CN104121338A - Switching reciprocating incomplete non-circular gear speed changing box and transmitting mechanism thereof - Google Patents
Switching reciprocating incomplete non-circular gear speed changing box and transmitting mechanism thereof Download PDFInfo
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- CN104121338A CN104121338A CN201410093553.6A CN201410093553A CN104121338A CN 104121338 A CN104121338 A CN 104121338A CN 201410093553 A CN201410093553 A CN 201410093553A CN 104121338 A CN104121338 A CN 104121338A
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- 230000007246 mechanism Effects 0.000 title claims abstract description 42
- 230000005540 biological transmission Effects 0.000 claims description 100
- 238000005086 pumping Methods 0.000 claims description 51
- 230000008859 change Effects 0.000 claims description 36
- 230000008878 coupling Effects 0.000 claims description 14
- 238000010168 coupling process Methods 0.000 claims description 14
- 238000005859 coupling reaction Methods 0.000 claims description 14
- 238000009434 installation Methods 0.000 claims description 7
- 238000000034 method Methods 0.000 description 12
- 239000003921 oil Substances 0.000 description 9
- 238000005553 drilling Methods 0.000 description 5
- 238000005065 mining Methods 0.000 description 5
- 238000012545 processing Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 239000003208 petroleum Substances 0.000 description 4
- 238000010587 phase diagram Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 241000208125 Nicotiana Species 0.000 description 1
- 235000002637 Nicotiana tabacum Nutrition 0.000 description 1
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- 239000010779 crude oil Substances 0.000 description 1
- 230000002498 deadly effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000005530 etching Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 239000003129 oil well Substances 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 238000007639 printing Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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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
- F16H27/00—Step-by-step mechanisms without freewheel members, e.g. Geneva drives
- F16H27/04—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement
- F16H27/08—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement with driving toothed gears with interrupted toothing
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/42—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/084—Non-circular rigid toothed member, e.g. elliptic 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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- E—FIXED CONSTRUCTIONS
- E21—EARTH OR ROCK DRILLING; MINING
- E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
- E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
- E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
- E21B43/121—Lifting well fluids
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
- F16H2003/008—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths comprising means for selectively driving countershafts
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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
- F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
Abstract
A switching reciprocating non-circular gear speed changing box is formed by a driving switching incomplete non-circular gear (5), a first driven switching incomplete non-circular gear (4), a first driven switching incomplete non-circular gear (6), a cylinder gear system, a box body and a box cover. The switching reciprocating non-circular gear speed changing box is a power transmitting device. According to the power transmitting device, when an input shaft rotates continuously, an output shaft can clockwise and anticlockwise switch the rotation direction in a reciprocating mode at the changeable speed. The driving switching incomplete non-circular gear (5) comprises two deformed switching teeth, and the driven switching incomplete non-circular gears (4 and 6) comprise two deformed switching tooth grooves respectively. The section curve of the driving switching incomplete non-circular gear (5) and the section curves of the driven switching incomplete non-circular gears (4 and 6) can present various technical characteristics according to different main machine loads and movement requirements. The switching reciprocating incomplete non-circular gear speed changing box and a transmitting device of the switching reciprocating incomplete non-circular gear speed changing box can output speed-change motion with the rotation direction switched in a reciprocating mode through one single shaft or multiple shafts and can replace some mechanical or electric reversing mechanism.
Description
Technical field
The present invention relates to a kind of reciprocal imperfect non-circular gear transmission and driving mechanism thereof of switching, it is for needing the motion of input shaft continuous rotation and output shaft back and forth to switch continuously all kinds of mechanical mechanisms of sense of rotation.The invention belongs to machinery field, can be applicable to reciprocating reversing and the driving mechanism of light industry and machinery industry or petroleum drilling and mining industry machinery.
Background technique
Many machinery all need the action of reciprocation cycle rotation, and some machinery also needs the output of multiaxis multiposition back and forth to switch the mechanism of sense of rotation, as the tobacco machine of light industry, beverage machine, and package packing machine, grain and oil machinery, printing machinery etc.At present, some heavy industry machinery are also in the urgent need to Zhe Lei mechanism, if the vertical oil-pumping machine of petroleum drilling and mining industry is exactly one of them typical case.The mechanical mechanism of traditional reciprocal switching sense of rotation, comparatively complicated, the structural type that life and reliability is good is few.We are analyzed as a classical case using the vertical oil-pumping machine of petroleum drilling and mining industry below.
As everyone knows, as the beam pumping unit of oil drilling and extracting equipment main force equipment, can adapt to the round-the-clock severe working environment in field and famous with special, it is simple in structure simultaneously, few easy workout part, solid durable, reliability is strong, easy and simple to handle, easy to maintenance, the advantage that maintenance expenses is low, makes its dominate in oil production equipment always.
Along with the continuous increase of well depth and output, while is along with the continuous appearance of oil mining complex situations, as operating modes such as high viscosity, many wax, rocky, many gas, water logging and deep-etchings, many problems of traditional beam pumping unit are obviously displayed, the energy consumption that is mainly beam pumping unit is high, weight is large, be difficult to realize long stroke, low jig frequency oil pumping, in oil pumping is produced, the accident of sucker rod increases, oil pumping pump delivery reduction etc.In order to overcome these shortcomings, domestic and international many producers have successively developed front beam-pumping unit, phased crank pumping unit, air balance pumping unit etc., although overcome some shortcomings of conventional beam-pumping unit, still do not departed from traditional beam pumping unit and utilize quadratic crank mechanism to be converted into the kind of drive of linear reciprocating motion by rotatablely moving.The motion of this quadratic crank mechanism and mechanical characteristic make it in energy-saving analysis, endure to the fullest extent and denounce, especially the energy consumption issues that low load with strong power and accessory torque are large is constantly challenged by people's scientific practice, and therefore all kinds of novel energy-conservings also constantly come out without beam pumping unit.
