CN109083985B - Gear reducer with accurate and reliable reduction ratio - Google Patents
Gear reducer with accurate and reliable reduction ratio Download PDFInfo
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- CN109083985B CN109083985B CN201811088978.2A CN201811088978A CN109083985B CN 109083985 B CN109083985 B CN 109083985B CN 201811088978 A CN201811088978 A CN 201811088978A CN 109083985 B CN109083985 B CN 109083985B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- General Engineering & Computer Science (AREA)
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Abstract
The invention discloses a gear reducer with accurate and reliable reduction ratio, comprising a shell; an inner fluted disc; the planet gears are arranged in the inner fluted disc at intervals; a sun wheel set is arranged on the column body between the center of the gear column and the first end of the gear column; the at least two follow-up wheel sets are symmetrically arranged on the periphery of the sun wheel set, the radial positions of the follow-up wheel sets are fixed on the inner fluted disc, and the follow-up wheel sets synchronously and axially move along with the gear columns; the grading gear set is sleeved on the periphery of the follow-up gear set and synchronously and axially moves along with the gear column; an inner gear ring is arranged on the inner side wall of each grading gear, the innermost end of the follow-up gear is meshed with the outermost side wall of the corresponding sun gear, the outermost end of the follow-up gear is meshed with the inner gear ring of the corresponding grading gear, and the outermost side wall of each grading gear is axially and selectively meshed with the innermost side wall of the planet gear. The invention solves the technical problem that the precision of the output reduction ratio of the speed reducer is unreliable in the prior art.
Description
Technical Field
The invention relates to the technical field of speed reducers, in particular to a gear speed reducer with accurate and reliable speed reduction ratio.
Background
The speed reducer is generally used for low-rotating-speed and large-torque transmission equipment, and the purpose of reducing speed of a motor, an internal combustion engine or other high-speed running power is achieved by meshing a gear with a small number of teeth on an input shaft of the speed reducer with a large gear on an output shaft.
At present, in order to enrich the reduction ratio of a speed reducer and provide more selectivity, a stepless speed reducer is appeared in the prior art, the reduction ratio is continuously adjustable, but the output reliability of the stepless speed reducer is poor, and the accurate and reliable reduction ratio cannot be provided, so that the industrial application is frustrated.
Disclosure of Invention
An object of the present invention is to solve at least the above problems and to provide at least the advantages described later.
It is a further object of the present invention to provide a gear reducer with an accurate and reliable reduction ratio, which is equipped with a plurality of continuously adjustable reduction ratios that can be adjusted automatically according to the actual requirements, which solves the technical problem of the prior art that the reduction ratio output by the reducer is not accurate.
To achieve these objects and other advantages in accordance with the purpose of the invention, there is provided a gear reducer having an accurate and reliable reduction ratio, comprising:
the first end of the shell is provided with an open structure, and the opening of the shell is closed by an end cover;
the inner fluted disc is rotatably arranged in an accommodating space formed by the end cover and the shell, and the opening direction of the shell is opposite to that of the inner fluted disc;
the planet gears are arranged in the inner fluted disc at intervals, the axial directions of the planet gears are parallel to the axial direction of the inner fluted disc, and the outer side walls of the planet gears are meshed with the inner side walls of the inner fluted disc;
the gear column is axially arranged at the center of the inner fluted disc, a sun wheel set is arranged on a column body between the center of the gear column and the first end of the gear column, the sun wheel set comprises a plurality of sun wheels which are continuously and concentrically arranged, the diameter of each sun wheel is gradually reduced towards the direction of the first end of the gear column, and the outer side end of each sun wheel is distributed in a step shape which is gradually contracted towards the first end of the gear column on the axis; a first shaft connecting seat is arranged at the end of the second end of the gear column, and a limiting ring body is convexly arranged on a column body between the first shaft connecting seat and the sun gear set; a second shaft connecting seat is formed in the center of the outer side of the inner fluted disc, and an output connecting shaft is arranged in the second shaft connecting seat;
the follow-up wheel sets are symmetrically arranged on the periphery of the sun wheel set, the radial positions of the follow-up wheel sets are fixed on the inner fluted disc, the follow-up wheel sets synchronously and axially move along with the gear column, each follow-up wheel set comprises a plurality of follow-up gears concentrically arranged at intervals, the diameter of each follow-up gear gradually increases towards the bottom direction of the inner fluted disc, and the outer side ends of the follow-up gears are distributed in a step shape gradually increasing towards the first end of the gear column on the axis; and
the grading gear set is sleeved on the periphery of the follow-up gear set and synchronously and axially moves along with the gear column, the grading gear set comprises a plurality of grading gears which are continuously and concentrically arranged, a hollow part is concentrically arranged in each grading gear, the outer diameters of the grading gears are consistent, the inner diameters of the grading gears are gradually increased towards the bottom direction of the inner fluted disc, and the inner side ends of the grading gears are distributed in a step shape which gradually shrinks towards the second end of the gear column on the axis;
an inner gear ring is arranged on the inner side wall of each grading gear, the innermost end of the follow-up gear is meshed with the outermost side wall corresponding to the sun gear, the outermost end of the follow-up gear is meshed with the inner gear ring corresponding to the grading gears, and the outermost side wall of each grading gear is axially and selectively meshed with the innermost side wall of the planet gear.
Preferably, the sun gear set comprises a first sun gear, a second sun gear, a third sun gear, a fourth sun gear, a fifth sun gear and a fourth sun gear, wherein the first sun gear, the second sun gear and the fifth sun gear rotate synchronously with the gear column, and the diameters of the first sun gear, the second sun gear and the fifth sun gear are sequentially reduced; the follow-up wheel set comprises a first follow-up gear, a second follow-up gear, a third follow-up gear, a fourth follow-up gear and a fourth follow-up gear, wherein the first follow-up gear, the second follow-up gear and the third follow-up gear rotate independently, and the diameters of the first follow-up gear, the second follow-up gear and the fourth follow-up gear are gradually increased; the hierarchical gear train includes first hierarchical gear to fifth hierarchical gear, first to fifth hierarchical gear independently rotate, the internal diameter of first to fifth hierarchical gear is crescent.
