CN113531076A - Non-circular gear speed change device and implementation method thereof - Google Patents
Non-circular gear speed change device and implementation method thereof Download PDFInfo
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- CN113531076A CN113531076A CN202110925961.3A CN202110925961A CN113531076A CN 113531076 A CN113531076 A CN 113531076A CN 202110925961 A CN202110925961 A CN 202110925961A CN 113531076 A CN113531076 A CN 113531076A
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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
- F16H35/00—Gearings or mechanisms with other special functional features
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G47/00—Article or material-handling devices associated with conveyors; Methods employing such devices
- B65G47/22—Devices influencing the relative position or the attitude of articles during transit by conveyors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G47/00—Article or material-handling devices associated with conveyors; Methods employing such devices
- B65G47/74—Feeding, transfer, or discharging devices of particular kinds or types
- B65G47/82—Rotary or reciprocating members for direct action on articles or materials, e.g. pushers, rakes, shovels
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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
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/001—Gearings with eccentric mounted gears, e.g. for cyclically varying ratio
Abstract
The invention discloses a non-circular gear speed change device and an implementation method of the speed change device, wherein the non-circular gear speed change device comprises three pairs of non-circular gears, three pairs of cylindrical gears, a shaft sleeve and a bracket, the three pairs of non-circular gears are in the same pitch curve shape and are fixedly connected with three different phases of 120 degrees, 240 degrees and 360 degrees, the three pairs of non-circular gears consist of a first non-circular gear, a second non-circular gear, a third non-circular gear, a fourth non-circular gear, a fifth non-circular gear and a sixth non-circular gear, and the three pairs of cylindrical gears consist of a first cylindrical gear, a second cylindrical gear, a third cylindrical gear, a fourth cylindrical gear, a fifth cylindrical gear and a sixth cylindrical gear; the invention has convenient use and stable transmission, can realize uniform and variable speed motion and is beneficial to improving the production efficiency; meanwhile, the transmission structure is simplified, and the problem of processing difficulty caused by designing a five-connecting-rod cam in a small-range assembly space is solved.
Description
Technical Field
The present invention relates to a non-circular gear transmission and a method for implementing the transmission.
Background
In an automatic production line of sanitary products, in order to improve production efficiency or meet station requirements, it is an important part of mechanical design to rapidly realize speed change of products according to known station requirements. The uniform speed → variable speed → the uniform speed → variable speed motion rule can be generally realized by the cam five-link mechanism in the space rotation motion, but the space position of the variable speed mechanism given by the actual automatic equipment is limited, namely the size of the cam five-link mechanism must be small, on the premise that the processing precision of a cam pressure angle and an actual contour line must be ensured, the processing cost of the variable speed gear is greatly increased, the assembly precision is higher, and one set of the cam five-link mechanism can only realize the speed change of a specification product according to the preset motion rule, so that the existing variable speed gear can not meet the requirement of the existing production, and a novel variable pitch gear is urgently needed to be developed.
Disclosure of Invention
The technical problem to be solved by the invention is to provide a non-circular gear speed changing device and a pitch changing method, which are convenient to use, stable in transmission, capable of realizing uniform speed and variable speed movement, beneficial to improving production efficiency and practical and widely applicable.
In order to solve the problems, the invention adopts the following technical scheme:
a non-circular gear speed change device comprises three pairs of non-circular gears, three pairs of cylindrical gears, shaft sleeves and supports, wherein the three pairs of non-circular gears are in the same pitch curve shape and are fixedly connected with three different phases of 120 degrees, 240 degrees and 360 degrees, the three pairs of non-circular gears comprise a non-circular gear I, a non-circular gear II, a non-circular gear III, a non-circular gear IV, a non-circular gear V and a non-circular gear VI, the three pairs of cylindrical gears comprise a cylindrical gear I, a cylindrical gear II, a cylindrical gear III, a cylindrical gear IV, a cylindrical gear V and a cylindrical gear VI, the shaft sleeves comprise a shaft sleeve I, a shaft sleeve II and a shaft sleeve III, the shaft sleeve II is arranged inside the shaft sleeve III, the shaft sleeve III is arranged inside the shaft sleeve II, the shaft sleeve II is connected with the cylindrical gear III, the shaft sleeve II is connected with the cylindrical gear I, the shaft sleeve I is connected with the cylindrical gear I, one ends of the shaft sleeve III, the shaft sleeve II and the shaft sleeve I are all provided with wind box mounting seats, and the third shaft sleeve, the second shaft sleeve and the first shaft sleeve are respectively provided with a third wind box, a second wind box and a first wind box.
