CN104121338B - One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism - Google Patents
One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism Download PDFInfo
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- CN104121338B CN104121338B CN201410093553.6A CN201410093553A CN104121338B CN 104121338 B CN104121338 B CN 104121338B CN 201410093553 A CN201410093553 A CN 201410093553A CN 104121338 B CN104121338 B CN 104121338B
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- switching
- circular 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
- 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
- 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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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The reciprocal imperfect non-circular gear transmission of one kind switching is formed by actively switching imperfect non-circular gear (5), the imperfect non-circular gear (4) of the first driven switching, the imperfect non-circular gear (6) of the first driven switching, Cylinder Gear train, casing, case lid etc..It is a kind of when input shaft is continuously run, and output shaft is with the clockwise direction changed, the actuating unit of reciprocal switching direction of rotation counterclockwise.Actively switching imperfect non-circular gear (5) has two deformation teeth changes, the driven imperfect non-circular gear (4) (6) of switching respectively to have two deformation switching teeth groove.Actively switch imperfect non-circular gear (5), multifarious technical characteristic is presented according to different load on host computers and movement needs in the pitch curve of the driven imperfect non-circular gear (4) (6) of switching.A kind of switching reciprocal imperfect non-circular gear transmission and its transmission mechanism can be alternative some mechanically or electrically to control changement with the motion of single shaft or the reciprocal switching direction of rotation of multi-shaft output variable speed.
Description
Technical field
The present invention relates to one kind to switch reciprocal imperfect non-circular gear transmission and its transmission mechanism, and it is used to need to input
The continuous rotary motion of axle and output shaft continuously back and forth switch all kinds of mechanical mechanisms of direction of rotation.The invention belongs to plant equipment neck
Domain, it can be applied to the reciprocating reversing and transmission mechanism of light industry and machinery industry or petroleum drilling and mining industry plant equipment.
Background technology
Many plant equipment are required for the action that reciprocation cycle rotates, and some plant equipment also need to the output of multiaxis multiposition
The mechanism of reciprocal switching direction of rotation, tobacco machine, beverage machine such as light industry, package packing machine, grain and oil machinery, printing machine
Tool etc..At present, some heavy industry plant equipment are also exactly it there is an urgent need to this kind of mechanism, such as vertical oil-pumping machine of petroleum drilling and mining industry
In a typical case.The mechanical mechanism of traditional reciprocal switching direction of rotation, complex, the good structure of life and reliability
Form is few.We are analyzed using the vertical oil-pumping machine of petroleum drilling and mining industry as a classical case below.
It is well known that the beam pumping unit as oil drilling and extracting equipment main force equipment, especially to adapt to field whole day
The harsh environments of time and it is famous, while its is simple in construction, few easy workout part, solid durable, highly reliable, easy to operate, dimension
Repair conveniently, the low advantage of maintenance cost, it is occupied leading position in oil production equipment always.
With being continuously increased for well depth and yield, while with the emergence of oil mining complex situations, as high viscosity,
More waxes, sandy, more gas and waters flood with the operating mode such as deep-etching, many problems of traditional beam pumping unit is substantially displayed, it is main
If the high energy consumption of beam pumping unit, weight are big, it is difficult to realize long stroke, low jig frequency oil pumping, the sucker rod in oil pumping produces
Accident increase, the discharge capacity of oil well pump reduces etc..In order to overcome these shortcomings, many producers successively have developed forward type both at home and abroad
Oil pumper, phased crank oil pumper, air balance oil pumper etc., although overcoming some shortcomings of conventional beam-pumping unit,
But the biography still without the traditional beam pumping unit of disengaging using quadric chain by convert rotational motion for linear reciprocating motion
Flowing mode.The motion of this quadric chain and mechanical characteristic make it endure to the fullest extent in energy-saving analysis to denounce, and especially big horse traction is small
Car and the big energy consumption issues of accessory torque are constantly challenged by the scientific practice of people, all kinds of novel energy-conservings without beam pumping unit because
This also constantly comes out.
After the last century 80's, each oil production equipment manufacturer have developed the oil pumping of New-generation efficient energy-saving type in succession
Machine, correct for most of problem of above-mentioned type, and various no beam pumping units start to produce and put into oil recovery building site in succession to be made
With the vertical oil-pumping machine of no walking beam is exactly Typical Representative therein.Its advantages of is to eliminate beam pumping unit using four to connect
Power consumption transmission link of the linkage by convert rotational motion for linear motion.The characteristics of motion of vertical oil-pumping machine is using a kind of wide
Width belt or chain do clockwise, reciprocal switching rotation direction counterclockwise rotation fortune under the driving guiding of roller and roller or sprocket wheel
Dynamic, so as to drive sucker rod and oil well pump that underground crude oil is drawn on ground, the vertical oil-pumping machine of different size has difference
Stroke and jig frequency, just have the variable motion of short time, 90% length of stroke during vertical oil-pumping machine up-down stroke commutates
It is uniform motion straight up and down, thus dynamic load is smaller, exchange weight is small, simply 1 to the two/3rds of beam pumping unit point
One of.Compact-sized, floor space is small, is particularly suitable for doing long stroke pumping unit, increases stroke by increasing the sides of rack levels
Method is completed.Vertical oil-pumping machine easily realizes long stroke, and the jig frequency of long stroke pumping unit is relatively low, greatly reduces adding for kinematic system
Speed, inertial load is small, and inertial load significantly declines, and oil pumper performance is greatly improved.But this vertical oil-pumping machine
Also there is its deadly defect：One is the changement fault rate of vertical chain oil pumper is higher, and it is fragile, the second is vertical belt
The motor commutation frequency converter cost of oil pumper is high, and is difficult to be competent at round-the-clock harsh environments.So it is difficult to advise greatly so far
The replacement beam pumping unit of mould.