Preferably, the thickness of each sun gear is not less than that of the follower gear, a first concave cavity is formed in the outer side wall of each sun gear, and the outer side wall of each follower gear is installed in the first concave cavity; the axial positions of the first to fifth sun gears and the first to fifth follow-up gears are in one-to-one correspondence, and the first to fifth sun gears are meshed with the first to fifth follow-up gears at the corresponding positions;
the thickness of each grading gear is consistent with that of the sun gear and is not less than that of the planet gear; a second concave cavity is formed in the side wall of the inner gear ring of the grading gear, and the outer side wall of the follow-up gear is installed in the second concave cavity; the first to fifth step gears are in one-to-one correspondence with the axial positions of the first to fifth follow-up gears, and the inner gear rings of the first to fifth step gears are meshed with the first to fifth follow-up gears at the corresponding positions;
the outer side walls of the first to fifth step gears are selectively meshed with the planet gears at corresponding positions.
Preferably, the first end of the shell and the end cover are sequentially connected through a screw rod to form an integral structure, a first through hole is formed in the center of the end cover, and the output connecting body shaft penetrates through the first through hole and extends outwards for a certain distance.
Preferably, a first constant head tank is seted up to the first end of gear post, the internal surface center of internal tooth dish is provided with a second constant head tank, first constant head tank and second constant head tank set up relatively, it is equipped with a spring to press from both sides between first constant head tank and the second constant head tank, when the spring is in normal condition, first constant head tank and second constant head tank interval certain distance, fifth gear with the planet wheel meshing.
Preferably, the thickness of the housing is not less than the distance between the first sun gear and the first positioning groove, a guide groove is formed in a cylinder body at the second end of the gear column, a circular slip ring is rotatably arranged in the guide groove, at least two connecting rods symmetrically extend from the periphery of the circular slip ring, the direction of each connecting rod is perpendicular to the axial direction of the gear column, a guide sleeve is arranged at the other end of each connecting rod, a guide column is movably arranged in each guide sleeve, the direction of each guide column is parallel to the axial direction of the gear column, and the length of each guide column is not less than the distance between the first sun gear and the fifth sun gear;
at least two positioning holes are symmetrically formed in the inner surface of the inner fluted disc, and the first ends of the guide posts are fixed in the positioning holes.
Preferably, a rolling bearing is fixedly arranged at the center of each of the first to fifth follow-up gears, the first to fifth follow-up gears are sleeved on the guide post through the rolling bearing, the rolling bearing and the guide post are axially movable, so that each follow-up gear is engaged between the corresponding sun gear and the inner gear ring, the sun gear, the follow-up gears and the grading gears axially move synchronously, the outer ends of the grading gears are enabled to be on the same circumferential surface, and the outer ends are selectively engaged with the inner side walls of the corresponding planet gears.
Preferably, the center of the second end of the shell is penetrated and provided with a second through hole, the first through hole is aligned with the second through hole, the second through hole extends outwards to form a section of first hollow column, the second end of the gear column is penetrated through the second through hole and extends into the first hollow column, the inner diameter of the first hollow column is larger than the outer diameter of the limiting ring body, a guide bearing is fixedly installed in the first hollow column, the guide bearing is slidably sleeved on the gear column body between the first sun gear and the limiting ring body, and the distance between the first sun gear and the limiting ring body is not smaller than the distance between the first sun gear and the fifth sun gear.
Preferably, set up a sliding tray at least on the first hollow post lateral wall, the direction of sliding tray with the axial of first hollow post is unanimous, the length of sliding tray is not less than interval between first sun gear and the fifth sun gear, the spaced apart a plurality of locking grooves that are equipped with between sliding tray end to the end tail, the direction of locking groove with the direction of sliding tray is perpendicular, adjacent two distance between the locking groove is unanimous with adjacent two distance between the sun gear, every another end extension locking breach of locking groove.
Preferably, the first hollow column is slidably sleeved with a position adjuster, the position adjuster comprises a second hollow column, the center of the second hollow column is divided into a first cavity and a second cavity which are communicated, the inner diameter of the first cavity is smaller than the inner diameter of the second cavity, the outer diameter of the second hollow column is larger than the outer diameter of the first hollow column, the inner diameter of the first cavity is between the inner diameter and the outer diameter of the limiting ring body, the inner diameter of the second cavity is larger than the outer diameter of the limiting ring body, a hollow ring body is arranged in the side wall of the second hollow column, the axial distance of the hollow ring body is not smaller than the distance between the first sun gear and the fifth sun gear, and the hollow ring body is movably sleeved on the first hollow column; the outer side wall of the bottom of the hollow ring body is convexly provided with a guide block, the guide block is slidably arranged in the sliding groove or each locking groove, an annular ball disc is arranged at the joint of the first cavity and the second cavity, the outer diameter of the annular ball disc is arranged between the inner diameter of the first cavity and the inner diameter of the second cavity, the inner diameter of the annular ball disc is arranged between the inner diameter and the outer diameter of the limiting ring body, and the annular ball disc is in rolling press fit on the limiting ring body.
The invention at least comprises the following beneficial effects:
1. the speed reducer can greatly improve the speed reduction ratio;
2. the reduction gear is provided with a plurality of continuously adjustable reduction ratios, can be conveniently adjusted according to actual requirements, and simultaneously effectively improves the reliability of the accuracy of the reduction ratios, thereby expanding the application range of the reduction gear.
Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention.
