CN1051603C - Speed varying mechanism and its processing method - Google Patents
Speed varying mechanism and its processing method Download PDFInfo
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- CN1051603C CN1051603C CN95110613A CN95110613A CN1051603C CN 1051603 C CN1051603 C CN 1051603C CN 95110613 A CN95110613 A CN 95110613A CN 95110613 A CN95110613 A CN 95110613A CN 1051603 C CN1051603 C CN 1051603C
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- gear
- eccentric
- shaft
- high speed
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Abstract
The present invention relates to a speed changing mechanism and a processing method thereof, which belongs to a transmission device. The present invention is a new gear design on the basis of the existing gear speed changing mechanism, namely that a basic eccentric circular gear is used in the present invention, and the profile of the basic eccentric circular gear is formed according to the motion trajectory of a point on tangential central lines of the basic eccentric gear and an engaged gear when the basic eccentric gear and the engaged gear rotate in a certain transmission ratio. Compared with involute gear transmission, modules of the present invention is 3 to 5 times of those of an involute gear under the conditions of the same central distance and transmission ratio, the bending resistant performance and the bearing capacity of the present invention is 5 to 12 times larger than those of an involute gear under the condition of the same processing material, the comprehensive bearing capacity of the present invention can also be increased by 1.3 to 2.5 times by taking contact intensity into account, and the present invention has the advantages of small slip ratio and good processing manufacturability.
Description
The present invention relates to a kind of transmission device, particularly relate to a kind of gear shift and processing method that contains the element that is meshing with each other except that involute tooth or cycloid tooth.
In the current transmission device that generally uses, belt transmission is arranged, chain transmission, hydraulic transmission and gear transmission or the like.What its gear-driven gear usually adopted is involute tooth or cycloid tooth, and these gear teeth often occur in transmission process most common failures such as tooth fractures, damage, repairs very difficultly, and it is good to process these gear requirement materials, the technological level height.In transmission, the sliding ratio of involute gear changes between 0～∞, generally can only be controlled between the 1.5-8 in the practice, and worm geared sliding ratio is then up to 2-10.The single staged transmission ratio of involute gear is generally below 6.3, though the velocity ratio single-stage of worm screw can reach 50, its sliding ratio is big, and efficient is very low.The SU-652-394 patent that on March 15th, 1979 announced discloses a kind of eccentric swing pinion transmission, but it is a kind of interior engagement Gear Planet Transmission of eccentric rotation, and its transmission efficiency is low, and sliding ratio is big.
The purpose of this invention is to provide a kind of gear shift, make its in concentricity distance, with the velocity ratio condition under with other forms of gear mechanism relatively, the number of teeth of steamboat is minimum can accomplish 1, its number of teeth and can accomplish minimum, and modulus can be accomplished maximum, and sliding ratio is little, can improve bearing capacity, can reduce frictional loss again, improve mechanical efficiency, and a kind of manufacture method of gear shift is provided.
In order to realize the foregoing invention purpose, the technical solution that adopts is to carry out new gear teeth design on the basis of existing gear shift, be that transmission is held wheel and adopted basic eccentric gear, the flank profil of the driving and driven gear of this kind all is to form by the movement locus that perseverance when being engaged the gear number of teeth and being meshing with each other transmission as velocity ratio is tangential on the point on the two-wheeled center line with being engaged gear according to basic eccentric wheel, and the envelope curver polar equation of its flank profil is ρ=R+r+e-ecos θ ± e
2Cosn θ+r
2-e
2Following formula is ρ=R when θ=0 °, when θ=π/n, ρ=R+2e with this basic eccentric wheel as reciprocal feed according to the intermeshing novel parallel shaftgear of a pair of large and small gear gear that processes.Minimum each 2 of the sheet number of its gear mesh can require and can choose in 2～24 according to different stationarity, between each sheet of every pair of gear all according to sheet number and the number of teeth different each interlacedly open a different α angle.The value at its α angle is
The large and small gear of the number of teeth in the formula has nothing in common with each other, and the sheet number is identical, so the α angle difference of large and small gear.The gearwheel number of teeth can be more than or equal to 2, and small gear number of teeth minimum can accomplish 1.Its single staged transmission ratio in principle can be unrestricted during the open type transmission, and single staged transmission ratio is equal to or less than 10 during the enclosed transmission.