Find a kind of mechanical changement, make vertical oil-pumping machine both possessed beam pumping unit commutate it is reliability and durability excellent
Gesture, and manufacturing cost can be reduced simultaneously, adapt to the severe environmental conditions of all weather operations.In this way, vertical oil-pumping machine commutation portion
Part short life, insecure weakness can be obtained by effective and thorough change, so that this vertical with obvious technical advantage
Formula oil pumper more adapts to various complicated conditions of work and environment.
The content of the invention
1. the reciprocal imperfect non-circular gear transmission of one kind switching, including input shaft 1 and the master on the input shaft 1
The imperfect non-circular gear 5 of dynamic switching, the first power transmission shaft 2 and the first driven switching on first power transmission shaft 2 are imperfect
The roller gear 8 of non-circular gear 4 and first, second driving shaft 3 and on the second driving shaft 3 second it is driven switching it is endless
The whole roller gear 7 of non-circular gear 6 and second, casing 11 and case lid 12, the imperfect non-circular gear 4 of the first driven switching, the
The two driven imperfect non-circular gears 6 of switching are located at the both sides for actively switching imperfect non-circular gear 5 and side by side engagement installation,
The rotary speed change of the first imperfect non-circular gear 4 of driven switching, the second driven imperfect non-circular gear 6 of switching be from slowly to
Hurry up, be at the uniform velocity quick, near it is slow, again to switching rotation direction, disposed thereon switch when input shaft 1 and actively imperfect non-knuckle-tooth
When wheel 5 according to being often rotated by 360 ° clockwise or counterclockwise, the first power transmission shaft 2 and second driving shaft 3 are then simultaneously according to the inverse time
Pin, order clockwise or clockwise, counterclockwise respectively rotate once,
It is characterized in that：
Actively switch imperfect non-circular gear 5 to turn clockwise and start and the second driven imperfect non-circular gear 6 of switching
When thering is the parts of tooth to enter intermeshing, what the second imperfect non-circular gear 6 of driven switching was connected with coaxial power second justifies
Stud wheel 7 starts to make rotate counterclockwise, the first roller gear 8 for being engaged with the second roller gear 7 and with the first roller gear 8
The first imperfect non-circular gear 4 of driven switching of coaxial power connection turns clockwise, when actively switching imperfect non-knuckle-tooth
Wheel 5 with second it is driven switch imperfect non-circular gear 6 engage and turned clockwise 180 degree when, second driving shaft 3 and be located at
The second imperfect roller gear 7 of non-circular gear 6 and second of driven switching thereon then rotate counterclockwise once, the first power transmission shaft
2 and the disposed thereon first imperfect non-circular gear 4 of driven switching, the first roller gear 8 then turned clockwise once；
When actively switch imperfect non-circular gear 5 continue to turn clockwise and start with first it is driven switching it is imperfect not rounded
When thering is the parts of tooth to enter intermeshing of gear 4, the first imperfect non-circular gear 4 of driven switching be connected with coaxial power the
One roller gear 8 makees rotate counterclockwise, the second roller gear 7 for being engaged with the first roller gear 8 and with the second Cylinder Gear
The the second driven imperfect non-circular gear 6 of switching for taking turns the connection of 7 coaxial powers turns clockwise, imperfect not rounded when actively switching
When gear 5 engages with the first imperfect non-circular gear 4 of driven switching and continues have rotated 180 degree clockwise, second driving shaft 3 with
And the second driven imperfect roller gear 7 of non-circular gear 6 and second of switching disposed thereon has turned clockwise once, first passes
Moving axis 2 and the disposed thereon first imperfect non-circular gear 4 of driven switching, the first roller gear 8 then rotate counterclockwise one
It is secondary.
2. reciprocal one of the imperfect non-circular gear transmission, its architectural feature of switching is, main output par, c by
Output shaft 10 and the output shaft roller gear 9 on the output shaft 10 are formed, the Cylinder Gear of output shaft roller gear 9 and first
Wheel 8 engages with the second roller gear 7, or can also use 2 groups of output shafts 10 and output shaft Cylinder Gear disposed thereon
Wheel 9 engages with the first roller gear 8 and the second roller gear 7 respectively.