Drawings
FIG. 1 is a schematic view of the overall construction of a reducer;
FIG. 2 is a schematic view of an installation structure of an inner fluted disc and an end cover;
FIG. 3 is a schematic view of an installation structure of an inner fluted disc and a planet wheel;
FIG. 4 is a schematic structural view of a gear column;
FIG. 5 is a side view of the gear column;
FIG. 6 is a side view of the mounting structure of the guide post;
FIG. 7 is a side view of the mounting structure of the follower gear and the sun gear;
FIG. 8 is a sectional view of the mounting structure of the follower gear and the sun gear;
FIG. 9 is a sectional view of the mounting structure of the stepped gear, the follower gear and the sun gear;
FIG. 10 is a top view of the mounting structure for the follower gear;
FIG. 11 is a top view of the mounting structure for the stepped gear, the follower gear and the sun gear;
FIG. 12 is a schematic structural view of an end cap;
FIG. 13 is a bottom structure view of the internal gear plate;
FIG. 14 is a schematic view of the mounting structure of the output shaft;
FIG. 15 is a schematic structural view of a first hollow column;
FIG. 16 is a schematic view of the overall structure of the positioner;
FIG. 17 is a cross-sectional view of the positioner;
FIG. 18 is a schematic view of the bottom structure of the decelerator;
fig. 19 is a cross-sectional view of the planet gears engaging the first stepped gear;
fig. 20 is a cross-sectional view of the planetary gear in mesh with a fifth stage gear.
Detailed Description
The present invention is further described in detail below with reference to the attached drawings so that those skilled in the art can implement the invention by referring to the description text.
It will be understood that terms such as "having," "including," and "comprising," as used herein, do not preclude the presence or addition of one or more other elements or groups thereof.
As shown in fig. 1 to 18, the present invention provides a gear reducer with an accurate and reliable reduction ratio, which includes a housing 110, and an inner toothed disc 130 and a reduction gear assembly rotatably disposed in the housing 110, wherein a plurality of planet gears 160 are disposed in the inner toothed disc 130.
Specifically, a plurality of first bearings 141 are symmetrically installed on the inner surface of the inner toothed disc 130, the first bearings 141 are close to the tooth surface of the inner toothed disc 130, in this embodiment, five first bearings 141 are provided, a planet gear 160 is rotatably installed on the first bearings 141, a second bearing 142 is rotatably installed on the other end shaft of the planet gear 160, a positioning cavity 111 for accommodating and fixing the second bearing 142 is correspondingly and convexly provided at the other end of the housing 110, the second bearing 142 is fixedly installed in the positioning cavity 111, the positions of the first bearings 141 and the second bearings 142 are fixed, and the planet gear 160 is rotatably disposed between the first bearings 141 and the second bearings 142.
The outer side wall of the planet gear 160 is meshed with the inner side wall of the inner toothed disc 130, a gear column 170 is axially arranged at the center of the inner toothed disc 130, a sun gear set is arranged on a column from the axial center of the gear column 170 to the first end 176 of the gear column, the sun gear set comprises a first sun gear 171 to a fifth sun gear 175 which are continuously and concentrically arranged, the first to fifth sun gears 175 and the gear column 170 synchronously rotate, the diameter of each sun gear gradually decreases towards the first end 176 of the gear column 170, that is, the diameters of the first to fifth sun gears 175 sequentially decrease, so that the outer side end of each sun gear is distributed in a step shape which gradually shrinks towards the first end 176 of the gear column on the axis.
At least two follow-up wheel sets are symmetrically arranged on the periphery of the sun wheel set, the radial positions of the follow-up wheel sets are fixed on the inner fluted disc, and the follow-up wheel sets move along with the gear column 170 in a synchronous axial mode. Specifically, the follower gear set includes first to fifth follower gears 275 concentrically arranged at intervals, so that the first to fifth follower gears 275 can rotate independently, the diameter of each of the follower gears gradually increases toward the bottom of the inner toothed disc 130, that is, the diameter of the first to fifth follower gears gradually increases, the outer ends of each of the follower gears are distributed in a step shape gradually increasing toward the first end 176 of the gear column 170 on the axis, and the step corresponds to the step of the sun gear set.
The first to fifth sun gears 175 are in one-to-one correspondence with axial positions of the first to fifth follower gears 275, the first to fifth sun gears 175 are engaged with side walls of the first to fifth follower gears 275, as shown in the figure, the first follower gear 271 is engaged with the first sun gear 171, the second follower gear 272 is engaged with the second sun gear 172, the third follower gear 273 is engaged with the third sun gear 173, the fourth follower gear 274 is engaged with the fourth sun gear 174, and the fifth follower gear 275 is engaged with the fifth sun gear 175, and when the driving gear column 170 rotates, the corresponding follower gears are driven to rotate by the sun gears.
Hierarchical gear train cover is established follow-up wheelset's periphery, just hierarchical gear train follows gear post 170 synchronous axial displacement, in this embodiment, correspond hierarchical gear train includes the first to fifth gear 375 that set up in succession with one heart, and each hierarchical gear independently rotates simultaneously, a hollow portion is seted up with one heart to the inside of hierarchical gear for hierarchical gear is two-sided gear ring structure, each hierarchical gear's external diameter is unanimous, and the internal diameter orientation the bottom direction crescent of internal tooth dish 130, exactly first to fifth gear 375's internal diameter crescent, each hierarchical gear's medial extremity be on the axis to gear post 170 second end step distribution that shrinks gradually, this step corresponds with follow-up wheelset's step.