The flank profil of driving and driven gear described in the such scheme all be according to basic eccentric wheel be engaged gear and form by the movement locus that perseverance when being engaged the gear number of teeth and being meshing with each other transmission as velocity ratio is tangential on the point on the two-wheeled center line, owing to introduced a basic eccentric wheel, so we are for the time being with the basic eccentric gear of this kind gear called after.
The basic principle of this programme and the track of gear tooth profile, as shown in Figure 1, promptly basic eccentric wheel (wheel B) is stated as follows with the intermeshing principle of basic eccentric gear (wheel A):
The Root radius of wheel A is R, and the center is O
a, the number of teeth is n, and its tip circle radius is R+2e, and the radius of wheel B is r, and throw of eccentric is e, its center of rotation is O
bWhen taking turns B around O
bDuring rotation, its center of circle is around with O
bBeing the center, is that the circumference of radius periodically changes with e, and existing to require the rotating ratio as wheel A and wheel B be 1: during n, two-wheeled is crossing forever and be tangential on O
a, O
bOn line on, promptly when two-wheeled by direction as shown with 1: during the ratio transmissions of n, A turns over θ when wheel
1, wheel B must turn over n θ
1(illustrated ∠ B
oO
dB
l); A turns over θ when wheel
2, wheel B must turn over n θ
2, the rest may be inferred by analogy.A shown in the figure
0B
0, A
1B
1, A
2B
2, A
3B
3, A
dB
dDeng each point all is to retouch out by this movement locus.In order to make two-wheeled by 1: its arc length that was equates substantially to reduce slip during the n ratio transmissions, general desirable R=nr, when being meshing with each other with basic eccentric gear in the eccentric wheel of this ratio manufacturing, its maximum sliding ratio can be less than 1.3, the minimum average B configuration sliding ratio that this value promptly can be accomplished less than involute gear, more be significantly smaller than the sliding ratio of cylindrical worm, thereby can obtain transmission efficiency preferably, (above-mentioned n is integer) (it is more suitable to get e=r/4～r/6) designs rational processing scheme by above rule can process the basic eccentric gear flank profil of any number of teeth more than 2 teeth accurately, and the envelope curver polar equation of its flank profil is ρ=R+r+
Following formula is ρ=R when θ=0 °, when θ=π/n, ρ=R+2e, can directly mesh with basic eccentric wheel with the basic eccentric gear that same basic eccentric circle and throw of eccentric process by this rule, basic eccentric gear that again can the various different numbers of teeth is meshing with each other, to obtain different velocity ratios.
Because this basic eccentric gear flank profil is to make according to basic eccentric wheel tangent with it track when the transmission, and the instantaneous radius of gyration at eccentric wheel its point of contact when rotating is by cycle alternately change between r+e and r-e, it is cumulative to r+e from r-e that 1/2 circle is wherein arranged, 1/2 circle is pursued by r+e and reduces to r-e in addition, when wheel B active, have only when the instantaneous radius of gyration is cumulative, just to promote to take turns the A rotation, have only more than two pairs can produce continuous transmission for this reason by the overlapping installation of certain intersecting angle.
The processing method of its basic eccentric gear can be divided into three kinds.
Method 1: cut into the gear sheet again after adopting integral body to process flank profil, assembling method is overlapping.
(1) stay the mill amount accurately to process cylindrical with a long bar by circle size outside the finished product;
(2) angle [alpha] and the position degree requirement by the assembling that is overlapping processes auxiliary hole, and its hole count is according to the gear sheet number of packages decision of overlapping assembling, and promptly hole count equals assembling gear sheet number of packages, and processes endoporus simultaneously;
Formed to-and-fro motion drives in rotating when (3) rotating by gear ratio with basic eccentric circle wheel hobboing cutter or emery wheel process gear tooth profile with periodic to-and-fro motion, the precision of its flank profil must meet the requirements fully, can root circle during check and the size tolerance requirements of top circle as test basis;
(4) gear sheet thickness in accordance with regulations cuts off, and end face polishes, and guarantees the perpendicularity of end face and endoporus;
(5) each part is all got one of them positioning hole and common endoporus as the positioning hole that is overlapping and installs, and adjacent two α angles of staggering process the keyway that each part communicates after the accurate positioning check is errorless again, axle is put into.