3. the spy for the reciprocal imperfect non-circular gear of switching installed in the reciprocal imperfect non-circular gear transmission of switching
Sign is：
Actively switch the pitch curve 28 of imperfect non-circular gear 5 by 29, radians of speed-change area that two radians are 60 degree
It is that 180 degree is formed without tooth form area 31 for 60 degree of 30, one, at the uniform velocity area radian；The section for actively switching imperfect non-circular gear 5 is bent
At the uniform velocity area 30 in line 28 corresponds to orthodrome region positioned at there is parts of tooth；Actively switch the pitch curve of imperfect non-circular gear 5
In 28 without the corresponding small arc-shaped region in tooth form area 31；The center line for actively switching imperfect non-circular gear 5 passes through at the uniform velocity area 30
Between a teeth groove；The number of teeth for actively switching imperfect non-circular gear 5 is even number, and teeth groove number is odd number.
The pitch curve 33 of the first driven driven imperfect non-circular gear 6 of switching of the imperfect non-circular gear 4 and second of switching is equal
35, radians of the speed-change area for being 60 degree by two angles are that 37, one, the at the uniform velocity area radian of 180 degree is 60 degree without tooth form area
36 are formed；In the pitch curve 33 of the first driven driven imperfect non-circular gear 6 of switching of the imperfect non-circular gear 4 and second of switching
At the uniform velocity area 37 corresponds to small arc-shaped region positioned at there is parts of tooth；The first driven imperfect non-circular gear 4 and second of switching is driven to be cut
Change in the pitch curve 33 of imperfect non-circular gear 6 without the corresponding orthodrome region in tooth form area 36；First driven switching is imperfect non-
The wheel that the rotation centerline of the driven imperfect non-circular gear 6 of switching of Knucle-gear 4 and second passes through the at the uniform velocity stage casing position of area 37
Tooth；The number of teeth of the first driven driven imperfect non-circular gear 6 of switching of the imperfect non-circular gear 4 and second of switching is odd number,
Teeth groove number is then even number,
It is described actively to switch imperfect non-circular gear 5, the first driven imperfect 4 and second driven switching of non-circular gear of switching
The pivot " O " of imperfect non-circular gear 6, it is the geometric center of orthodrome and small arc-shaped,
Actively switch the driven driven switching of the imperfect non-circular gear 4 or the second of switching of imperfect non-circular gear 5 and first not
During the complete engagement of non-circular gear 6 operating, when the imperfect non-circular gear engagement operation of driven switching is at the uniform velocity area, its gearratio I
Coincidence formula：
I=R1/R2,
I interval is：Greatest measure is Imax=R1：Minimum value is Imin=1/R1；
The pitch curve 32 for actively switching the imperfect speed-change area 29 of non-circular gear 5, the first driven switching are imperfect not rounded
The mathematic(al) representation F (α) of the pitch curve 34 of the driven imperfect speed-change area 35 of non-circular gear 6 of switching of gear 4 and second meets public affairs
Formula：
F (α)=R1*sin (α)/R2；
Wherein：
R1 is actively to switch the pitch curve 28 of imperfect non-circular gear 5, first driven switch imperfect non-circular gear 4 and the
The radius in the orthodrome region of the pitch curve 33 of the two driven imperfect non-circular gears 6 of switching；
R2 is actively to switch the pitch curve 28 of imperfect non-circular gear 5, first driven switch imperfect non-circular gear 4 and the
The radius in the small arc-shaped region of the pitch curve 33 of the two driven imperfect non-circular gears 6 of switching；
α is the 32, the first driven imperfect non-knuckle-tooth of switching of pitch curve of speed-change area 29 for actively switching imperfect non-circular gear 5
Any point on the pitch curve 34 of speed-change area 35 of the driven imperfect non-circular gear 6 of switching of wheel 4 and second is each complete at it
Corresponding angle in pitch curve coordinate system.
4. the reciprocal imperfect non-circular gear of switching, is further characterized in that, actively switching imperfect non-circular gear 5 has 2
Individual speed-change area 29, this 2 speed-change areas 29 respectively have a deformation teeth change 39 close to the end without tooth form area 31；Accordingly first
2 speed-change areas 35 of the driven driven imperfect non-circular gear 6 of switching of the imperfect non-circular gear 4 and second of switching are close to without tooth form area
Respectively there is a deformation teeth change teeth groove 38 36 end.
5. the reciprocal imperfect non-circular gear of switching, its feature are that actively switching imperfect non-circular gear 5 has 2 again
Individual deformation teeth change 39, the transverse tooth thickness of this 2 deformation teeth changes are 3 times of gear teeth transverse tooth thickness adjacent thereto, deform the tooth of teeth change 39
Overall height is 1.0 times to 1.65 times of gear teeth whole depth adjacent thereto, deform teeth change 39 addendum line line segment shape and with its phase
Adjacent pitch curve line segment is parallel, and the flank profil of the deformation teeth change 39 is also involute profile.