Inner gear rings are arranged on the inner side walls of the stepped gears, the first to fifth stepped gears 375 are in one-to-one correspondence with the axial positions of the first to fifth follow-up gears 275, the inner side walls of the first to fifth stepped gears 375 are meshed with the outer side walls of the first to fifth follow-up gears 275, namely the inner gear rings are meshed and sleeved on the peripheries of the corresponding follow-up gears, as shown in the figure, the first follow-up gear 271 is meshed with the inner gear ring of the first stepped gear 371, the second follow-up gear 272 is meshed with the inner gear ring of the second stepped gear 372, the third follow-up gear 273 is meshed with the inner gear ring of the third stepped gear 373, the fourth follow-up gear 274 is meshed with the inner gear ring of the fourth stepped gear 374, and the fifth follow-up gear 275 is meshed with the inner gear ring of the fifth stepped gear 375, and when the driving gear column 170 rotates, the corresponding stepped gears can be driven by the sun gear and the follow-up gears.
Every be provided with the outer ring gear on the hierarchical gear lateral wall, the outer ring gear of first to fifth grading gear 375 and the inside wall axial selective meshing of planet wheel, namely can select one of them hierarchical gear and each planet wheel 160 meshing through axial displacement gear post 170, when drive gear post 170 rotates, drive the planet wheel through one of them sun gear and its corresponding follower gear and hierarchical gear and rotate, can drive inner fluted disc 130 and rotate, and because the diameter of each sun gear is different, so when planet wheel 160 and different hierarchical gear meshing linkage, the reduction gear can output different reduction ratios, in order to reach the effect of variable reduction ratio.
Specifically, a guide groove 179 is formed in a cylinder at the second end of the gear column 170, the guide groove 179 is formed in a cylinder close to the first sun gear 171, a circular sliding ring 730 is rotatably disposed in the guide groove 179, and the circular sliding ring 730 is restricted from rotating in the guide groove 179, so that the circular sliding ring 730 and the gear column 170 can rotate independently, but the circular sliding ring 730 moves axially along with the gear column 170.
The periphery of the circular sliding ring 730 is at least symmetrically extended with two connecting rods 700, the direction of the connecting rod 700 is perpendicular to the axial direction of the gear column 170, the other end of the connecting rod 700 is provided with a guide sleeve 720, a guide column 710 is movably arranged in the guide sleeve 720, and the guide sleeve 720 is used for providing a guiding effect for the relative movement of the guide column 710, so that the gear column 170 and the guide sleeve 720 axially move along the guide column 710. The direction of the guide post 710 is parallel to the axial direction of the gear post 170, and the length of the guide post 710 is not less than the distance between the first to fifth sun gears, so as to provide enough distance for the axial movement of the gear post 170, and each stepped gear can contact with the planetary gear in the axial direction.
Two positioning holes 131 are symmetrically formed in the inner surface of the inner toothed disc 130 in the inner space of the first bearing 141, the distance between the two positioning holes 131 is the same as the radial distance between the two guide columns 710, and the first ends of the guide columns 710 are fixed in the positioning holes 131, so that the circular sliding ring 730 and the inner toothed disc 130 do not rotate relatively, and the gear column 170 and the inner toothed disc 130 rotate relatively.
First to fifth follower gear 275 center fixed be provided with a antifriction bearing, specifically, every follower gear center has seted up the cavity, the cavity internal fixation is provided with a antifriction bearing, first to fifth follower gear pass through the antifriction bearing cover is established on the guide post 710, interval connection between two adjacent antifriction bearings for each antifriction bearing independently rotates on the guide post 710, and has guaranteed the synchronous axial displacement of each antifriction bearing.
The rolling bearings and the guide columns 710 are axially movable, so that the following gears are engaged between the corresponding sun gears and the inner gear rings, the sun gears, the following gears and the grading gears axially move synchronously, the outer ends of the grading gears are on the same circumferential surface and are selectively engaged with the inner side walls of the corresponding planet gears, namely the planet gears 160 are linked with the sun gears with different diameters through the following gears and the grading gears at corresponding positions, and the outermost ends of the grading gears are on the same circumferential surface, so that when the gear columns 170 axially move, the grading gears are smoothly switched and engaged with the planet gears 160.
The gear column 170 is disposed at the center of the inner gear plate 130, and after the gear column 170 is mounted in place, along with the axial movement of the gear column 170, the outer side wall of each stepped gear is selectively engaged with the outer side wall of the corresponding planet gear 160, so that the inner gear plate 130 is linked with sun gears of different diameters on the gear column 170 to adjust the reduction ratio.
The thicknesses of the sun wheel and the grading gears are consistent and not smaller than the thickness of the planet wheels 160, so that enough contact space is provided for meshing and linkage of the planet wheels 160 and the grading gears, and the planet wheels 160 are prevented from being simultaneously contacted with two grading gears in the grading gear set.
The thickness of each sun gear is not less than that of the follower gear, the structure of the gear column is shown in fig. 4, but in order to enable the sun gear, the follower gear and the step gear to move axially synchronously, a first concave cavity 1711 is formed on the outer side wall of each sun gear, as shown in fig. 5-6, the height of the first concave cavity 1711 is consistent with the thickness of the follower gear, the outer side wall of the follower gear is installed in the first concave cavity 1711 and is meshed with the side wall in the first concave cavity 1711, so that the follower gear is limited in the first concave cavity 1711, the positioning installation of the follower gear and the sun gear is completed, and when the sun gear moves axially, the follower gear can be driven to move axially synchronously. The first to fifth sun gears are in one-to-one correspondence with the axial positions of the first to fifth follow-up gears, and the first to fifth sun gears are meshed with the first to fifth follow-up gears at the corresponding positions.
Similarly, a second concave cavity is formed in the side wall of each inner gear ring of the grading gear, and the outer side wall of the follow-up gear is installed in the second concave cavity; the height of the second cavity is consistent with the thickness of the follow-up gear, the outer side wall of the follow-up gear is installed in the second cavity and meshed with the side wall in the second cavity, so that the follow-up gear is limited in the second cavity, positioning and installation of the follow-up gear and the grading gear are completed, and when the sun gear moves axially, the follow-up gear and the grading gear can be synchronously driven to move axially.