After eighties of last century eighties, each oil production equipment manufacturer has researched and developed New-generation efficient energy-saving type pumping unit in succession, correct most of problem of above-mentioned type, various without beam pumping unit in succession start to produce and drop into oil recovery building site use, be exactly Typical Representative wherein without the vertical oil-pumping machine of walking beam.Its advantage is to have cancelled beam pumping unit to use quadratic crank mechanism will rotatablely move and be converted into straight-line power consumption transmission link.The characteristics of motion of vertical oil-pumping machine is to use a kind of wide cut belt or chain to do clockwise under the driving guiding of cylinder and roller or sprocket wheel, back and forth switch counterclockwise rotatablely moving of rotation direction, thereby drive sucker rod and oil well pump that underground crude oil is drawn on ground, the vertical oil-pumping machine of different size has different strokes and jig frequency, during the commutation of vertical oil-pumping machine up-down stroke, just there is the variable motion of short time, 90% length of stroke is uniform motion straight up and down, thereby dynamic load is less, exchange weight is little, it is 1/3rd to 1/2nd of beam pumping unit.Compact structure, floor space is little, is particularly suitable for doing long stroke pumping unit, strengthens stroke and completes by the method that increases stand height.Vertical oil-pumping machine is easily realized long stroke, and the jig frequency of long stroke pumping unit is lower, greatly reduces the acceleration of moving system, and inertial load is little, and inertial load significantly declines, and pumping unit performance is greatly improved.But this vertical oil-pumping machine also has its deadly defect: the changement rate of fault of first vertical chain pumping unit is higher, fragile, it two is that the motor commutation frequency variator cost of vertical belt pumping unit is high, and is difficult to competent round-the-clock severe working environment.So, be difficult to so far substitute on a large scale beam pumping unit.
Find a kind of changement of machinery, make vertical oil-pumping machine both possess the beam pumping unit reliability and durability advantage that commutates, can reduce manufacture cost again, adapt to the severe environmental conditions of all weather operations simultaneously.So, short, the insecure weakness of vertical oil-pumping machine commutation component life just can obtain sound change, thereby makes this vertical oil-pumping machine with obvious technical advantage more adapt to operating conditions and the environment of various complexity.
Summary of the invention
1. one kind switches reciprocal imperfect non-circular gear transmission, comprise input shaft 1 and be positioned at and initiatively switch imperfect noncircular gear 5 on this input shaft 1, the first transmission shaft 2 and be positioned at the imperfect noncircular gear 4 of the first driven switching and the first cylindrical gears 8 on this first transmission shaft 2, second driving shaft 3 and be positioned at the imperfect noncircular gear 6 of the second driven switching and the second cylindrical gears 7 on this second driving shaft 3, casing 11 and case lid 12, the imperfect noncircular gear 4 of described the first driven switching, the imperfect noncircular gear 6 of the second driven switching is positioned at described initiatively the switch both sides of imperfect noncircular gear 5 and engagement installation side by side, the imperfect noncircular gear 4 of the first driven switching, it is from slowly to soon that the rotational speed of the imperfect noncircular gear 6 of the second driven switching changes, at the uniform velocity quick, from near slowly, arrive again and switch rotation direction, when input shaft 1 and be located thereon initiatively switch imperfect noncircular gear 5 according to every rotating 360 degrees clockwise or counterclockwise time, the first transmission shaft 2 and second driving shaft 3 whiles are according to counterclockwise, clockwise or clockwise, the each rotation of counterclockwise order once,
It is characterized in that:
Initiatively switching imperfect noncircular gear 5 turns clockwise and starts and enter when intermeshing with the parts of tooth that has of the imperfect noncircular gear 6 of the second driven switching, the second cylindrical gears 7 that the imperfect noncircular gear 6 of the second driven switching is connected with coaxial power starts to be rotated counterclockwise, the first cylindrical gears 8 engaging with the second cylindrical gears 7 and the imperfect noncircular gear 4 of the first driven switching being connected with the coaxial power of the first cylindrical gears 8 turn clockwise, engage with the imperfect noncircular gear 6 of the second driven switching and turned clockwise 180 while spending when initiatively switching imperfect noncircular gear 5, second driving shaft 3 and the imperfect noncircular gear 6 of the second driven switching and 7 of the second cylindrical gearss that are located thereon have been rotated counterclockwise once, the first transmission shaft 2 and the imperfect noncircular gear 4 of the first driven switching being located thereon, the first 8 of cylindrical gearss have turned clockwise once,
Continue to turn clockwise and start and enter when intermeshing with the parts of tooth that has of the imperfect noncircular gear 4 of the first driven switching when initiatively switching imperfect noncircular gear 5, the first cylindrical gears 8 that the imperfect noncircular gear 4 of the first driven switching is connected with coaxial power is all rotated counterclockwise, the second cylindrical gears 7 engaging with the first cylindrical gears 8 and the imperfect noncircular gear 6 of the second driven switching being connected with the coaxial power of the second cylindrical gears 7 turn clockwise, engage with the imperfect noncircular gear 4 of the first driven switching and continue clockwise to have rotated 180 while spending when initiatively switching imperfect noncircular gear 5, second driving shaft 3 and the imperfect noncircular gear 6 of the second driven switching and the second cylindrical gears 7 that are located thereon have turned clockwise once, the first transmission shaft 2 and the imperfect noncircular gear 4 of the first driven switching being located thereon, the first 8 of cylindrical gearss have been rotated counterclockwise once.
2. the reciprocal imperfect non-circular gear transmission of switching according to claim 1, it is characterized in that, it also has output shaft 10 and is positioned at the output shaft cylindrical gears 9 on this output shaft 10, described output shaft cylindrical gears 9 engages with described the first cylindrical gears 8 or with the second cylindrical gears 7, or adopts 2 groups of output shafts 10 and the output shaft cylindrical gears 9 that is located thereon engages with the first cylindrical gears 8 and the second cylindrical gears 7 simultaneously.