Preferably, the wind box III, the wind box II and the wind box I are connected with a wind pipe connector I.
This setting is convenient for accomplish the evacuation to the powder box inside to realize the negative pressure.
Preferably, an axle sleeve fixing seat is installed on the support, the axle sleeve is fixed on the axle sleeve fixing seat, a fixing rod is arranged on one side of the axle sleeve fixing seat, and one end of the fixing rod is connected with a driving disc fixing seat.
This setting has realized fixing, installing of driving-disc and axle sleeve etc..
Preferably, the driving disc fixing seat is provided with a driving disc, a fan pipeline and a servo motor, and one end of the servo motor is connected with the driving disc.
This setting has realized the rotation of driving-disc for tuber pipe interface two rotates with minute union coupling synchronous.
Preferably, an air pipe joint II is installed on the inner side of the driving disc fixing seat, one end of the air pipe joint II is connected with a fan pipeline, and the other end of the air pipe joint II is connected with the air pipe joint I.
This setting has realized the inside negative pressure of wind box for article can not drop at the in-process of following rotation or removal.
A pitch-variable method of a non-circular gear for producing sanitary products comprises the following steps:
1) carrying out freedom degree analysis and determining the freedom degree of the speed changing device to be 1;
2) preliminarily determining the motion rule of the driven non-circular gear according to the motion rule of the wind box required to be uniform → variable → uniform → variable and the combination of the size of the outer diameter of the wind box and the space position limit condition of the actual mechanism;
3) according to the characteristics of various products with different specifications, the outer diameter of the wind box is selected, so that the non-circular gear required by each specification product is ensured to be continuously free of impact when being meshed;
4) comprehensively considering the installation positioning requirements when products of different specifications are changed, adding the constraint condition into a designed and calculated variable speed section curve, and solving a variable speed section speed function formula according to the constraint conditions of speed, acceleration, phase and installation positioning, wherein the function formula adopts a quintic polynomial function formula;
5) preliminarily drawing up a center distance, and accurately calculating the speed motion law when the non-circular gears are meshed, so that the pitch curve shape of each non-circular gear can be preliminarily obtained;
6) considering actual working requirements such as load, rotating speed and the like, calculating the meshing bending strength of the non-circular gear, selecting parameters such as the modulus, the material, the processing technology, the tooth thickness and the like of the non-circular gear, performing gear shaping on a pitch curve of the non-circular gear, reasonably adjusting the center distance according to the tooth number by selecting an integer system principle, and finally determining the size of each part;
7) considering that the mass center of the non-circular gear is not on the rotation center, the centrifugal force generated by the non-circular gear during the middle-high speed operation excites the main shaft, if the excitation frequency reaches the vicinity of the natural vibration frequency band of the main shaft, resonance occurs, and adverse effects are generated on the service life of a bearing and the strength of the main shaft, in order to eliminate the hidden trouble, the dynamic balance design calculation needs to be carried out on the non-circular gear in advance under the premise of considering the strength, so that the mass center of the non-circular gear is close to the rotation center;
8) the non-circular gears are installed and positioned in three different phases of 120 degrees, 240 degrees and 360 degrees, and finally speed change is achieved through the action of the non-circular gears.
The invention has the beneficial effects that: by adopting the combination mechanism of three pairs of non-circular gear trains and three pairs of cylindrical gear trains, the transmission structure is simplified, the problem of processing difficulty caused by designing a five-link cam in a small-range assembly space is solved, products of different specifications only need to replace the non-circular gears, and stable operation of the speed change device under the conditions of safety, economy, high efficiency and high speed can be realized.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, but the present invention is not limited to the scope of the present invention.