The first to fifth step gears 375 are in one-to-one correspondence with the axial positions of the first to fifth follower gears, and the ring gears of the first to fifth step gears 375 are meshed with the first to fifth follower gears at the corresponding positions. The outer side walls of the first to fifth step gears 375 are selectively meshed with the planet wheels at the corresponding positions.
A first positioning groove is formed at a first end 176 of the gear column 170, a second positioning groove 150 is formed in the center of the inner surface of the inner toothed disc 130, the first positioning groove and the second positioning groove 150 are oppositely arranged, and a spring is clamped between the first positioning groove and the second positioning groove 150, that is, the spring is installed and positioned between the two oppositely arranged positioning grooves. When the spring is in a normal state, the first positioning groove and the second positioning groove 150 are spaced at a certain distance, at this time, the fifth sun gear 175, the fifth follower gear 275 and the fifth stepped gear 375 thereof are engaged with the planet gear 160, and the gear column 170 and the inner fluted disc 130 are linked after being decelerated by the engaged fifth sun gear 175 and the planet gear 160.
When the gear column 170 is pushed to move towards the bottom of the inner toothed disc 130, the fourth sun gear, the fourth follower gear and the fourth stepped gear thereof move towards the planet gears 160 until the fourth sun gear and the fourth follower gear are meshed with each other, the fifth stepped gear 375 is separated from the planet gears 160, and the gear column 170 and the inner toothed disc 130 are in linkage after being decelerated through the meshed fourth sun gear and the meshed planet gears 160.
When the gear column 170 is continuously pushed to move towards the bottom of the internal gear disc 130, the gear column 170 and the internal gear disc 130 are in linkage after being decelerated through the meshed third sun gear and planet gears 160; by analogy, the last gear column 170 and the inner gear plate 130 are in linkage after being decelerated through the meshed first sun gear 171 and the planet gear 160; in the process, the spring is compressed and, when the sun gear set is reset, the fifth sun gear 175 remains in engagement with the planet gears 160 under the action of the spring. Therefore, the gear column 170 and the inner gear 130 have five continuous linkage modes, and the diameters of the first to fifth sun gears 175 are different, so five different reduction ratios can be obtained, and the number of sun gears in the sun gear set can be adjusted according to actual conditions, so as to adjust the configuration number of the reduction ratios.
A first shaft connecting seat 177 is arranged at the end of the second end of the gear column 170, the first shaft connecting seat 177 is used as the input shaft end of the speed reducer, and a limiting ring body 178 is convexly arranged on the column body between the first shaft connecting seat 177 and the first sun gear 171; a second axle connecting seat 113 is seted up at inner fluted disc 130 outside center, and second axle connecting seat 113 rotates with inner fluted disc 130 synchronous, be provided with an output shaft 410 in the second axle connecting seat 113, this output shaft 410 rotates with inner fluted disc 130 synchronous as the output of reduction gear, output shaft 410 is to the extension of casing 110 outside, drives external equipment through output shaft 410.
Or a linkage sun gear 420 may be integrally disposed at the extending end of the output connecting body shaft 410, and the external device is conveniently driven by the linkage sun gear 420.
The first end of the casing 110 is set to be an open structure, the opening direction of the casing 110 is opposite to the opening direction of the inner toothed disc 130, the opening of the casing 110 is closed by an end cover 120, the height in the casing 110 is not less than the height of the sun gear set so as to provide an axial movement space of the sun gear set, the inner toothed disc 130 is located in an accommodating space formed by the end cover 120 and the casing 110, a first through hole 121 is formed in the center of the end cover 120, the bottom of the inner toothed disc 130 is rotatably installed on the upper surface of the end cover 120, the first through hole 121 is aligned with the second shaft connecting seat 113, and the linkage sun gear 420 penetrates through the first through hole 121 and extends outwards for a certain distance.
Specifically, a first circular guide rail groove is seted up at end cover 120 upper surface center, first circular guide rail groove is located first through-hole 121 periphery, first circular guide rail inslot is provided with an annular rolling disc 122, annular rolling disc 122 protrusion in end cover 120 upper surface certain distance, a second circular guide rail groove 112 is seted up to internal tooth dish 130 lower surface center correspondence, second circular guide rail groove 112 is located the 113 periphery of second shaft connecting seat, second circular guide rail groove 112 is installed on annular rolling disc 122, internal tooth dish 130 bottom is passed through annular rolling disc 122 rotates and sets up end cover 120 upper surface.
Specifically, the thickness of the housing 110 is not less than the distance between the fifth sun gear 175 and the first positioning groove, so that the sun gear set and the column of the gear column 170 at the lower end thereof can move in the housing 110.
In this embodiment, the first end of the housing 110, the end cap 120, and the inner gear plate 130 are sequentially connected to form an integral structure through a screw, a second through hole is formed through the center of the second end of the housing 110, the first through hole 121 is aligned with the second through hole, a section of the first hollow column 180 extends outward from the second through hole, the second end of the gear column 170 extends through the second through hole and extends into the first hollow column 180, and the first shaft connecting seat 177 is exposed to the outside to facilitate input connection of the speed reducer.
The inner diameter of the first hollow column 180 is larger than the outer diameter of the limiting ring body 178, so that the limiting ring body 178 can extend into the first hollow column 180, a guide bearing (not shown in the figure) is fixedly mounted in the first hollow column 180, the outer side wall of the guide bearing is fixed with the inner side wall of the first hollow column 180, the guide bearing is slidably sleeved on the gear column 170 between the circular sliding ring 730 and the limiting ring body 178, so that the guide bearing can only move relatively between the circular sliding ring 730 and the limiting ring body 178, and the distance between the circular sliding ring 730 and the limiting ring body 178 is not smaller than the distance between the first sun gear 171 and the fifth sun gear 175, so that the planetary gear 160 can be respectively contacted with the first to fifth sun gears 175. Meanwhile, the guide bearing also plays a role in axial guiding, and strictly limits the gear column 170 to axial movement.