3. the reciprocal imperfect non-circular gear transmission of switching according to claim 1, is characterized in that:
At the uniform velocity district that speed-change area that the described pitch curve 28 that initiatively switches imperfect noncircular gear 5 is 60 degree by two radians 29, radian are 60 degree 30, a radian are that 180 degree form without flute profile district 31; At the uniform velocity district 30 in the described pitch curve 28 that initiatively switches imperfect noncircular gear 5 is positioned at and has parts of tooth, corresponding orthodrome R1 region; In the described pitch curve 28 that initiatively switches imperfect noncircular gear 5 without corresponding small arc-shaped R2 region, flute profile district 31; The center line that initiatively switches imperfect noncircular gear 5 passes through an at the uniform velocity middle teeth groove of district 30; The described number of teeth of initiatively switching imperfect noncircular gear 5 is even number, and teeth groove number is odd number,
At the uniform velocity district that speed-change area that the pitch curve 33 of the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching is 60 degree by two angles 35, radian are 180 degree 37, a radian are forming without flute profile district 36 of 60 degree; At the uniform velocity district 37 in the pitch curve 33 of the imperfect noncircular gear 4 of described the first driven switching and the imperfect noncircular gear 6 of the second driven switching is positioned at and has parts of tooth, corresponding small arc-shaped R2 region; In the pitch curve 33 of the imperfect noncircular gear 4 of described the first driven switching and the imperfect noncircular gear 6 of the second driven switching without corresponding orthodrome R1 region, profile of tooth district 36; The rotation centerline of the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching passes through at the uniform velocity gear teeth at 37 positions, stage casing, district; The number of teeth of the imperfect noncircular gear 4 of described the first driven switching and the imperfect noncircular gear 6 of the second driven switching is odd numbers, and teeth groove number is even number,
The described rotating center " 0 " that initiatively switches imperfect noncircular gear 5, the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching, is the geometrical center of orthodrome R1 and small arc-shaped R2,
Initiatively switch imperfect noncircular gear 5 and engage when running with the imperfect noncircular gear 6 of the driven switching of the imperfect noncircular gear 4 or the second of the first driven switching, in the time that the imperfect noncircular gear engagement of driven switching moves at the uniform velocity district, its velocity ratio I coincidence formula:
I＝R1/R2，
The interval of I is: greatest measure is Imax=R1: minimum value is Imin=1/R1;
The mathematic(al) representation F (α) of the pitch curve 34 of the described pitch curve 32, the imperfect noncircular gear 4 of the first driven switching and imperfect noncircular gear 6 speed-change areas 35 of the second driven switching that initiatively switch imperfect noncircular gear 5 speed-change areas 29 is coincidence formula all:
F(α)=R1*sin(α)/R2；
Wherein:
R1 is the radius that initiatively switches the orthodrome region of the pitch curve 33 of pitch curve 28, the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching of imperfect noncircular gear 5;
R2 is the radius that initiatively switches the small arc-shaped region of the pitch curve 33 of pitch curve 28, the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching of imperfect noncircular gear 5;
α initiatively switches any point on speed-change area 35 pitch curves 34 of speed-change area 29 pitch curves 32, the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching of imperfect noncircular gear 5 in its corresponding angle in complete pitch curve system of coordinates separately.
4. according to the reciprocal imperfect non-circular gear transmission of the switching one of claim 1-3 Suo Shu, it is characterized in that, at described 2 speed-change areas that initiatively switch imperfect noncircular gear 5 29 near respectively there is a distortion teeth change 39 without the end in flute profile district 31; At 2 speed-change areas 35 of the imperfect noncircular gear 4 of described the first driven switching and the imperfect noncircular gear 6 of the second driven switching near respectively there is a distortion teeth change teeth groove 38 without the end in flute profile district 36.
5. the reciprocal imperfect non-circular gear transmission of switching according to claim 4, it is characterized in that, the transverse tooth thickness of the described distortion teeth change 39 of initiatively switching imperfect noncircular gear 5 is to be adjacent 3 times of gear teeth transverse tooth thickness, the whole depth of distortion teeth change 39 is to be adjacent 1.0 times to 1.65 times of gear teeth whole depth, the addendum line line segment shape of distortion teeth change 39 is parallel with the pitch curve line segment being adjacent, and the flank profil of this distortion teeth change 39 is still involute profile.
6. the reciprocal imperfect non-circular gear transmission of switching according to claim 5, it is characterized in that, the teeth groove thickness of the distortion teeth change teeth groove 38 of the imperfect noncircular gear 4 of described the first driven switching and the imperfect noncircular gear 6 of the second driven switching is 3 times of the gear teeth teeth groove thickness that is adjacent, the gullet depth of distortion teeth change teeth groove 38 is 1.0 times to 1.75 times of the gear teeth gullet depth that is adjacent, and the line segment shape of the Root line of distortion teeth change teeth groove 38 is parallel with the pitch curve line segment being adjacent.
7. a driving mechanism, is characterized in that, this driving mechanism comprises the reciprocal imperfect non-circular gear transmission of switching as described in one of claim 1-6.
8. driving mechanism according to claim 7, it is characterized in that, the input shaft 1 of the reciprocal imperfect non-circular gear transmission of switching in this driving mechanism is implemented power input after can being connected by coupling with the one or more combination in sprocket wheel, belt pulley, all kinds of gear mechanism.
9. according to the driving mechanism described in claim 7 or 8, it is characterized in that, the output shaft 10 of the reciprocal imperfect non-circular gear transmission of described switching is connected by coupling and the 3rd transmission shaft 21 and the three cylindrical gear 13 being located thereon, the 4th transmission shaft 15 and the 4th cylindrical gears 14 that is located thereon, thereby realizes power output.
10. according to the driving mechanism described in claim 7 or 8, it is characterized in that, the output shaft 10 of the reciprocal imperfect non-circular gear transmission of described switching by coupling with can with sprocket system, belt train or sprocket wheel, belt pulley, Cylinder Gear train in one of or be connected, thereby realize power output.
11. 1 kinds of vertical oil-pumping machines, is characterized in that, its sucker rod changement is up and down reciprocatingly the driving mechanism of having installed as described in one of claim 7-10.
Brief description of the drawings:
Fig. 1 is a kind of sketch that switches reciprocal imperfect non-circular gear transmission of the present invention.
Fig. 2 switches the phase diagram that the imperfect noncircular gear 5 of initiatively switching of reciprocal imperfect non-circular gear transmission turns clockwise in the time that initial 0 spends in Fig. 1.
Fig. 3 switches the phase diagram that the imperfect noncircular gear 5 of initiatively switching of reciprocal imperfect non-circular gear transmission turns clockwise in the time that 180 spend in Fig. 1.
Fig. 4 initiatively switches the instantaneous state that imperfect noncircular gear 5 switches to the imperfect noncircular gear 6 of the second driven switching.
Fig. 5 is the imperfect noncircular gear 6 of the second driven switching output speed instantaneous state in rotary course from slow to fast while being rotated counterclockwise.
Fig. 6 is the imperfect noncircular gear 6 of the second driven switching output speed instantaneous state at the uniform velocity, in fast rotational process while being rotated counterclockwise.
Fig. 7 is the imperfect noncircular gear 6 of the second driven switching output speed instantaneous state in rotary course from fast to slow while being rotated counterclockwise.
Fig. 8 initiatively switches the instantaneous state that imperfect noncircular gear 5 switches to the imperfect noncircular gear 4 of the first driven switching.
Fig. 9 is the imperfect noncircular gear 4 of the first driven switching output speed instantaneous state in rotary course from slow to fast while being rotated counterclockwise.
The instantaneous state of output speed at the uniform velocity, in fast rotational process when Figure 10 shows the imperfect noncircular gear 4 of the first driven switching and is rotated counterclockwise.
An output speed instantaneous state in rotary course from fast to slow when Figure 11 shows the imperfect noncircular gear 4 of the first driven switching and is rotated counterclockwise.
Figure 12 initiatively switches the moment that imperfect noncircular gear 5 switches to the imperfect noncircular gear 6 of the second driven switching again, and the motion of again new reciprocal switching rotation direction has started.
Figure 13 is the another kind of sketch that switches reciprocal imperfect non-circular gear transmission of the present invention.
