gear shaft (7) is the highest gear shaft (7).

3. A linear high-speed planetary module according to claim 1 or 2, characterized in that: The left and right sides of the meshing position between the inner spline planetary wheel (13) and the spline wheel (10) are both axially fixed by elastic retaining rings (11) through the first hole.

4. The linear high-speed planetary module according to claim 3, characterized in that: The left end portion of the gear shaft (7) is sleeved with a first shaft elastic retaining ring (8), and the first shaft elastic retaining ring (8) is fitted with the left end face of the spline wheel (10).

5. The linear high-speed planetary module according to claim 4, characterized in that: An L-shaped washer (12) is provided between the spline wheel (10) and the flange support (14), wherein the vertical edge of the L-shaped washer (12) is in close contact with the right end face of the spline wheel (10), and the horizontal edge of the L-shaped washer (12) is in close contact with the outer peripheral surface of the gear shaft (7).

6. The linear high-speed planetary module according to claim 5, characterized in that: A second shaft elastic circlip (22) is sleeved on the output shaft (19), and the second shaft elastic circlip (22) is fitted to the end face of the external gear.

7. A linear high-speed planetary module according to claim 1 or 2, characterized in that: A first oil hole (142) is provided at the connection between the flange support (14) and the No. 1 fifth bearing (151), and the first oil hole (142) is communicated with the first lubricating oil groove (143). A second oil hole (202) is provided at the connection between the mounting seat (20) and the No. 3 fifth bearing (153), and the second oil hole (202) is communicated with the second lubricating oil groove (203).

8. The linear high-speed planetary module according to claim 7, characterized in that: An oil guide plate (16) is welded on the mounting seat (20), and the oil guide plate (16) is located above the highest gear shaft (7). The oil guide plate (16) includes an oil baffle plate (161), and oil guide grooves (162) are provided on both sides of the oil baffle plate. The left end opening of the oil guide groove (162) faces the first lubricating oil groove (143), and the right end opening of the oil guide groove (162) faces the second lubricating oil groove (203).

9. A linear high-speed planetary module according to claim 1 or 2, characterized in that: The left end of the input shaft (4) is an internal spline structure or a flat key shaft structure.

10. A linear high-speed planetary module according to claim 1 or 2, characterized in that: The right end of the output shaft (19) is any one of an external gear structure, an external spline structure, an internal spline structure, and a flat key shaft structure.

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