6. the reciprocal imperfect non-circular gear of switching, its another feature are, the first driven switching is imperfect not rounded
The driven imperfect non-circular gear 6 of switching of gear 4 and second has 2 deformation teeth change teeth groove 38, the deformation teeth change teeth groove 38
Teeth groove thickness be 3 times of gear teeth teeth groove thickness adjacent thereto, the gullet depth of deformation teeth change teeth groove 38 is adjacent thereto
1.0 times to 1.75 times of gear teeth gullet depth, the line segment shape of the dedendum line of deformation teeth change teeth groove 38 and adjacent thereto
Pitch curve line segment is parallel.
7. the reciprocal imperfect non-circular gear transmission of switching, and other transmission parts are combined can also form one kind
The non-circular gear variable transmission mechanism of direction of rotation can back and forth be switched.
8. the non-circular gear variable transmission mechanism that can back and forth switch direction of rotation, it is characterised in that the driver
The input shaft 1 of the reciprocal imperfect non-circular gear transmission of switching included in structure can with sprocket system, belt train, gear train
One or more combinations connected by shaft coupling after implement power input.
9. the non-circular gear variable transmission mechanism that can back and forth switch direction of rotation, is further characterized in that, the transmission
The output shaft 10 for the reciprocal imperfect non-circular gear transmission of switching that mechanism is included by shaft coupling and the 3rd power transmission shaft 21 with
And the 3rd roller gear 13, the 4th power transmission shaft 15 and the 4th roller gear 14 disposed thereon disposed thereon is connected and realized
Power output.
10. the non-circular gear variable transmission mechanism that can back and forth switch direction of rotation, its feature are again, the transmission
The output shaft 10 for the reciprocal imperfect non-circular gear transmission of switching that mechanism is included can be with sprocket system, belt pulley by shaft coupling
One of system, Cylinder Gear train or combination connection, so as to realize power output.
11. the transmission mechanism of this imperfect non-circular gear transmission for containing and can back and forth switching direction of rotation is used
In a kind of power drive mechanism of vertical oil-pumping machine, the vertical oil-pumping machine may dispense with motor frequency conversion changement, using machine
The mode of tool commutation, realize the technical goal of high reliability and energy-conservation.
Brief description of the drawings：
Fig. 1 is a kind of sketch of the reciprocal imperfect non-circular gear transmission of switching of the present invention.
Fig. 2 be switch in Fig. 1 reciprocal imperfect non-circular gear transmission actively to switch imperfect non-circular gear 5 clockwise
It is rotated in state diagram when originating 0 degree.
Fig. 3 be switch in Fig. 1 reciprocal imperfect non-circular gear transmission actively to switch imperfect non-circular gear 5 clockwise
It is rotated in state diagram during 180 degree.
Fig. 4 is actively to switch the instantaneous shape that imperfect non-circular gear 5 switches to the second driven imperfect non-circular gear 6 of switching
State.
Fig. 5 is the second driven output speed rotary course from slow to fast when switching imperfect 6 rotate counterclockwise of non-circular gear
In an instantaneous state.
Fig. 6 be second it is driven switch imperfect 6 rotate counterclockwise of non-circular gear when output speed at the uniform velocity, quick rotary course
In an instantaneous state.
Fig. 7 is the second driven output speed rotary course from fast to slow when switching imperfect 6 rotate counterclockwise of non-circular gear
In an instantaneous state.
Fig. 8 is actively to switch the instantaneous shape that imperfect non-circular gear 5 switches to the first driven imperfect non-circular gear 4 of switching
State.
Fig. 9 is the first driven output speed rotary course from slow to fast when switching imperfect 4 rotate counterclockwise of non-circular gear
In an instantaneous state.
Output speed at the uniform velocity, quickly revolves when Figure 10 shows the first driven switching imperfect 4 rotate counterclockwise of non-circular gear
An instantaneous state during turning.
Output speed rotates from fast to slow when Figure 11 shows the first driven switching imperfect 4 rotate counterclockwise of non-circular gear
During an instantaneous state.
Figure 12 is actively to switch imperfect non-circular gear 5 again to the second driven imperfect non-circular gear 6 of switching to switch
Moment, the motion of reciprocal switching rotation direction new again start.
Figure 13 is the sketch of the reciprocal imperfect non-circular gear transmission of another switching 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 the imperfect non-circular gear 4 of the driven switching of of the invention first, the second driven imperfect non-circular gear 6 of switching
Pitch curve 33 and VELOCITY DISTRIBUTION region.
Figure 16 is the pitch curve 28 and the VELOCITY DISTRIBUTION region that actively switch imperfect non-circular gear 5 of the present invention.
Figure 17 is actively switch imperfect non-circular gear 5, first driven switching imperfect non-circular gear 4, for the present invention
The deformation teeth change gear teeth and deformation teeth change teeth groove of the two driven imperfect non-circular gears 6 of switching.
Figure 18 is back and forth its input of imperfect non-circular gear transmission affix, the output transmission mechanism of switching shown in Fig. 1
Sketch.