At least one sliding groove 181 is formed in the outer side wall of the first hollow column 180, the direction of the sliding groove 181 is the same as the axial direction of the first hollow column 180, and the length of the sliding groove 181 is not smaller than the distance between the first sun gear 171 and the fifth sun gear 175, so that the planet gears 160 can be in contact with the first sun gear 175, the second sun gear 175 and the fifth sun gear 175 respectively. First locking groove 182 to fifth locking groove 184 are seted up to the interval between sliding tray 181 end to the end tail, first locking groove 182 to fifth locking groove 184 the direction with the direction of sliding tray 181 is perpendicular, adjacent two distance between the locking groove is unanimous with adjacent two distance between the sun gear, every another end of locking groove extends a locking breach, as shown in the figure, another end of first locking groove 182 is provided with locking breach 183, and another end of fifth locking groove 184 is provided with locking breach 185.
The first hollow column 180 is slidably sleeved with a position adjuster 300, the position adjuster 300 comprises a second hollow column, the center of the second hollow column is divided into a first cavity 320 and a second cavity 350 which are communicated, the inner diameter of the first cavity 320 is smaller than the inner diameter of the second cavity 350, the outer diameter of the second hollow column is larger than the outer diameter of the first hollow column 180, the inner diameter of the first cavity 320 is between the inner diameter and the outer diameter of the limiting ring body 178, the inner diameter of the second cavity 350 is larger than the outer diameter of the limiting ring body 173, a hollow ring body 310 is arranged in the side wall of the second hollow column, the axial distance of the hollow ring body 310 is not smaller than the distance between the first sun wheel 171 and the fifth sun wheel 175, and the hollow ring body 310 is movably sleeved on the side wall of the first hollow column 180; a guide block 330 is convexly arranged on the outer side wall of the bottom of the hollow ring body 310, and the guide block 330 is limited to be slidably arranged in the sliding groove 181 or each locking groove, so that the position adjuster 300 is movably arranged on the first hollow column 180.
An annular ball disc 340 is arranged at the joint of the first cavity 320 and the second cavity 350, the outer diameter of the annular ball disc 340 is between the inner diameter and the inner diameter of the first cavity 320 and the second cavity 350, the inner diameter of the annular ball disc 340 is between the inner diameter and the outer diameter of the limiting ring body 178, when the position adjuster 300 is sleeved on the first hollow column 180, the annular ball disc 340 is rolled and pressed on the limiting ring body 178 to push the position adjuster 300 to push the gear column 170, and the first shaft connecting seat 177 is exposed outside from the first cavity 320.
The working process is as follows:
an input end shaft of the external device is connected to the first shaft connection base 177, and is decelerated by the decelerator and then output by the output connecting shaft 410 or the linkage sun gear 420. In a normal state, the positioner 300 is rotated to move the guide block 330 into the sliding groove 181, and the spring pushes the gear column 170 to move toward the top of the inner toothed disc 130, so that the fifth-stage gear 375 is engaged with the planetary gears 160, as shown in fig. 20, and the gear column 170 and the inner toothed disc 130 are linked after being decelerated by the engaged fifth sun gear 175 and the engaged planetary gears 160.
When the reduction ratio of the speed reducer needs to be reduced, the position adjuster 300 is pressed, the limiting ring body 178 and the whole gear column 170 move towards the bottom of the inner toothed disc 130 through the annular ball disc 340, the position adjuster 300 moves on the outer side wall of the first hollow column 180 along the sliding groove 181 until the guide block 330 moves to the position where the sliding groove 181 corresponds to the first locking groove 182, in the process, the spring is continuously compressed, the fourth sun gear, the fourth follower gear and the fourth stepped gear thereof move towards the planet gears 160 until the planet gears 160 are meshed with each other, the fifth stepped gear 375 is separated from the planet gears 160, and the gear column 170 and the inner toothed disc 130 are in linkage after being reduced in speed through the meshed fourth sun gear and the planet gears 160. The positioner 300 is then rotated so that the guide block 330 moves into the first locking slot 182 until the guide block 330 is trapped in the locking notch 183, the guide block 330 being locked under the pressure of the spring and the axial position of the gear column 170 being fixed.
When the reduction ratio of the speed reducer needs to be reduced continuously, the positioner 300 is rotated, so that the guide block 330 is disengaged from the locking notch 183 and moves into the sliding groove 181, and the gear column 170 is pushed to move towards the bottom of the inner toothed disc 130 continuously, in the process, the spring is further compressed, the third sun gear, the third follower gear and the third stepped gear move towards the planet gears 160 until the third sun gear, the third follower gear and the third stepped gear are meshed with the planet gears 160, the fourth stepped gear is separated from the planet gears 160, and the gear column 170 and the inner toothed disc 130 are linked after being reduced in speed through the meshed third sun gear and the planet gears 160. The positioner 300 is then rotated so that the guide block 330 moves into the second locking slot until the guide block 330 is trapped in the locking notch on the second locking slot, the guide block 330 being locked under the pressure of the spring and the axial position of the gear column 170 being fixed.
When it is necessary to continue to reduce the reduction ratio of the speed reducer, the adjustment process is analogized, and finally the gear column 170 and the inner toothed disc 130 are linked after being reduced by the engaged first sun gear 171 and the planet gears 160, as shown in fig. 19.
When the spring needs to be reset, the positioner 300 is pressed to enable the guide block 330 to be separated from the locking notch 185, and then the positioner 300 is rotated to enable the guide block 330 to move into the sliding groove 181. When the sun set is reset, the fifth sun gear 175 remains in communication with the planet gears 160 under the influence of the spring.