Figure 14 is the sketch of the reciprocal imperfect non-circular gear transmission of another switching of the present invention.
Figure 15 is pitch curve 33 and the velocity distribution region of the imperfect noncircular gear 4 of the first driven switching of the present invention, the imperfect noncircular gear 6 of the second driven switching.
Figure 16 is pitch curve 28 and velocity distribution region of initiatively switching imperfect noncircular gear 5 of the present invention.
Figure 17 is the distortion teeth change gear teeth and the distortion teeth change teeth groove that initiatively switches imperfect noncircular gear 5, the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching of the present invention.
Figure 18 is the sketch that switches its input of reciprocal imperfect non-circular gear transmission affix, output driving mechanism shown in Fig. 1.
Figure 19 is the sketch of the present invention has been installed switches the vertical oil-pumping machine of reciprocal imperfect non-circular gear transmission and driving mechanism thereof.
Embodiment:
A kind of reciprocal imperfect non-circular gear transmission (Fig. 1) and driving mechanism (Figure 18) thereof of switching of the present invention, can provide input shaft continuous rotation output shaft back and forth to switch the function (Fig. 1, Fig. 2, Fig. 3) of rotation direction rotation output by clockwise, counterclockwise or counterclockwise, clockwise rotation regulation.
As an embodiment, we are arranged on the vertical oil-pumping machine of petroleum drilling and mining industry (Figure 18), realized commutation reliably, accurately convenient, increased substantially the performance of vertical oil-pumping machine.We narrate respectively embodiments of the present invention below.
1. switch the embodiment of reciprocal imperfect non-circular gear transmission
Fig. 1 shows that to switch reciprocal imperfect non-circular gear transmission be by input shaft 1 and is positioned at and initiatively switches imperfect noncircular gear 5 on this input shaft 1, the first transmission shaft 2 and be positioned at the imperfect noncircular gear 4 of the first driven switching and the first cylindrical gears 8 on this first transmission shaft 2, second driving shaft 3 and be positioned at the imperfect noncircular gear 6 of the second driven switching and the second cylindrical gears 7 on this second driving shaft 3, output shaft 10 and be positioned at the output shaft cylindrical gears 9 on this output shaft 10, casing 11, case lid 12 component such as grade form.
Simultaneously, Fig. 1 also shows the critical function gear train that makes output shaft 10, the first transmission shaft 2, the second driving shaft 3 of the reciprocal imperfect non-circular gear transmission of this switching can back and forth switch rotation direction and is out of shape the formation of switching gear train, and it is namely initiatively to switch 5 and 2 imperfect noncircular gears of driven switching of imperfect noncircular gear by 1 driving gear namely the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching form.Initiatively switching imperfect noncircular gear 5 is mounted on input shaft 1, the imperfect noncircular gear 4 of the first driven switching is mounted on the first transmission shaft 2, the imperfect noncircular gear 6 of the second driven switching is arranged on second driving shaft 3, and these 2 imperfect noncircular gears of driven switching are arranged on respectively and initiatively switch the both sides of imperfect noncircular gear 5 and engagement installation side by side.
Fig. 1 also shows the imperfect noncircular gear 4 of the first driven switching and is connected with the coaxial installation of the first cylindrical gears 8 coaxial power, the imperfect noncircular gear 6 of the second driven switching is connected with the coaxial installation of the second cylindrical gears 7 coaxial power, wherein, the second cylindrical gears 7 and the intermeshing installation of the first cylindrical gears 8, be arranged on 9 of output shaft cylindrical gearss on output shaft 10 intermeshing and back and forth switch rotatablely moving of rotation direction to switching transmission outside reciprocal imperfect non-circular gear transmission with the first cylindrical gears 8.
The reciprocal imperfect non-circular gear transmission of this switching after Fig. 2 shows and installs initiatively switches the phase diagram of imperfect noncircular gear 5 in the time that 0 spends while work:
Turn clockwise and start and enter when intermeshing with the parts of tooth that has of the imperfect noncircular gear 6 of the second driven switching when initiatively switching imperfect noncircular gear 5, the second cylindrical gears 7 that the imperfect noncircular gear 6 of the second driven switching is connected with coaxial power starts to be rotated counterclockwise, the first cylindrical gears 8 engaging with the second cylindrical gears 7 and the imperfect noncircular gear 4 of the first driven switching being connected with the coaxial power of the first cylindrical gears 8 turn clockwise, the output shaft 10 being connected with 9 of the intermeshing cylindrical gearss of the first cylindrical gears 8 turning clockwise and power is rotated counterclockwise simultaneously.Engage with the imperfect noncircular gear 6 of driven switching and turned clockwise 180 while spending when initiatively switching imperfect noncircular gear 5, second driving shaft 3 and the imperfect noncircular gear 6 of the second driven switching being located thereon and the second cylindrical gears 7, output shaft 10 and the output shaft cylindrical gears 9 being located thereon have been rotated counterclockwise once, and the first transmission shaft 2 and the imperfect noncircular gear 4 of the first driven switching, 8 of the first cylindrical gearss that are located thereon have turned clockwise once.
Fig. 3 shows and initiatively switches the phase diagram of imperfect noncircular gear 5 in the time that 180 spend:
Continue to turn clockwise and start and enter when intermeshing with the parts of tooth that has of the imperfect noncircular gear 4 of the first driven switching when initiatively switching imperfect noncircular gear 5, the first cylindrical gears 8 that the imperfect noncircular gear 4 of the first driven switching is connected with coaxial power is all rotated counterclockwise, the second cylindrical gears 7 engaging with the first cylindrical gears 8 and the imperfect noncircular gear 6 of the second driven switching being connected with the coaxial power of the first cylindrical gears 7 turn clockwise, turn clockwise with 9 output shafts that are connected with power 10 of the intermeshing output shaft cylindrical gears of the first cylindrical gears 8 that are rotated counterclockwise simultaneously, engage with the imperfect noncircular gear 4 of the first driven switching and continue clockwise to have rotated after 180 degree when initiatively switching imperfect noncircular gear 5, second driving shaft 3 and the imperfect noncircular gear 6 of the second driven switching and the second cylindrical gears 7 that are located thereon, output shaft 10 and the output shaft cylindrical gears 9 being located thereon have turned clockwise once, the first transmission shaft 2 and the imperfect noncircular gear 4 of the first driven switching being located thereon, the first 8 of cylindrical gearss have been rotated counterclockwise once.
Fig. 4 shows and initiatively switches the instantaneous state that imperfect noncircular gear 5 switches to the imperfect noncircular gear 6 of the second driven switching.
An output speed instantaneous state in rotary course from slow to fast when Fig. 5 shows the imperfect noncircular gear 6 of the second driven switching and is rotated counterclockwise.