Figure 19 is the vertical oil pumping for being mounted with present invention switching reciprocal imperfect non-circular gear transmission and its transmission mechanism
The sketch of machine.
Embodiment：
One kind of the present invention switches reciprocal imperfect non-circular gear transmission (Fig. 1) and its transmission mechanism (Figure 18),
The continuous rotating output shaft of input shaft can be provided by rotation regulation clockwise, counterclockwise or counterclockwise, clockwise back and forth to switch
The function (Fig. 1, Fig. 2, Fig. 3) of rotation direction rotation output.
As one embodiment, we are installed on the vertical oil-pumping machine of petroleum drilling and mining industry (Figure 18), realized
Commutation is reliable, accurate convenient, and the performance of vertical oil-pumping machine is greatly improved.We describe the embodiment party of the present invention respectively below
Formula.
1. the embodiment of the reciprocal imperfect non-circular gear transmission of switching
Fig. 1 shows that the reciprocal imperfect non-circular gear transmission of switching is by input shaft 1 and on the input shaft 1
Actively switch imperfect non-circular gear 5, the first power transmission shaft 2 and on first power transmission shaft 2 first it is driven switching it is endless
The whole roller gear 8 of non-circular gear 4 and first, second driving shaft 3 and on the second driving shaft 3 second it is driven switching not
The complete roller gear 7 of non-circular gear 6 and second, output shaft 10 and output shaft roller gear 9, case on the output shaft 10
What the parts such as body 11, case lid 12 were formed.
Meanwhile Fig. 1 is also shown for being driven the output shaft 10, first of the reciprocal imperfect non-circular gear transmission of this switching
The critical function gear train that axle 2, second driving shaft 3 can back and forth switch rotation direction deforms the composition of switching gear train, and it is by 1
Individual driving gear namely actively switches imperfect non-circular gear 5 and 2 driven imperfect non-circular gears namely first of switching
The imperfect non-circular gear 4 of driven switching, the second driven imperfect non-circular gear 6 of switching are formed.Actively switch imperfect non-
Knucle-gear 5 is mounted on input shaft 1, the first imperfect non-circular gear 4 of driven switching be mounted in the first power transmission shaft 2 it
On, the second driven imperfect non-circular gear 6 of switching is arranged on second driving shaft 3, this 2 driven imperfect non-knuckle-tooth of switching
Wheel is separately mounted to actively switch the both sides of imperfect non-circular gear 5 and side by side engagement installation.
Fig. 1 also show the first driven imperfect non-circular gear 4 of switching and be co-axially mounted with the first roller gear 8 and coaxially move
Power connects, and the second driven imperfect non-circular gear 6 of switching is co-axially mounted with the second roller gear 7 and coaxial power is connected, wherein,
Second roller gear 7 and the intermeshing of the first roller gear 8 are installed, the output shaft roller gear 9 on output shaft 10
Then it is intermeshed with the first roller gear 8 and back and forth switches rotation direction to transmission outside the reciprocal imperfect non-circular gear transmission of switching
Rotary motion.
Fig. 2 shows that this switching after installing actively switches not when back and forth imperfect non-circular gear transmission works
Complete state diagram of the non-circular gear 5 at 0 degree：
Turn clockwise and start and the second imperfect non-circular gear of driven switching when actively switching imperfect non-circular gear 5
6 when having parts of tooth entrance intermeshing, the second circle that the second driven imperfect non-circular gear 6 of switching is connected with coaxial power
Stud wheel 7 starts to make rotate counterclockwise, the first roller gear 8 for being engaged with the second roller gear 7 and with the first roller gear 8
The first driven imperfect non-circular gear 4 of switching of coaxial power connection turns clockwise, with the first cylinder to turn clockwise
The intermeshing roller gear 9 of gear 8 then does rotate counterclockwise simultaneously with the output shaft 10 of power connector.It is endless when actively switching
Whole non-circular gear 5 engaged with the imperfect non-circular gear 6 of driven switching and turned clockwise 180 degree when, second driving shaft 3 and position
The second driven the switching imperfect roller gear 7 of non-circular gear 6 and second, output shaft 10 and output disposed thereon thereon
The rotate counterclockwise of axial cylindrical gear 9 once, first power transmission shaft 2 and the disposed thereon first driven imperfect non-knuckle-tooth of switching
The 4, first roller gear 8 of wheel has then turned clockwise once.