Therefore, the speed reducer can greatly improve the speed reduction ratio; meanwhile, the speed reducer is provided with multiple continuously adjustable speed reducing ratios, can be conveniently adjusted according to actual requirements, and meanwhile, the reliability of the precision of the speed reducing ratios is effectively improved, so that the application range of the speed reducer is expanded.
While embodiments of the invention have been described above, it is not limited to the applications set forth in the description and the embodiments, which are fully applicable in various fields of endeavor to which the invention pertains, and further modifications may readily be made by those skilled in the art, it being understood that the invention is not limited to the details shown and described herein without departing from the general concept defined by the appended claims and their equivalents.
Claims (10)
1. A gear reducer having an accurate and reliable reduction ratio, comprising:
the first end of the shell is provided with an open structure, and the opening of the shell is closed by an end cover;
the inner fluted disc is rotatably arranged in an accommodating space formed by the end cover and the shell, and the opening direction of the shell is opposite to that of the inner fluted disc;
the planet gears are arranged in the inner fluted disc at intervals, the axial directions of the planet gears are parallel to the axial direction of the inner fluted disc, and the outer side walls of the planet gears are meshed with the inner side walls of the inner fluted disc;
the gear column is axially arranged at the center of the inner fluted disc, a sun wheel set is arranged on a column body between the center of the gear column and the first end of the gear column, the sun wheel set comprises a plurality of sun wheels which are continuously and concentrically arranged, the diameter of each sun wheel is gradually reduced towards the direction of the first end of the gear column, and the outer side end of each sun wheel is distributed in a step shape which is gradually contracted towards the first end of the gear column on the axis; a first shaft connecting seat is arranged at the end of the second end of the gear column, and a limiting ring body is convexly arranged on a column body between the first shaft connecting seat and the sun gear set; a second shaft connecting seat is formed in the center of the outer side of the inner fluted disc, and an output connecting shaft is arranged in the second shaft connecting seat;
the follow-up wheel sets are symmetrically arranged on the periphery of the sun wheel set, the radial positions of the follow-up wheel sets are fixed on the inner fluted disc, the follow-up wheel sets synchronously and axially move along with the gear column, each follow-up wheel set comprises a plurality of follow-up gears concentrically arranged at intervals, the diameter of each follow-up gear gradually increases towards the bottom direction of the inner fluted disc, and the outer side ends of the follow-up gears are distributed in a step shape gradually increasing towards the first end of the gear column on the axis; and
the grading gear set is sleeved on the periphery of the follow-up gear set and synchronously and axially moves along with the gear column, the grading gear set comprises a plurality of grading gears which are continuously and concentrically arranged, a hollow part is concentrically arranged in each grading gear, the outer diameters of the grading gears are consistent, the inner diameters of the grading gears are gradually increased towards the bottom direction of the inner fluted disc, and the inner side ends of the grading gears are distributed in a step shape which gradually shrinks towards the second end of the gear column on the axis;
an inner gear ring is arranged on the inner side wall of each grading gear, the innermost end of the follow-up gear is meshed with the outermost side wall corresponding to the sun gear, the outermost end of the follow-up gear is meshed with the inner gear ring corresponding to the grading gears, and the outermost side wall of each grading gear is axially and selectively meshed with the innermost side wall of the planet gear.
2. A gear reducer with accurate and reliable reduction ratio according to claim 1, characterized in that said sun gear group comprises first to fifth sun gears rotating in synchronism with said gear post, said first to fifth sun gears decreasing in diameter in sequence; the follow-up wheel set comprises a first follow-up gear, a second follow-up gear, a third follow-up gear, a fourth follow-up gear and a fourth follow-up gear, wherein the first follow-up gear, the second follow-up gear and the third follow-up gear rotate independently, and the diameters of the first follow-up gear, the second follow-up gear and the fourth follow-up gear are gradually increased; the hierarchical gear train includes first hierarchical gear to fifth hierarchical gear, first to fifth hierarchical gear independently rotate, the internal diameter of first to fifth hierarchical gear is crescent.
3. A gear reducer with accurate and reliable reduction ratio according to claim 2, wherein the thickness of each sun gear is not less than the thickness of the follower gear, a first concave cavity is formed on the outer side wall of the sun gear, and the outer side wall of the follower gear is installed in the first concave cavity; the axial positions of the first to fifth sun gears and the first to fifth follow-up gears are in one-to-one correspondence, and the first to fifth sun gears are meshed with the first to fifth follow-up gears at the corresponding positions;
the thickness of each grading gear is consistent with that of the sun gear and is not less than that of the planet gear; a second concave cavity is formed in the side wall of the inner gear ring of the grading gear, and the outer side wall of the follow-up gear is installed in the second concave cavity; the first to fifth step gears are in one-to-one correspondence with the axial positions of the first to fifth follow-up gears, and the inner gear rings of the first to fifth step gears are meshed with the first to fifth follow-up gears at the corresponding positions;
the outer side walls of the first to fifth step gears are selectively meshed with the planet gears at corresponding positions.
4. The gear reducer of claim 2 in which the first end of the housing and the end cap are connected in series by a threaded rod to form a unitary structure, the end cap having a first through hole in the center thereof, the output shaft extending outwardly through the first through hole for a predetermined distance.
5. The gear reducer of claim 2, wherein the first end of the gear column has a first positioning groove, the inner surface of the inner gear has a second positioning groove, the first positioning groove and the second positioning groove are opposite, a spring is sandwiched between the first positioning groove and the second positioning groove, the first positioning groove and the second positioning groove are spaced apart by a predetermined distance when the spring is in a normal state, and the fifth-stage gear is engaged with the planetary gears.