The instantaneous state of output speed at the uniform velocity, in fast rotational process when Fig. 6 shows the imperfect noncircular gear 6 of the second driven switching and is rotated counterclockwise.
An output speed instantaneous state in rotary course from fast to slow when Fig. 7 shows the imperfect noncircular gear 6 of the second driven switching and is rotated counterclockwise.
Fig. 8 shows and initiatively switches the instantaneous state that imperfect noncircular gear 5 switches to the imperfect noncircular gear 4 of the first driven switching.
An output speed instantaneous state in rotary course from slow to fast when Fig. 9 shows the imperfect noncircular gear 4 of the first driven switching and is rotated counterclockwise.
The instantaneous state of output speed at the uniform velocity, in fast rotational process when Figure 10 shows the imperfect noncircular gear 4 of the first driven switching and is rotated counterclockwise.
An output speed instantaneous state in rotary course from fast to slow when Figure 11 shows the imperfect noncircular gear 4 of the first driven switching and is rotated counterclockwise.
Figure 12 shows and initiatively switches the moment that imperfect noncircular gear 5 switches to the imperfect noncircular gear 6 of the second driven switching again, and new output again is back and forth switched rotatablely moving of rotation direction and started.
Figure 13 shows the another kind of reciprocal imperfect non-circular gear transmission that switches of the present invention: in the time that main frame does not need the rotating speed of the first transmission shaft 2 or second driving shaft 3 to change, the output shaft cylindrical gears 9 that can remove output shaft 10 and be located thereon, directly adopt the first transmission shaft 2 or second driving shaft 3 as output shaft, so still can reach the back and forth object rotatablely moving of switching rotation direction of output.
Figure 14 shows the reciprocal imperfect non-circular gear transmission of another switching of the present invention: in the time that main frame need to add one or several output shafts in the reciprocal imperfect non-circular gear transmission of described switching again, we can increase a set of or several covers " output shaft 10 and be positioned at the output shaft cylindrical gears 9 on output shaft 10 " again, and in the output shaft cylindrical gears 9 that makes newly to increase and casing, original output shaft cylindrical gears 9 or the second cylindrical gears 7 are intermeshing, form by the first transmission shaft 2, second driving shaft 3, the output function of sense of rotation is back and forth switched in the multiaxis multiposition output of one or more output shaft 10 common compositions.
2. initiatively switch the specific implementation method of the imperfect noncircular gear 4 of imperfect noncircular gear 5 and the first driven switching, the imperfect noncircular gear 6 of the second driven switching:
Fig. 2 and Fig. 3 also show and initiatively switch imperfect noncircular gear 5 and the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching switching the ordered state after assembling in reciprocal imperfect non-circular gear transmission.
Figure 15 and Figure 16 show respectively the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching, initiatively switch the pitch curve form of imperfect noncircular gear 5, and they are made up of orthodrome R1 and small arc-shaped R2 and the speed-change area pitch curve between R1, R2.
Figure 15 shows at the uniform velocity district that speed-change area that the pitch curve 33 of the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching is 60 degree by two angles 35, radian are 180 degree 37, a radian is forming without flute profile district 36 of 60 degree.At the uniform velocity district 37 in the pitch curve 33 of the imperfect noncircular gear 4 of this first driven switching, the imperfect noncircular gear 6 of the second driven switching is positioned at and has parts of tooth, corresponding small arc-shaped R2 region.Simultaneously should be from the pitch curve 33 of the first dynamic deformation change gear 4, the imperfect noncircular gear 6 of the second driven switching without corresponding orthodrome R1 region, profile of tooth district 36.Pass through at the uniform velocity gear teeth at 37 positions, stage casing, district according to the rotation centerline of the imperfect noncircular gear 4 of the first driven switching of above-mentioned pitch curve completion of processing, the imperfect noncircular gear 6 of the second driven switching, and the number of teeth of the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching is odd numbers, teeth groove number is even number.
It is that the speed-change area that is 60 degree by two radians 29, radian at the uniform velocity district that is 60 degree 30, a radian are that 180 degree form without flute profile district 31 that Figure 16 shows the pitch curve 28 that initiatively switches imperfect noncircular gear 5.This initiatively switches at the uniform velocity district 30 in the pitch curve 28 of imperfect noncircular gear 5 and is positioned at and has parts of tooth, corresponding orthodrome R1 region.Simultaneously this initiatively switch in the pitch curve 28 of imperfect noncircular gear 5 without corresponding small arc-shaped R2 region, flute profile district 31.According to the rotation centerline that initiatively switches imperfect noncircular gear 5 of above-mentioned pitch curve completion of processing, by a teeth groove in the middle of district at the uniform velocity 30, and the number of teeth of initiatively switching imperfect noncircular gear 5 is even number, and teeth groove number is odd number.
Figure 15 also illustrates with Figure 16: initiatively switching imperfect noncircular gear 5 is similar to the pitch curve form of the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching, but its each region parameter numerical value is not identical.Because the reciprocal imperfect non-circular gear transmission load variations form of described switching and motion require to have diversity, therefore the pitch curve 33 that initiatively switches the pitch curve 28 of imperfect noncircular gear 5 and the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching also has diversity, has also just determined initiatively to switch imperfect noncircular gear 5 and the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching also have diversity simultaneously.
Figure 15 and Figure 16 further show design principle and the method for initiatively switching imperfect noncircular gear and the imperfect noncircular gear of driven switching, can find out the rotating center " 0 " that initiatively switches the imperfect noncircular gear 4 of the driven switching of imperfect noncircular gear 5 or the first, the imperfect noncircular gear 6 of the second driven switching, be the geometrical center of orthodrome R1 and small arc-shaped R2.
Initiatively switching imperfect noncircular gear (5) engages with the imperfect noncircular gear of the first driven switching (4) or the imperfect noncircular gear of the second driven switching (6) while running, in the time that the engagement of the imperfect noncircular gear of driven switching moves at the uniform velocity district, its velocity ratio I coincidence formula:
I＝R1/R2，
The interval of I is: greatest measure is Imax=R1, and minimum value is Imin=1/R1;
The imperfect noncircular gear of the driven switching of pitch curve 32 or the first of the described speed-change area 29 that initiatively switches imperfect noncircular gear 54, second from
Mathematic(al) representation F (α) coincidence formula of the pitch curve 34 of the speed-change area 35 of dynamic deformation change gear 6:
F(α)=R1*sin(α)/R2；
Wherein:
R1 initiatively switches the pitch curve 28 of imperfect noncircular gear 5 or the radius from the orthodrome region of the pitch curve 33 of the first dynamic deformation change gear 4, the imperfect noncircular gear 6 of the second driven switching;
R2 is the radius in the small arc-shaped region of the pitch curve 33 of the imperfect noncircular gear 4 of the driven switching of pitch curve 28 or the first that initiatively switches imperfect noncircular gear 5, the imperfect noncircular gear 6 of the second driven switching;
α initiatively switches any point on speed-change area 35 pitch curves 34 of speed-change area 29 pitch curves 32, the imperfect noncircular gear 4 of the first driven switching and the imperfect noncircular gear 6 of the second driven switching of imperfect noncircular gear 5 in its corresponding angle in complete pitch curve system of coordinates separately.