(6) on high speed shaft, adorn basic eccentric gear, correspondence is adorned basic eccentric gear on lower velocity shaft with it, between basic eccentric gear and adjacent basic eccentric gear, clamp packing ring, and the α angle of staggering between the gear, between eccentric gear and adjacent eccentric gear, clamp packing ring, to adorn install to body on parallel of high speed shaft of eccentricity gear again with lower velocity shaft, the upper end dress flowing cover of high speed shaft, lower end dress end cap, but dress go side, the lower end of lower velocity shaft lid, upper end dress end cap, the eccentric shaft bearing sleeve is all loaded onto at end cap two at high speed shaft, between bearing and gear, adorn spacer, between bearing on the lower velocity shaft and gear, adorn spacer, adorn gear shift cover on the body.
Method 2: whole processing all-in-one-piece way.
Promptly get the material that adheres to specification, process cylindrical, endoporus, keyway earlier, width by every tooth processes middle interval trough again, determine the starting point of a feed then, process the flank profil on the left side, again cutter is moved to a slice tooth on the right by the method for method 1 processing flank profil, and will process starting point and rotate the α angle and process the right a slice flank profil, this moment, two profiles of tooth were identical, but staggered α angle, then the rest may be inferred more than three in processing.
Method 3: adopt drawing, assembling method is overlapping.
Earlier make punch die, use the drawing of punch die burst by flank profil, again by method 1 processing technology hole, keyway etc., after the staggered earlier gear piece processing flank profil, interlocking, each gear piece is overlapping to be assembled again.
Owing to adopted above technical solution, realized the object of the invention preferably.The gear that adopts basic sheet heart Knucle-gear to be meshed and to constitute, compare with Involutes Gears Transmission, in centre distance, under the identical condition of velocity ratio, its modulus can be accomplished involute gear 3～5 times, therefore under rapidoprint condition of the same race, its bending bearing capacity can be big 5～12 times, if consider that the raising of contact strength is less, its comprehensive load capacity also can be big 1.3～2.5 times.The single staged transmission ratio of this gear is generally optional between 1-50 or in the bigger scope, and the velocity ratio bigger as needs can multistagely be contacted, and has overcome the suitable little unsuitable big or suitable greatly unsuitable little defective of existing other driving mechanism.The flank of tooth sliding ratio of this mechanism is very little, can be controlled between 0～1.3,, improve mechanical efficiency and increase the service life so help reducing friction, wearing and tearing, its single-stage driving efficient can be stabilized in more than 0.98, and its transmission efficiency can not reduce with the increase of velocity ratio.Because this transmission does not have axial force, then do not need to adopt thrust-bearing again.But also it is good to have a technology capability, with characteristics such as material are less demanding.
Description of drawings:
Fig. 1 is that the basic eccentric gear theory of engagement and flank profil track form schematic representation.
Fig. 2 is the assembling schematic representation (B-B among Fig. 3 cuts open) that basic eccentric gear engagement constitutes gear.
Fig. 3 be Fig. 2 overlook (A-A cuts open) schematic representation.
Fig. 4 is 3 pairs of basic eccentric gear mesh schematic representations (B-B among Fig. 5 analyses and observe).
Fig. 5 is the A-A sectional view of Fig. 4.
Fig. 6 is basic eccentric gear (greatly) schematic representation (3 auxiliary holes and corresponding 3 keyways are positions of expression 3 plate gears among the figure).
Fig. 7 is the E-E section among Fig. 6.
Fig. 8 is the eccentric wheel schematic representation.
Fig. 9 is the sectional view of Fig. 8.