6. The gear reducer with precise and reliable reduction ratio according to claim 5, wherein the thickness of the housing is not less than the distance between the first sun gear and the first positioning groove, the cylinder at the second end of the gear column is provided with a guide groove, the guide groove is rotatably provided with a circular slip ring, the periphery of the circular slip ring is symmetrically extended with at least two connecting rods, the direction of the connecting rods is perpendicular to the axial direction of the gear column, the other end of the connecting rods is provided with a guide sleeve, the guide sleeve is movably provided with a guide post, the direction of the guide post is parallel to the axial direction of the gear column, and the length of the guide post is not less than the distance between the first to fifth sun gears;
at least two positioning holes are symmetrically formed in the inner surface of the inner fluted disc, and the first ends of the guide posts are fixed in the positioning holes.
7. The gear reducer of claim 6, wherein a rolling bearing is fixedly disposed at the center of each of the first to fifth follower gears, the first to fifth follower gears are sleeved on the guide post through the rolling bearing, the rolling bearing and the guide post are axially movable, so that each follower gear is engaged between the corresponding sun gear and the inner gear ring, the sun gear, the follower gears and the step gears axially move synchronously, and the outer ends of the step gears are on the same circumferential surface and selectively engaged with the inner side walls of the corresponding planet gears.
8. The gear reducer of claim 4, wherein a second through hole is formed through a center of a second end of the housing, the first through hole is aligned with the second through hole, the second through hole extends outward to form a first hollow column, a second end of the gear column extends through the second through hole and extends into the first hollow column, an inner diameter of the first hollow column is larger than an outer diameter of the limiting ring body, a guide bearing is fixedly mounted in the first hollow column, the guide bearing is slidably sleeved on the gear column body between the first sun gear and the limiting ring body, and a distance between the first sun gear and the limiting ring body is not smaller than a distance between the first sun gear and the fifth sun gear.
9. The gear reducer with precise and reliable reduction ratio according to claim 8, characterized in that at least one sliding groove is formed on the outer side wall of the first hollow column, the direction of the sliding groove is consistent with the axial direction of the first hollow column, the length of the sliding groove is not less than the distance between the first sun gear and the fifth sun gear, a plurality of locking grooves are arranged between the end head and the end tail of the sliding groove at intervals, the direction of the locking grooves is perpendicular to the direction of the sliding groove, the distance between two adjacent locking grooves is consistent with the distance between two adjacent sun gears, and the other end of each locking groove extends to form a locking notch.
10. The gear reducer with precise and reliable reduction ratio according to claim 9, wherein the first hollow column is slidably sleeved with a position adjuster, the position adjuster comprises a second hollow column, the center of the second hollow column is divided into a first cavity and a second cavity which are communicated, the inner diameter of the first cavity is smaller than the inner diameter of the second cavity, the outer diameter of the second hollow column is larger than the outer diameter of the first hollow column, the inner diameter of the first cavity is between the inner diameter and the outer diameter of the limiting ring body, the inner diameter of the second cavity is larger than the outer diameter of the limiting ring body, a hollow ring body is arranged in the side wall of the second hollow column, the axial distance of the hollow ring body is not smaller than the distance between the first sun gear and the fifth sun gear, and the hollow ring body is movably sleeved on the first hollow column; the outer side wall of the bottom of the hollow ring body is convexly provided with a guide block, the guide block is slidably arranged in the sliding groove or each locking groove, an annular ball disc is arranged at the joint of the first cavity and the second cavity, the outer diameter of the annular ball disc is arranged between the inner diameter of the first cavity and the inner diameter of the second cavity, the inner diameter of the annular ball disc is arranged between the inner diameter and the outer diameter of the limiting ring body, and the annular ball disc is in rolling press fit on the limiting ring body.
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| CN201811088978.2A CN109083985B (en) | 2018-09-18 | 2018-09-18 | Gear reducer with accurate and reliable reduction ratio |
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| CN201811088978.2A CN109083985B (en) | 2018-09-18 | 2018-09-18 | Gear reducer with accurate and reliable reduction ratio |
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| CN109083985B true CN109083985B (en) | 2021-08-03 |
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| CN111371243B (en) * | 2020-04-07 | 2021-02-12 | 江苏川钿明椿电气机械有限公司 | Stable output aluminum wire motor of speed reduction motor |
| CN111555198B (en) * | 2020-06-05 | 2021-04-06 | 南京工程学院 | High-altitude cable on-line peeling machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| IT1083061B (en) * | 1977-05-19 | 1985-05-21 | Sasso Luigi | TRANSMISSION TO MULTIPLE REPORTS, PARTICULARLY BY ORDERS |
| JPS63101545A (en) * | 1986-10-15 | 1988-05-06 | Matsushita Electric Works Ltd | Planetary speed change gear |
| PL349209A1 (en) * | 2001-08-20 | 2003-02-24 | Slawomir Pawelec | Clutch integrated with a multiple-speed permanent-intermesh transmission gear |
| KR20040062213A (en) * | 2002-12-31 | 2004-07-07 | 남석봉 | Auto transmission |
| CN2842085Y (en) * | 2005-05-30 | 2006-11-29 | 蔡贵席 | Wolf teeth sliding drive multiple speed transmission |
| KR20080088700A (en) * | 2007-03-30 | 2008-10-06 | 경종만 | Automobile transmission |
| DE112010002613T5 (en) * | 2009-05-19 | 2013-07-04 | Kyung-Yul Hyun | Multi-stage automatic transmission |
| CN105570397B (en) * | 2016-01-08 | 2017-12-15 | 任孝忠 | Full ratchet-gear wheel stepless speed change device |
| CN108458060B (en) * | 2018-02-28 | 2023-11-10 | 广西洪钢新能源科技有限公司 | Novel automatic electromagnetic stepless speed changer for automobile |
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