Figure 17 shows the imperfect noncircular gear 5 that initiatively switches of completion of processing on numerical control machine tool 2 speed-change areas 29, this speed-change area 29 is near respectively there is a distortion teeth change 39 without the end in flute profile district 31, at 2 speed-change areas 35 of the imperfect noncircular gear 4 of described the first driven switching, the imperfect noncircular gear 6 of the second driven switching near respectively there is a distortion teeth change teeth groove 38 without the end in flute profile district 36.
The technical requirements of distortion teeth change 39 that imperfect noncircular gear 5 is initiatively switched in processing is: the transverse tooth thickness of being out of shape teeth change 39 is to be adjacent 3 times of gear teeth transverse tooth thickness, the whole depth of distortion teeth change 39 is to be adjacent 1.0 times to 1.65 times of gear teeth whole depth, the addendum line line segment shape of distortion teeth change 39 is parallel with the pitch curve line segment being adjacent, and the flank profil of this distortion teeth change 39 is still involute profile.
The technical requirements of processing the distortion teeth change teeth groove 38 of the imperfect noncircular gear 4 of the first driven switching, the imperfect noncircular gear 6 of the second driven switching is: the teeth groove thickness of distortion teeth change teeth groove 38 is 3 times of the gear teeth teeth groove thickness that is adjacent, the teeth groove overall height of distortion teeth change teeth groove 38 is 1.0 times to 1.75 times of the gear teeth teeth groove overall height that is adjacent, and the line segment shape of the Root line of distortion teeth change teeth groove 38 is parallel with the pitch curve line segment being adjacent.
After the imperfect noncircular gear group of above-mentioned switching is processed and is assembled, can turn round and switch reciprocal imperfect non-circular gear transmission, the reciprocal imperfect non-circular gear transmission of switching now the output speed clockwise and in counterclockwise two sense of rotation also just had from slowly to soon, at the uniform velocity fast, near slowly, again to the velocity variations feature of switching rotation direction.
3. switch the implementation methods of reciprocal imperfect non-circular gear transmission and driving mechanism thereof
The reciprocal imperfect non-circular gear transmission of switching shown in Figure 18 and driving mechanism thereof are by switching reciprocal imperfect non-circular gear transmission, with output shaft 10 or the first transmission shaft 2, the 3rd transmission shaft 21 that second driving shaft 3 power connect and the three cylindrical gear 13 being located thereon, the 4th transmission shaft 15 and the 4th cylindrical gears 14 being located thereon, the 5th transmission shaft 16 being connected with input shaft 1 power and the belt pulley 17 being located thereon, the 6th input shaft 18 and the belt pulley 19 being located thereon, the belt 20 being positioned on belt pulley 17 and belt pulley 18 forms.
Figure 18 also shows three cylindrical gear 13 and the 4th cylindrical gears 14 is intermeshing relations, and any one end of the 3rd transmission shaft 21 all can adopt the shaft end of coupling and output shaft 10 or the first transmission shaft 2, second driving shaft 3 to implement power and be connected.Input shaft 1 and the 5th transmission shaft 16 are also to adopt coupling interconnective.
Wherein, input shaft 1 can also be realized power by coupling with the 5th transmission shaft 16 with the combination in any of sprocket wheel or all kinds of gear mechanism or sprocket wheel, belt pulley, all kinds of gear mechanisms and is connected.
Figure 18 further shows us can be with one or more sets " three cylindrical gears 13, the 4th cylindrical gears 14, the 4th output shaft 15, the 3rd transmission shaft 21 " with the first transmission shaft 2 of the reciprocal imperfect non-circular gear transmission of described switching or second driving shaft 3 or output shaft 10 or simultaneously and the first transmission shaft 2, second driving shaft 3, the power that each axle head of output shaft 10 is implemented single shaft or multiaxis connects (as shown in phantom in Figure 16), the method that its power connects is by coupling and the first transmission shaft 2 or second driving shaft 3 or output shaft 10 or while and the first transmission shaft 2 by the axle head of one or more the 3rd transmission shafts 21, second driving shaft 3, each axle head of output shaft 10 is connected, can realize single shaft and export back and forth rotatablely moving or back and forth rotatablely moving of switching rotation direction of multiaxis multiposition output of switching rotation direction.Three cylindrical gear 13 in this driving mechanism, the 4th cylindrical gears 14 can also substitute by the combination in any of other sprocket wheels or belt pulley or Cylinder Gear train or sprocket wheel, belt pulley, Cylinder Gear train.
4. the specific implementation method of vertical oil-pumping machine
Vertical oil-pumping machine shown in Figure 19 is on the basis of existing vertical oil-pumping machine, removes this existing transmission in vertical oil-pumping machine ground and changement, retain existing vertical oil-pumping machine frame 23, sucker rod 24,
The parts such as belt 25, balancer weight 26, cylinder 27, and install the reciprocal imperfect non-circular gear transmission of switching of the present invention and driving mechanism thereof, can form a kind of novel vertical pumping unit that switches up-down stroke direction that has.
Concrete installation method is:
The shaft end of the 5th transmission shaft 16 in driving mechanism is connected by coupling with the shaft end of the input shaft 1 that switches reciprocal imperfect non-circular gear transmission, the shaft end of the 6th transmission shaft 18 is connected by coupling with the shaft end of motor 22, the combination in any that can make to be positioned at sprocket wheel on the 5th transmission shaft 16 and the 6th transmission shaft 18 or belt pulley or gear mechanism or sprocket wheel, belt pulley, gear mechanism runs well, and realizes the power input of vertical oil-pumping machine.
Be connected by coupling with the 3rd transmission shaft 21 switching reciprocal imperfect non-circular gear transmission and the output shaft (10) of driving mechanism thereof or the shaft end of the first transmission shaft (2) or second driving shaft (3), make to be positioned at the three cylindrical gear 13 on the 3rd transmission shaft 21, be positioned at the 4th cylindrical gears 14 correct engagement on the 4th transmission shaft 15, again the shaft end of the 4th shaft end of transmission shaft (15) and the component drum 27 of former vertical oil-pumping machine is connected by coupling, can realize the power conduction of vertical pumping unit, and this novel vertical pumping unit is run well.