Figure 10 is basic eccentric gear (little) schematic representation.
Figure 11 is the sectional view of Figure 10.
Figure 12 is the cross-sectional schematic of eccentric shaft bearing sleeve.
Figure 13 is the left view of Figure 12.
Figure 14 is the structural representation of the whole processing of basic eccentric gear.
Figure 15 is the sectional view of Figure 14.
Embodiment 1:
Accompanying drawing has been described one embodiment of the present of invention, processes 3 pairs of basic eccentric gears according to the principle design of Fig. 1, is made into gear as shown in Figure 2 then.Promptly this gear 2 (this example is 2 teeth, can be monodentate or multiple tooth) is adorned basic eccentric gear 3 (this routine number of teeth is 6, and α is 30 °) on the corresponding with it lower velocity shaft, the former steamboat, and the latter is a bull wheel, present embodiment is got 3 pairs of engaging gears.Between steamboat and steamboat, clamp packing ring 9, clamp packing ring 13 between bull wheel and the bull wheel.The upper end of high speed shaft (input end) but dress go side lid 6, lower end dress end cap 10; The lower end of lower velocity shaft (output shaft) but dress go side lid 15, upper end dress end cap 11; But all load onto eccentric shaft bearing sleeve 7 at lid two, the go side of high speed shaft, be used to adjust two-wheeled centre distance, dress spacer 8 between axle sleeve and the gear; Dress spacer 14 between bearing on the lower velocity shaft and the gear; Add gear shift cover 1 on the body, promptly become gear of the present invention.
Its basic eccentric gear is made by aforesaid method 1, cuts into the gear sheet again after promptly adopting integral body to process flank profil, and the method that is assembled that is overlapping is made.
Embodiment 2:
Press 5 pairs of basic eccentric gears of principle design processing of Fig. 1, then by structure fabrication gear shown in Figure 2.The basic eccentric gear of present embodiment adopts whole processing all-in-one-piece method to make, and method 2 is described as the aforementioned.The present embodiment small gear number of teeth adopts 2 teeth, and the gearwheel number of teeth adopts 9 teeth.
Embodiment 3:
Press 12 pairs of basic eccentric gears of principle design processing of Fig. 1, then by structure fabrication gear shown in Figure 2, its basic eccentric gear adopts drawing, the assembling that is overlapping, and method 3 is described as described above.
Claims (5)
1, a kind of gear shift is made up of body, case lid, lower velocity shaft parallel to each other and high speed shaft etc., it is characterized in that driving gear has adopted basic eccentric gear, and the envelope curver polar equation of flank profil is ρ=R+r+e-ecos θ ± e
2Cosn θ+r
2-e
2R is basic eccentric gear Root radius in the following formula, and r is the number of teeth for eccentric substantially radius, n, and e is a throw of eccentric, when θ=0 °, ρ=R is when θ=π/n, ρ=R+2e, the sheet number of its engaging gear 2-24 between, every pair of interleaved α angle of gear.The value of its α is:
During as the enclosed transmission, its single staged transmission ratio is equal to or less than 10.
2,, it is characterized in that gearwheel number in the driving gear is more than or equal to 2 by the described a kind of gear shift of claim 1.
3,, it is characterized in that small gear number in the driving gear is more than or equal to 1 by the described a kind of gear shift of claim 1.
4, the manufacture method of the described gear of a kind of claim 1, comprise the routine processing of parts such as body, case lid, high speed shaft and lower velocity shaft, the processing method that it is characterized in that basic eccentric gear is to cut into the gear sheet again after adopting integral body to process flank profil, becomes wrong overlapping assembling, that is:
(1) stay the mill amount accurately to process cylindrical with a long bar by circle size outside the finished product;
(2) angle [alpha] and the position degree requirement by the assembling that is overlapping processes auxiliary hole, and its hole count equals overlapping assembling gear sheet number of packages, and processes endoporus simultaneously;
Formed to-and-fro motion drives in rotating when (3) rotating by gear ratio with basic eccentric circle wheel hobboing cutter or emery wheel process flank profil with periodic to-and-fro motion;
(4) gear sheet thickness in accordance with regulations cuts off, and end face polishes, and guarantees the perpendicularity of end face and endoporus;
(5) each part is all got one of them positioning hole and common endoporus as the positioning hole that is overlapping and installs, and adjacent two α angles of staggering after accurate positioning is errorless, process the keyway that each part communicates again.