Fig. 3 shows the state diagram for actively switching imperfect non-circular gear 5 in 180 degree：
When actively switch imperfect non-circular gear 5 continue to turn clockwise and start with first it is driven switching it is imperfect not rounded
When thering is the parts of tooth to enter intermeshing of gear 4, the first imperfect non-circular gear 4 of driven switching be connected with coaxial power the
One roller gear 8 makees rotate counterclockwise, the second roller gear 7 for being engaged with the first roller gear 8 and with the first Cylinder Gear
The the second driven imperfect non-circular gear 6 of switching for taking turns the connection of 7 coaxial powers turns clockwise, the first circle with rotate counterclockwise
The intermeshing output shaft roller gear 9 of stud wheel 8 then turns clockwise simultaneously with the output shaft 10 of power connector, when actively
Switch imperfect non-circular gear 5 to engage with the first driven imperfect non-circular gear 4 of switching and continue to have rotated 180 degree clockwise
Afterwards, second driving shaft 3 and the disposed thereon second imperfect roller gear 7 of non-circular gear 6 and second of driven switching, output shaft
10 and output shaft roller gear 9 disposed thereon turned clockwise once, the first power transmission shaft 2 and disposed thereon first from
Then rotate counterclockwise is once for the imperfect non-circular gear 4 of dynamic switching, the first roller gear 8.
Fig. 4, which is shown, actively switches the wink that imperfect non-circular gear 5 switches to the second driven imperfect non-circular gear 6 of switching
When state.
Output speed rotates from slow to fast when Fig. 5 shows the second driven switching imperfect 6 rotate counterclockwise of non-circular gear
During an instantaneous state.
Output speed at the uniform velocity, quickly rotates when Fig. 6 shows the second driven switching imperfect 6 rotate counterclockwise of non-circular gear
During an instantaneous state.
Output speed rotates from fast to slow when Fig. 7 shows the second driven switching imperfect 6 rotate counterclockwise of non-circular gear
During an instantaneous state.
Fig. 8, which is shown, actively switches the wink that imperfect non-circular gear 5 switches to the first driven imperfect non-circular gear 4 of switching
When state.
Output speed rotates from slow to fast when Fig. 9 shows the first driven switching imperfect 4 rotate counterclockwise of non-circular gear
During an instantaneous state.
Output speed at the uniform velocity, quickly revolves when Figure 10 shows the first driven switching imperfect 4 rotate counterclockwise of non-circular gear
An instantaneous state during turning.
Output speed rotates from fast to slow when Figure 11 shows the first driven switching imperfect 4 rotate counterclockwise of non-circular gear
During an instantaneous state.
Figure 12 shows that actively switch imperfect non-circular gear 5 cuts to the second driven imperfect non-circular gear 6 of switching again
The moment changed, the rotary motion of the reciprocal switching rotation direction of output new again start.
Figure 13 shows the reciprocal imperfect non-circular gear transmission of another switching of the present invention：When main frame does not need first
When the rotating speed of power transmission shaft 2 or second driving shaft 3 is changed, output shaft 10 and output shaft Cylinder Gear disposed thereon can be removed
Wheel 9, output shaft is directly used as using the first power transmission shaft 2 or second driving shaft 3, so still can reach the reciprocal switching rotation direction of output
The purpose of rotary motion.
Figure 14 shows the reciprocal imperfect non-circular gear transmission of another switching of the present invention：When main frame is needed described
When adding one or several output shafts again in the reciprocal imperfect non-circular gear transmission of switching, we can be further added by it is a set of or
A few set " output shaft 10 and the output shaft roller gears 9 " on output shaft 10, and make the output axial cylindrical newly increased
Gear 9 is intermeshed with original roller gear 7 of output shaft roller gear 9 or second in casing, form by the first power transmission shaft 2,
The output for the reciprocal switching direction of rotation of multiaxis multiposition output that second driving shaft 3, one or more output shafts 10 collectively constitute
Function.
2. actively switch the imperfect non-circular gear 4 of the driven switching of imperfect non-circular gear 5 and first, the second driven switching not
The specific implementation method of complete non-circular gear 6：
Fig. 2 and Fig. 3 also show actively switch the imperfect non-circular gear 4 of the driven switching of imperfect non-circular gear 5 and first,
Arrangement shape of the second driven imperfect non-circular gear 6 of switching in the reciprocal imperfect non-circular gear transmission of switching after assembling
State.
It is imperfect non-that Figure 15 and Figure 16 respectively illustrates the first imperfect non-circular gear 4 of driven switching, the second driven switching
Knucle-gear 6, the pitch curve form for actively switching imperfect non-circular gear 5, they are by orthodrome R1 and small arc-shaped R2 and position
What the speed-change area pitch curve between R1, R2 formed.
Figure 15 shows the first imperfect non-circular gear 4 of driven switching, the section of the second driven imperfect non-circular gear 6 of switching
35, radians of the speed-change area that curve 33 is 60 degree by two angles are that 37, one, the at the uniform velocity area radian of 180 degree is 60 degree
Formed without tooth form area 36.The section of the imperfect non-circular gear 4 of the first driven switching, the second driven imperfect non-circular gear 6 of switching
At the uniform velocity area 37 in curve 33 corresponds to small arc-shaped R2 regions positioned at there is parts of tooth.Simultaneously should be from the first dynamic deformation change gear
4th, in the pitch curve 33 of the second imperfect non-circular gear 6 of driven switching without the corresponding orthodrome R1 regions in tooth form area 36.According to upper
State the rotation of the first driven switching imperfect non-circular gear 4, the second driven imperfect non-circular gear 6 of switching of pitch curve completion of processing
Turn a gear teeth of the center line by the at the uniform velocity stage casing position of area 37, and the first driven imperfect non-circular gear 4, second of switching from
The number of teeth of the dynamic imperfect non-circular gear 6 of switching is odd number, and teeth groove number is then even number.