This novel vertical pumping unit that switches reciprocal imperfect non-circular gear transmission and driving mechanism thereof of having installed, implement the commutation function of up-down stroke because its changement has adopted the reciprocal imperfect non-circular gear transmission of reliable switching, the insecure technical barrier of vertical oil-pumping machine commutation function is in the past overcome.
Claims (11)
1. one kind switches reciprocal imperfect non-circular gear transmission, comprise input shaft (1) and be positioned at and initiatively switch imperfect noncircular gear (5) on this input shaft (1), the first transmission shaft (2) and be positioned at the imperfect noncircular gear of the first driven switching (4) and the first cylindrical gears (8) on this first transmission shaft (2), second driving shaft (3) and be positioned at the imperfect noncircular gear of the second driven switching (6) and the second cylindrical gears (7) on this second driving shaft (3), casing (11) and case lid (12), the imperfect noncircular gear of described the first driven switching (4), the imperfect noncircular gear of the second driven switching (6) is positioned at described initiatively the switch both sides of imperfect noncircular gear (5) and engagement installation side by side, the imperfect noncircular gear of the first driven switching (4), it is from slowly to soon that the rotational speed of the imperfect noncircular gear of the second driven switching (6) changes, at the uniform velocity quick, from near slowly, arrive again and switch rotation direction, when input shaft (1) and be located thereon initiatively switch imperfect noncircular gear (5) according to every rotating 360 degrees clockwise or counterclockwise time, the first transmission shaft (2) and second driving shaft (3) are simultaneously according to counterclockwise, clockwise or clockwise, the each rotation of counterclockwise order once,
It is characterized in that:
Initiatively switching imperfect noncircular gear (5) turns clockwise and starts and enter when intermeshing with the parts of tooth that has of the imperfect noncircular gear of the second driven switching (6), the second cylindrical gears (7) that the imperfect noncircular gear of the second driven switching (6) is connected with coaxial power starts to be rotated counterclockwise, turn clockwise with first cylindrical gears (8) of the second cylindrical gears (7) engagement and the imperfect noncircular gear of the first driven switching (4) being connected with the coaxial power of the first cylindrical gears (8), engage with the imperfect noncircular gear of the second driven switching (6) and turned clockwise 180 while spending when initiatively switching imperfect noncircular gear (5), second driving shaft (3) and the imperfect noncircular gear of the second driven switching (6) being located thereon and the second cylindrical gears (7) have been rotated counterclockwise once, the first transmission shaft (2) and the imperfect noncircular gear of the first driven switching (4) being located thereon, the first cylindrical gears (8) has turned clockwise once,
Continue to turn clockwise and start and enter when intermeshing with the parts of tooth that has of the imperfect noncircular gear of the first driven switching (4) when initiatively switching imperfect noncircular gear (5), the first cylindrical gears (8) that the imperfect noncircular gear of the first driven switching (4) is connected with coaxial power is all rotated counterclockwise, turn clockwise with second cylindrical gears (7) of the first cylindrical gears (8) engagement and the imperfect noncircular gear of the second driven switching (6) being connected with the coaxial power of the second cylindrical gears (7), engage with the imperfect noncircular gear of the first driven switching (4) and continue clockwise to have rotated 180 while spending when initiatively switching imperfect noncircular gear (5), second driving shaft (3) and the imperfect noncircular gear of the second driven switching (6) being located thereon and the second cylindrical gears (7) have turned clockwise once, the first transmission shaft (2) and the imperfect noncircular gear of the first driven switching (4) being located thereon, the first cylindrical gears (8) has been rotated counterclockwise once.
2. the reciprocal imperfect non-circular gear transmission of switching according to claim 1, it is characterized in that, it also has output shaft 10 and is positioned at the output shaft cylindrical gears (9) on this output shaft (10), described output shaft cylindrical gears (9) engages with described the first cylindrical gears (8) or with the second cylindrical gears (7), or adopts 2 groups of output shafts (10) and the output shaft cylindrical gears (9) that is located thereon to engage with the first cylindrical gears (8) and the second cylindrical gears (7) simultaneously.
3. the reciprocal imperfect non-circular gear transmission of switching according to claim 1, is characterized in that:
At the uniform velocity district (30), a radian that speed-change area (29) that the described pitch curve (28) that initiatively switches imperfect noncircular gear (5) is 60 degree by two radians, radian are 60 degree are that 180 degree form without flute profile district (31); At the uniform velocity district (30) in the described pitch curve (28) that initiatively switches imperfect noncircular gear (5) is positioned at and has parts of tooth, corresponding orthodrome R1 region; In the described pitch curve (28) that initiatively switches imperfect noncircular gear (5) without corresponding small arc-shaped R2 region, flute profile district (31); The center line that initiatively switches imperfect noncircular gear (5) passes through at the uniform velocity middle teeth groove of district (30); The described number of teeth of initiatively switching imperfect noncircular gear (5) is even number, and teeth groove number is odd number,
At the uniform velocity district (37), a radian that speed-change area (35) that the pitch curve (33) of the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) is 60 degree by two angles, radian are 180 degree are forming without flute profile district (36) of 60 degree; At the uniform velocity district (37) in the pitch curve (33) of the imperfect noncircular gear of described the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) is positioned at and has parts of tooth, corresponding small arc-shaped R2 region; In the pitch curve (33) of the imperfect noncircular gear of described the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) without corresponding orthodrome R1 region, profile of tooth district (36); The rotation centerline of the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) passes through at the uniform velocity gear teeth at position, stage casing, district (37); The number of teeth of the imperfect noncircular gear of described the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) is odd number, and teeth groove number is even number,
The described rotating center " 0 " that initiatively switches imperfect noncircular gear (5), the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6), it is the geometrical center of orthodrome R1 and small arc-shaped R2
Initiatively switching imperfect noncircular gear (5) engages with the imperfect noncircular gear of the first driven switching (4) or the imperfect noncircular gear of the second driven switching (6) while running, in the time that the engagement of the imperfect noncircular gear of driven switching moves at the uniform velocity district, its velocity ratio I coincidence formula:
I=R1/R2，
The interval of I is: greatest measure is Imax=R1: minimum value is Imin=1/R1;
The mathematic(al) representation F (α) of the pitch curve (34) of the described pitch curve (32), the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) speed-change area (35) that initiatively switch imperfect noncircular gear (5) speed-change area (29) is coincidence formula all:
F(α)=R1*sin(α)/R2；
Wherein:
R1 is for initiatively switching the radius in the orthodrome region of the pitch curve (33) of pitch curve (28), the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) of imperfect noncircular gear (5);
R2 is for initiatively switching the radius in the small arc-shaped region of the pitch curve (33) of pitch curve (28), the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) of imperfect noncircular gear (5);
α is for initiatively switching any point on speed-change area (35) pitch curve (34) of speed-change area (29) pitch curve (32), the imperfect noncircular gear of the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) of imperfect noncircular gear (5) in its angle of correspondence in complete pitch curve system of coordinates separately.