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic top view of the present invention;
FIG. 3 is a schematic view of the wind box installation of the present invention;
the wind power generation device comprises a first non-circular gear 1, a second non-circular gear 2, a third non-circular gear 3, a third non-circular gear 101, a fourth non-circular gear 102, a fifth non-circular gear 103, a sixth non-circular gear 103, a first cylindrical gear 4, a second cylindrical gear 5, a third cylindrical gear 6, a third cylindrical gear 104, a fourth cylindrical gear 105, a fifth cylindrical gear 106, a sixth cylindrical gear 7, an output shaft 8, a transmission shaft 9, a fixed shaft 10, a shaft sleeve fixing seat 10, a third shaft sleeve 11, a second shaft sleeve 12, a first shaft sleeve 13, a first shaft sleeve 14, a first wind pipe connector 15, a second wind pipe connector 16, a driving disc 17, a servo motor 18, a fan pipeline 19, a fixed rod 20, a bracket 21, a wind box mounting seat 22, a driving disc fixing seat 111, a third wind box 121, a second wind box 131 and a first wind box.
Detailed Description
Referring to fig. 1 to 3, a non-circular gear speed changing device includes three pairs of non-circular gears, three pairs of cylindrical gears, a shaft sleeve and a bracket 20, the three pairs of non-circular gears have the same pitch curve shape and are fixedly connected with three different phases of 120 °, 240 ° and 360 °, the three pairs of non-circular gears are composed of a non-circular gear 1, a non-circular gear 2, a non-circular gear 3, a non-circular gear four 101, a non-circular gear five 102 and a non-circular gear six 103, the non-circular gear 1, the non-circular gear two 2 and the non-circular gear three 3 are fixed on an input shaft 7, the non-circular gear 1 is engaged with the non-circular gear four 101, the non-circular gear two 2 is engaged with the non-circular gear five 102, and the non-circular gear three 3 is engaged with the non-circular gear six 103; the three pairs of cylindrical gears are fixed on the transmission shaft by a first cylindrical gear 4, a second cylindrical gear 5, a third cylindrical gear 6, a fourth cylindrical gear 104, a fifth cylindrical gear 105 and a sixth cylindrical gear 106, as well as a fourth non-circular gear 101, a fifth non-circular gear 102, a sixth non-circular gear 103, a fourth cylindrical gear 104, a fifth cylindrical gear 105 and a sixth cylindrical gear 106; the cylindrical gear I4, the cylindrical gear II 5 and the cylindrical gear III 6 are surrounded and fixed on the fixed shaft, the shaft sleeve comprises a shaft sleeve I13, a shaft sleeve II 12 and a shaft sleeve III 11, the shaft sleeve II 12 is arranged inside the shaft sleeve III 11, the shaft sleeve I13 is arranged inside the shaft sleeve II 12, the shaft sleeve III 11 is connected with the cylindrical gear III 6, the shaft sleeve II 12 is connected with the cylindrical gear II 5, the shaft sleeve I13 is connected with the cylindrical gear I4, one ends of the shaft sleeve III 11, the shaft sleeve II 12 and the shaft sleeve I13 are respectively provided with a wind box mounting seat 21, and the wind box III 111, the wind box II 121 and the wind box I131 are respectively arranged on the shaft sleeve III 11, the shaft sleeve II 12 and the wind box mounting seat 21 of the shaft sleeve I13.
Further, the first wind pipe joint 14 is connected to the third wind box 111, the second wind box 121 and the first wind box 131.
Further, install axle sleeve fixing base 10 on the support 20, the axle sleeve is fixed on axle sleeve fixing base 10, and one side of axle sleeve fixing base 10 is equipped with dead lever 19, and the one end of dead lever 19 is connected with driving-disc fixing base 22.
Further, a driving disc 16, a fan pipeline 18 and a servo motor 17 are mounted on the driving disc fixing seat 22, and one end of the servo motor 17 is connected with the driving disc 16.
Further, an air pipe joint II 15 is installed on the inner side of the driving disc fixing seat 22, one end of the air pipe joint II 15 is connected with the fan pipeline 18, and the other end of the air pipe joint II 15 is connected with the air pipe joint I14.