(6) on high speed shaft [5], adorn basic eccentric gear [2], the corresponding with it basic eccentric gear [3] of on lower velocity shaft [12], adorning, between basic eccentric gear [2] and adjacent basic eccentric gear [2], clamp packing ring [9], and the α angle of staggering between the gear, between eccentric gear [3] and adjacent eccentric gear [3], clamp packing ring [13], to adorn install to body [4] on parallel of high speed shaft [5] of eccentricity gear again with lower velocity shaft [12], the upper end dress flowing cover [6] of high speed shaft, lower end dress end cap [10], but the lower end of lower velocity shaft dress go side lid [15], upper end dress end cap [11], all load onto eccentric shaft bearing sleeve [7] at end cap two of high speed shaft, between bearing and gear, adorn spacer [8], between bearing on the lower velocity shaft and gear, adorn spacer [14], adorn gear shift cover [1] on the body.
5, manufacture method by the described gear shift of claim 1, comprise body, case lid, the routine processing of parts such as high speed shaft and lower velocity shaft, the processing method that it is characterized in that basic eccentric gear is first selection material processing excircles, endoporus, keyway, width by every tooth processes middle interval trough again, determine the starting point of a feed then, process a flank profil on the left side earlier, again cutter is moved to a slice tooth on the right, and will process starting point and rotate the α angle, process the flank profil of the right a slice, process the 3rd according to this, 4,5 etc., the master that will process then, driven gear is respectively charged into high speed shaft and lower velocity shaft, install on the body [4] this high speed shaft is parallel with lower velocity shaft again, but the upper end of high speed shaft dress go side lid [6], lower end dress end cap [10], but the lower end of lower velocity shaft dress go side lid [15], upper end dress end cap [11], all load onto eccentric shaft bearing sleeve [7] at end cap two of high speed shaft, between bearing and gear, adorn spacer [8], between bearing on the lower velocity shaft and gear, adorn spacer [14], adorn gear shift cover [1] on the body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN95110613A CN1051603C (en) | 1995-01-08 | 1995-01-08 | Speed varying mechanism and its processing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN95110613A CN1051603C (en) | 1995-01-08 | 1995-01-08 | Speed varying mechanism and its processing method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1126809A CN1126809A (en) | 1996-07-17 |
| CN1051603C true CN1051603C (en) | 2000-04-19 |
Family
ID=5077980
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95110613A Expired - Fee Related CN1051603C (en) | 1995-01-08 | 1995-01-08 | Speed varying mechanism and its processing method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1051603C (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102505163A (en) * | 2011-11-10 | 2012-06-20 | 西安航空动力股份有限公司 | Split eccentric adjustment mechanism for mounting edge |
| CN112392914A (en) * | 2020-12-03 | 2021-02-23 | 福建思普计量检测科技有限公司 | Disc distributed output mechanism with multiple transmission ratios |
| CN113084265B (en) * | 2021-04-19 | 2023-03-24 | 重庆沃菲特泵业有限公司 | Gear grinding device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US652394A (en) * | 1899-11-07 | 1900-06-26 | Albert Lagus | Means for raising or lowering windows. |
| CN2122974U (en) * | 1992-04-28 | 1992-11-25 | 万中宝 | Wave-wheel diven variable-speed mechanism |
-
1995
- 1995-01-08 CN CN95110613A patent/CN1051603C/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US652394A (en) * | 1899-11-07 | 1900-06-26 | Albert Lagus | Means for raising or lowering windows. |
| CN2122974U (en) * | 1992-04-28 | 1992-11-25 | 万中宝 | Wave-wheel diven variable-speed mechanism |
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| Publication number | Publication date |
|---|---|
| CN1126809A (en) | 1996-07-17 |
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