4. according to the reciprocal imperfect non-circular gear transmission of the switching one of claim 1-3 Suo Shu, it is characterized in that, at described 2 speed-change areas (29) that initiatively switch imperfect noncircular gear (5) near respectively there is a distortion teeth change (39) without the end of flute profile district (31); At 2 speed-change areas (35) of the imperfect noncircular gear of described the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) near respectively there is a distortion teeth change teeth groove (38) without the end of flute profile district (36).
5. the reciprocal imperfect non-circular gear transmission of switching according to claim 4, it is characterized in that, the transverse tooth thickness of the described distortion teeth change (39) of initiatively switching imperfect noncircular gear (5) is to be adjacent 3 times of gear teeth transverse tooth thickness, the whole depth of distortion teeth change (39) is to be adjacent 1.0 times to 1.65 times of gear teeth whole depth, the addendum line line segment shape of distortion teeth change (39) is parallel with the pitch curve line segment being adjacent, and the flank profil of this distortion teeth change (39) is still involute profile.
6. the reciprocal imperfect non-circular gear transmission of switching according to claim 5, it is characterized in that, the teeth groove thickness of the distortion teeth change teeth groove (38) of the imperfect noncircular gear of described the first driven switching (4) and the imperfect noncircular gear of the second driven switching (6) is 3 times of the gear teeth teeth groove thickness that is adjacent, the gullet depth of distortion teeth change teeth groove (38) is 1.0 times to 1.75 times of the gear teeth gullet depth that is adjacent, and the line segment shape of the Root line of distortion teeth change teeth groove (38) is parallel with the pitch curve line segment being adjacent.
7. a driving mechanism, is characterized in that, this driving mechanism comprises the reciprocal imperfect non-circular gear transmission of switching as described in one of claim 1-6.
8. driving mechanism according to claim 7, it is characterized in that, the input shaft (1) of the reciprocal imperfect non-circular gear transmission of switching in this driving mechanism is implemented power input after can being connected by coupling with the one or more combination in sprocket wheel, belt pulley, all kinds of gear mechanism.
9. according to the driving mechanism described in claim 7 or 8, it is characterized in that, the output shaft (10) of the reciprocal imperfect non-circular gear transmission of described switching is connected by coupling and the 3rd transmission shaft 21 and the three cylindrical gear 13 being located thereon, the 4th transmission shaft 15 and the 4th cylindrical gears 14 that is located thereon, thereby realizes power output.
10. according to the driving mechanism described in claim 7 or 8, it is characterized in that, the output shaft (10) of the reciprocal imperfect non-circular gear transmission of described switching by coupling with can with sprocket system, belt train or sprocket wheel, belt pulley, Cylinder Gear train in one of or be connected, thereby realize power output.
11. 1 kinds of vertical oil-pumping machines, is characterized in that, its sucker rod changement is up and down reciprocatingly the driving mechanism of having installed as described in one of claim 7-10.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410093553.6A CN104121338B (en) | 2014-03-14 | 2014-03-14 | One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism |
| PCT/CN2015/071166 WO2015135400A1 (en) | 2014-03-14 | 2015-01-21 | A switching reciprocating incomplete non-circular gear transmission box and a transmission mechanism thereof |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410093553.6A CN104121338B (en) | 2014-03-14 | 2014-03-14 | One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism |
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| CN104121338B CN104121338B (en) | 2018-04-10 |
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| WO2015135400A1 (en) * | 2014-03-14 | 2015-09-17 | 董剑 | A switching reciprocating incomplete non-circular gear transmission box and a transmission mechanism thereof |
| CN110030360A (en) * | 2019-04-11 | 2019-07-19 | 中国矿业大学 | A kind of design method of gear wheel reversing mechanism and its gear pair |
| CN110056615A (en) * | 2019-04-18 | 2019-07-26 | 中峰化学有限公司 | The transmission device of blanking is swung in acetic ester fiber element drying process |
| CN110425377A (en) * | 2019-08-16 | 2019-11-08 | 燕山大学 | A kind of inertia pipe robot of bidirectional-movement |
| CN111467811A (en) * | 2019-01-23 | 2020-07-31 | 智高实业股份有限公司 | Deformation gear and deformation gear transmission set using same |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3955887A (en) * | 1973-05-28 | 1976-05-11 | Canon Kabushiki Kaisha | Motion picture camera |
| JPH09229157A (en) * | 1996-02-28 | 1997-09-02 | Rhythm Watch Co Ltd | Reciprocative rotation mechanism |
| CN1229886A (en) * | 1999-04-23 | 1999-09-29 | 翟灵光 | Dual-speed energy saving beam-pumping unit with shaped wheel |
| CN2583358Y (en) * | 2002-11-01 | 2003-10-29 | 中国石油天然气股份有限公司 | Variable-speed well pumping unit |
| CN2725522Y (en) * | 2004-08-03 | 2005-09-14 | 翟灵光 | Self-speed changing energy-saving oil pumping machine |
| CN101463889A (en) * | 2008-05-26 | 2009-06-24 | 北京锋源技术有限公司 | Non-circular gear transmission and its transmission mechanism |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2082051C1 (en) * | 1994-07-20 | 1997-06-20 | Евгений Петрович Абрамцев | Device for conversion of rotary motion into compound motion |
| US6318199B1 (en) * | 2000-01-18 | 2001-11-20 | David A. Buck | Load equalizing power tong gear train |
| CN102606685A (en) * | 2011-01-25 | 2012-07-25 | 徐州非圆机械科技有限公司 | Gearbox comprising non-circular gear, internal gear and planet differential gear train |
| CN103527153B (en) * | 2013-10-25 | 2016-04-20 | 徐州非圆机械科技有限公司 | Non-circular gear up-down stroke automatic reversing cooking fume remover |
| CN104121338B (en) * | 2014-03-14 | 2018-04-10 | 董剑 | One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism |
-
2014
- 2014-03-14 CN CN201410093553.6A patent/CN104121338B/en not_active Expired - Fee Related
-
2015
- 2015-01-21 WO PCT/CN2015/071166 patent/WO2015135400A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3955887A (en) * | 1973-05-28 | 1976-05-11 | Canon Kabushiki Kaisha | Motion picture camera |
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| CN101463889A (en) * | 2008-05-26 | 2009-06-24 | 北京锋源技术有限公司 | Non-circular gear transmission and its transmission mechanism |
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| WO2015135400A1 (en) | 2015-09-17 |
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