It by two radians is 60 degree of speed-change area that Figure 16, which shows that the pitch curve 28 for actively switching imperfect non-circular gear 5 is,
29th, 30, one, the at the uniform velocity area radian that a radian is 60 degree is that 180 degree is formed without tooth form area 31.This actively switches imperfect non-
At the uniform velocity area 30 in the pitch curve 28 of Knucle-gear 5 corresponds to orthodrome R1 regions positioned at there is parts of tooth.This actively switches not simultaneously
In the pitch curve 28 of complete non-circular gear 5 without the corresponding small arc-shaped R2 regions in tooth form area 31.According to above-mentioned pitch curve completion of processing
The rotation centerline for actively switching imperfect non-circular gear 5 by a teeth groove among at the uniform velocity area 30, and actively switch
The number of teeth of imperfect non-circular gear 5 is even number, and teeth groove number is odd number.
Figure 15 and Figure 16 are also illustrated：Actively switch the driven imperfect non-circular gear of switching of imperfect non-circular gear 5 and first
4th, the pitch curve form of the second driven imperfect non-circular gear 6 of switching is similar, but its each region parameter numerical value has not been
Exactly the same.Due to the reciprocal imperfect non-circular gear transmission load version of the switching and movement needs have it is various
Property, thus the driven imperfect non-circular gear 4, second of switching of the pitch curve 28 and first that actively switches imperfect non-circular gear 5 from
The pitch curve 33 of the dynamic imperfect non-circular gear 6 of switching also has diversity, at the same also just determine actively switch it is imperfect not rounded
The imperfect non-circular gear 4 of the driven switching of gear 5 and first, the second driven imperfect non-circular gear 6 of switching also have diversity.
Figure 15 and Figure 16, which is further illustrated, actively switches imperfect non-circular gear and the driven imperfect non-circular gear of switching
Design principle and method, it can be seen that actively switch the imperfect non-circular gear of the driven switching of imperfect non-circular gear 5 or the first
4th, the pivot " O " of the second driven imperfect non-circular gear 6 of switching, it is orthodrome R1 and small arc-shaped R2 geometric center.
Actively switch imperfect non-circular gear (5) and the first imperfect non-circular gear (4) of driven switching or second are driven cuts
When changing imperfect non-circular gear (6) engagement operating, when the imperfect non-circular gear engagement operation of driven switching is at the uniform velocity area, it is passed
Move than I coincidence formula：
I=R1/R2,
I interval is：Greatest measure is Imax=R1, minimum value Imin=1/R1；
The driven switching of pitch curve 32 or the first of the speed-change area 29 for actively switching imperfect non-circular gear 5 is imperfect non-
Knucle-gear 4, 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 is the pitch curve 28 or driven from the first dynamic deformation change gear 4, second for actively switching imperfect non-circular gear 5
Switch the radius in the orthodrome region of the pitch curve 33 of imperfect non-circular gear 6；
R2 is that the pitch curve 28 or the first for actively switching imperfect non-circular gear 5 driven switches imperfect non-circular gear 4, the
The radius in the small arc-shaped region of the pitch curve 33 of the two driven imperfect non-circular gears 6 of switching；
α is the 32, the first driven imperfect non-knuckle-tooth of switching of pitch curve of speed-change area 29 for actively switching imperfect non-circular gear 5
Any point on the pitch curve 34 of speed-change area 35 of the driven imperfect non-circular gear 6 of switching of wheel 4 and second is each complete at it
Corresponding angle in pitch curve coordinate system.
Figure 17 shows that the imperfect non-circular gear 5 that actively switches of completion of processing has 2 speed-change areas 29 on Digit Control Machine Tool,
The speed-change area 29 respectively has a deformation teeth change 39 close to the end without tooth form area 31, imperfect non-in the described first driven switching
Knucle-gear 4,2 speed-change areas 35 of the second driven imperfect non-circular gear 6 of switching respectively have one close to the end without tooth form area 36
Deform teeth change teeth groove 38.
Processing the technical requirements for the deformation teeth change 39 for actively switching imperfect non-circular gear 5 is：Deform teeth change 39
Transverse tooth thickness is 3 times of gear teeth transverse tooth thickness adjacent thereto, the whole depth of deformation teeth change 39 be 1.0 times of gear teeth whole depth adjacent thereto extremely
1.65 times, the addendum line line segment shape of deformation teeth change 39 is parallel with pitch curve line segment adjacent thereto, the deformation teeth change 39
Flank profil be still involute profile.