A method of implementing a non-circular gear change mechanism comprising the steps of:
1) carrying out freedom degree analysis and determining the freedom degree of the speed changing device to be 1;
2) preliminarily determining the motion rule of the driven non-circular gear according to the motion rule of the wind box required to be uniform → variable → uniform → variable and the combination of the size of the outer diameter of the wind box and the space position limit condition of the actual mechanism;
3) according to the characteristics of various products with different specifications, the outer diameter of the wind box is selected, so that the non-circular gear required by each specification product is ensured to be continuously free of impact when being meshed;
4) comprehensively considering the installation positioning requirements when products of different specifications are changed, adding the constraint condition into a designed and calculated variable speed section curve, and solving a variable speed section speed function formula according to the constraint conditions of speed, acceleration, phase and installation positioning, wherein the function formula adopts a quintic polynomial function formula;
5) preliminarily drawing up a center distance, and accurately calculating the speed motion law when the non-circular gears are meshed, so that the pitch curve shape of each non-circular gear can be preliminarily obtained;
6) considering actual working requirements such as load, rotating speed and the like, calculating the meshing bending strength of the non-circular gear, selecting parameters such as the modulus, the material, the processing technology, the tooth thickness and the like of the non-circular gear, performing gear shaping on a pitch curve of the non-circular gear, reasonably adjusting the center distance according to the tooth number by selecting an integer system principle, and finally determining the size of each part;
7) considering that the mass center of the non-circular gear is not on the rotation center, the centrifugal force generated by the non-circular gear during the middle-high speed operation excites the main shaft, if the excitation frequency reaches the vicinity of the natural vibration frequency band of the main shaft, resonance occurs, and adverse effects are generated on the service life of a bearing and the strength of the main shaft, in order to eliminate the hidden trouble, the dynamic balance design calculation needs to be carried out on the non-circular gear in advance under the premise of considering the strength, so that the mass center of the non-circular gear is close to the rotation center;
8) the non-circular gears are installed and positioned in three different phases of 120 degrees, 240 degrees and 360 degrees, and finally speed change is achieved through the action of the non-circular gears.
When the wind box is in operation, the first noncircular gear, the second noncircular gear and the third noncircular gear respectively drive the fourth noncircular gear, the fifth noncircular gear and the sixth noncircular gear to rotate under the influence of a transmission shaft, the fourth cylindrical gear, the fifth cylindrical gear and the sixth cylindrical gear synchronously rotate, the fourth cylindrical gear, the fifth cylindrical gear and the sixth cylindrical gear respectively drive the first cylindrical gear, the second cylindrical gear and the third cylindrical gear to rotate, and in the rotating process, the first cylindrical gear, the second cylindrical gear and the third cylindrical gear respectively drive the first shaft sleeve, the second shaft sleeve and the third shaft sleeve to rotate, so that the first wind box, the second wind box and the third wind box to rotate; meanwhile, the servo motor drives the driving disc to rotate, so that the second air pipe connector and the first air pipe connector synchronously move, negative pressure is generated inside the air box under the action of the fan pipeline in the rotating process of the air box, and articles are adsorbed on the air box under the action of the negative pressure.
In the implementation process of the invention, the design of a plurality of shaft sleeves, a plurality of cylindrical gears, a plurality of non-circular gears and a plurality of wind boxes can be provided.
When the invention is implemented, the non-circular gear I, the non-circular gear II and the non-circular gear III are divided into driving non-circular gears; dividing a non-circular gear four, a non-circular gear five and a non-circular gear six into driven non-circular gears; and setting the first cylindrical gear, the second cylindrical gear and the third cylindrical gear as driven cylindrical gears, and setting the fourth cylindrical gear, the fifth cylindrical gear and the sixth cylindrical gear as driving cylindrical gears.
In the implementation process, firstly, the output motion rule of the driven non-circular gear needs to be determined, the motion rule of the driven non-circular gear is according to the uniform speed → speed change → uniform speed → speed change motion, the speed and the uniform speed holding time of the two uniform speed sections are according to the actual requirements, the functional equation of the two speed change curve sections needs to be solved, and the positioning requirement needs to be considered when the non-circular gears corresponding to products with different specifications are conveniently replaced, and the positioning requirement is converted into a mathematical model meaning, namely when the driving non-circular gear combination rotates at the uniform speed by 120 degrees, the driven non-circular gear combination needs to rotate by the same angle.
If the function of the speed change curve is a fifth order polynomial, the function has six unknowns, 1) the positioning requirement is given a constraint condition for solving the equation; 2) in order to ensure that the gear motion is continuous and has no impact, two constraint conditions that the speeds at two ends of a curve are required to be consistent with the constant speed are added, 3) two constraint conditions that the acceleration at two ends of the curve is 0 are added, 4) one constraint condition that the integral of the whole segmented angular velocity curve to time is equal to 360 degrees is added, so that 6 equations are obtained, the quintic polynomial function can be obtained according to a linear equation system solving method, the speed and the rotating angle of the non-circular gear at any moment are obtained, and a center distance is determined initially; the meshing of the non-circular gear pair can be equivalent to the meshing of a plurality of cylindrical gear pairs with different transmission ratios, the pitch curve size of the two gears at any moment can be obtained, the rotating angle at any moment is added, the data coordinate point of the non-circular gear at any moment can be obtained, the data coordinate point is collected and counted in a table, and the pitch curve shapes of the two gears can be obtained by fitting the coordinate point.
One driving non-circular gear rotates 120 degrees more than the other driving non-circular gear, at the moment, the driven non-circular gear rotates more than the driven non-circular gear by degrees clearly obtained from the table, namely the installation phase angle of the driven non-circular gear relative to the driven non-circular gear, the installation phase angle of the driven non-circular gear relative to the driven non-circular gear can be obtained by the same method, so far, the installation phase angles of the three pairs of non-circular gears are determined, the driving cylindrical gears are respectively fixedly connected with the driven non-circular gears, the driving cylindrical gears are respectively meshed with the driven cylindrical gears, the driven cylindrical gears are respectively fixedly connected with the shaft sleeves, the shafts are installed in a shaft sleeve shaft mode, meanwhile, the three wind box mechanisms are fixedly connected with the shaft sleeve respectively, so that the rotating speeds of the three wind boxes and the three driven non-circular gears can be kept consistent, and the interference phenomenon cannot occur in the movement process. At the other end, the servo motor drives the driving disc to rotate at a constant speed, the driving disc keeps the same with the rotating speed of the transmission shaft, the fan pipeline is the same as the third pipeline connector II on the driving disc, the third pipeline connector II is connected with the first pipeline connector through a hose, so that negative pressure can be generated on the wind box, and the product is guaranteed to be firmly adsorbed on the wind box in the rotating process.
Furthermore, three pairs of non-circular gears are adopted to drive to realize the variable-speed motion of the wind box, the non-circular gear meshing is equivalent to the meshing of a plurality of straight cylindrical gears with different transmission ratios, and it is of course to be noted that under the condition of medium-high speed operation, the meshing transmission ratio of the non-circular gears is close to 1 as much as possible, if the transmission ratio is too large, namely the speed difference of the two non-circular gears is too large, the phenomenon of undercut of the non-circular gears is easily caused, so that the bending strength of the gear teeth is reduced, which is extremely unsafe under the condition of medium-high speed operation, and in the process of designing the contour line curve of the non-circular gears, when one uniform speed interval is transited to the other uniform speed interval, the transition interval is ensured to be as large as possible, and the head and the tail of the transition curve of the transition interval are ensured to have continuous speed and acceleration, so that no impact phenomenon is ensured.
Further, as described above, in the medium-high speed situation, the speed change range is not too large when two non-circular gears are designed, the design curve ensures that the two non-circular gears are in convex engagement, and one non-circular gear does not simultaneously have convex and concave surfaces, which is very disadvantageous in the bending strength of the gear teeth during the machining or the engagement. And meanwhile, parameters such as the modulus, the tooth thickness, the meshing contact ratio, the non-circular gear material, the heat treatment process (required strength and toughness), the backlash and the like of the three pairs of non-circular gears are comprehensively considered according to the actual load condition, so that the three pairs of non-circular gears can be ensured to stably, high-speed and safely operate.
Further, as the mass center of the noncircular gear deviates from the rotation center, the excitation of centrifugal force to the main shaft in the rotating process of the three pairs of noncircular gears under lower frequency easily causes the mechanism to resonate, so that the service life of the bearing is greatly reduced, and the mechanism is very easy to damage under the resonant working condition, therefore, the dynamic balance design needs to be carried out under the condition of ensuring the meshing bending strength of the noncircular gears, so that the mass center and the rotation center are coincided, and the resonance probability can be greatly reduced by the dynamic balance design.
The above is only a specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that are not thought of through the inventive work should be included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope defined by the claims.
Claims (6)
1. A non-circular gear change device characterized by: the wind box comprises three pairs of non-circular gears, three pairs of cylindrical gears, a shaft sleeve and a support, wherein the three pairs of non-circular gears are same in pitch curve shape and are fixedly connected with three different phases of 120 degrees, 240 degrees and 360 degrees, the three pairs of non-circular gears comprise a first non-circular gear, a second non-circular gear, a third non-circular gear, a fourth non-circular gear, a fifth non-circular gear and a sixth non-circular gear, the three pairs of cylindrical gears comprise a first cylindrical gear, a second cylindrical gear, a fourth cylindrical gear, a fifth cylindrical gear and a sixth cylindrical gear, the shaft sleeve comprises a first shaft sleeve, a second shaft sleeve and a third shaft sleeve, the second shaft sleeve is arranged inside the third shaft sleeve, the first shaft sleeve is arranged inside the second shaft sleeve, the third shaft sleeve is connected with the third cylindrical gear, the second shaft sleeve is connected with the first cylindrical gear, one end of the third shaft sleeve, one shaft second shaft and one shaft sleeve are respectively provided with a wind box mounting seat, and the third shaft sleeve, the wind box mounting seats are respectively mounted on the third shaft sleeve, the second shaft sleeve and the wind box mounting seats, A second wind box and a first wind box.
2. A non-circular gear change device as claimed in claim 1, wherein: and the wind box III, the wind box II and the wind box I are connected with a wind pipe connector I.
3. A non-circular gear change device as claimed in claim 2, wherein: install the axle sleeve fixing base on the support, the axle sleeve is fixed on the axle sleeve fixing base, and one side of axle sleeve fixing base is equipped with the dead lever, and the one end of dead lever is connected with driving-disc fixing base.
4. A non-circular gear change device as claimed in claim 3, wherein: the driving disc fixing seat is provided with a driving disc, a fan pipeline and a servo motor, and one end of the servo motor is connected with the driving disc.
5. A non-circular gear change device as claimed in claim 4, wherein: and a second air pipe joint is arranged on the inner side of the driving disc fixing seat, one end of the second air pipe joint is connected with a fan pipeline, and the other end of the second air pipe joint is connected with the first air pipe joint.
6. A method of implementing a non-circular gear transmission, characterized by: the method comprises the following steps:
1) carrying out freedom degree analysis and determining the freedom degree of the speed changing device to be 1;
2) preliminarily determining the motion rule of the driven non-circular gear according to the motion rule of the wind box required to be uniform → variable → uniform → variable and the combination of the size of the outer diameter of the wind box and the space position limit condition of the actual mechanism;
3) according to the characteristics of various products with different specifications, the outer diameter of the wind box is selected, so that the non-circular gear required by each specification product is ensured to be continuously free of impact when being meshed;
4) comprehensively considering the installation positioning requirements when products of different specifications are changed, adding the constraint condition into a designed and calculated variable speed section curve, and solving a variable speed section speed function formula according to the constraint conditions of speed, acceleration, phase and installation positioning, wherein the function formula adopts a quintic polynomial function formula;
5) preliminarily drawing up a center distance, and accurately calculating the speed motion law when the non-circular gears are meshed, so that the pitch curve shape of each non-circular gear can be preliminarily obtained;
6) considering actual working requirements such as load, rotating speed and the like, calculating the meshing bending strength of the non-circular gear, selecting parameters such as the modulus, the material, the processing technology, the tooth thickness and the like of the non-circular gear, performing gear shaping on a pitch curve of the non-circular gear, reasonably adjusting the center distance according to the tooth number by selecting an integer system principle, and finally determining the size of each part;
7) considering that the mass center of the non-circular gear is not on the rotation center, the centrifugal force generated by the non-circular gear during the middle-high speed operation excites the main shaft, if the excitation frequency reaches the vicinity of the natural vibration frequency band of the main shaft, resonance occurs, and adverse effects are generated on the service life of a bearing and the strength of the main shaft, in order to eliminate the hidden trouble, the dynamic balance design calculation needs to be carried out on the non-circular gear in advance under the premise of considering the strength, so that the mass center of the non-circular gear is close to the rotation center;
8) the non-circular gears are installed and positioned in three different phases of 120 degrees, 240 degrees and 360 degrees, and finally speed change is achieved through the action of the non-circular gears.
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Application publication date: 20211022 |