Process the deformation switching of the first driven switching imperfect non-circular gear 4, the second driven imperfect non-circular gear 6 of switching
The technical requirements of tooth teeth groove 38 are：The teeth groove thickness of deformation teeth change teeth groove 38 is 3 times of gear teeth teeth groove thickness adjacent thereto,
The teeth groove overall height of deformation teeth change teeth groove 38 is 1.0 times to 1.75 times of gear teeth teeth groove overall height adjacent thereto, deforms teeth change
The line segment shape of the dedendum line of teeth groove 38 is parallel with pitch curve line segment adjacent thereto.
After the above-mentioned imperfect non-circular gear group of switching is processed and assembled, you can the reciprocal imperfect non-knuckle-tooth of operating switching
Wheel-speed regulating change box, the reciprocal imperfect non-circular gear transmission of switching now is defeated on two direction of rotation clockwise and anticlockwise
Go out speed be also just provided with from slowly to it is fast, at the uniform velocity quick, near it is slow, again to the velocity variations feature of switching rotation direction.
3. the implementation of switching reciprocal imperfect non-circular gear transmission and its transmission mechanism
Back and forth imperfect non-circular gear transmission and its transmission mechanism are reciprocal imperfect by switching for switching shown in Figure 18
Non-circular gear transmission, with the power transmission shaft 2 of output shaft 10 or first, the power connector of second driving shaft 3 the 3rd power transmission shaft 21 and
3rd roller gear 13, the 4th power transmission shaft 15 and the 4th roller gear 14 disposed thereon disposed thereon and input shaft 1 are dynamic
The 5th power transmission shaft 16 and belt pulley 17 disposed thereon, the 6th input shaft 18 and belt pulley disposed thereon of power connection
19th, the belt 20 on belt pulley 17 and belt pulley 18 forms.
It is intermeshing relation that Figure 18, which also show the 3rd roller gear 13 and the 4th roller gear 14, the 3rd power transmission shaft
21 either end, the shaft end of shaft coupling and the power transmission shaft 2 of output shaft 10 or first, second driving shaft 3 can be used to implement dynamic
Power connects.The power transmission shaft 16 of input shaft 1 and the 5th is also to be connected with each other using shaft coupling.
Wherein, input shaft 1 can also appoint with sprocket wheel or all kinds of gear mechanisms or sprocket wheel, belt pulley, all kinds of gear mechanisms
Meaning combination realizes power connector by shaft coupling and the 5th power transmission shaft 16.
Figure 18, which further illustrates us, can use one or more sets " the 3rd roller gear 13, the 4th roller gear 14,
First power transmission shaft 2 or the second of four output shafts 15, the 3rd power transmission shaft 21 " and the reciprocal imperfect non-circular gear transmission of the switching
Power transmission shaft 3 or output shaft 10 or implement simultaneously with each shaft end of the first power transmission shaft 2, second driving shaft 3, output shaft 10 single shaft or
The power connector (as shown in phantom in Figure 16) of multiaxis, the method for its power connector is by one or more 3rd power transmission shafts 21
Shaft end passes by shaft coupling and the first power transmission shaft 2 or second driving shaft 3 or output shaft 10 or simultaneously with the first power transmission shaft 2, second
Moving axis 3, each shaft end of output shaft 10 are connected, you can realize that the rotary motion of the reciprocal switching rotation direction of single shaft output or multiaxis are more
The rotary motion of the reciprocal switching rotation direction of position output.The 3rd roller gear 13, the 4th roller gear 14 in the transmission mechanism are also
It can be substituted with any combination 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 the vertical oil-pumping machine ground
Existing transmission and changement, retain the frame 23 of existing vertical oil-pumping machine, sucker rod 24,
The parts such as belt 25, balance weight 26, roller 27, and install the switching back and forth imperfect non-circular gear change of the present invention
Fast case and its transmission mechanism, you can form a kind of novel vertical oil pumper with switching up-down stroke direction.
Specifically installation method is：
By the shaft end of the 5th power transmission shaft 16 in transmission mechanism with switching the defeated of reciprocal imperfect non-circular gear transmission
The shaft end for entering axle 1 is connected by shaft coupling, and the shaft end of the shaft end of the 6th power transmission shaft 18 and motor 22 is passed through into shaft coupling
Device is connected, you can makes to be located at the 5th power transmission shaft 16 and sprocket wheel or belt pulley or gear mechanism or chain on the 6th power transmission shaft 18
Wheel, belt pulley, any combination of gear mechanism run well, and realize the power input of vertical oil-pumping machine.
The output shaft (10) or the first power transmission shaft (2) of reciprocal imperfect non-circular gear transmission and its transmission mechanism will be switched
Or the shaft end of second driving shaft (3) is connected with the 3rd power transmission shaft 21 by shaft coupling, make on the 3rd power transmission shaft 21
The 3rd roller gear 13, the correct engagement of the 4th roller gear 14 on the 4th power transmission shaft 15, then by the 4th power transmission shaft
(15) shaft end is connected with the shaft end of the component drum 27 of former vertical oil-pumping machine by shaft coupling, you can realizes vertical take out
The power conduction of oil machine, and this novel vertical oil pumper is run well.
This novel vertical oil pumper for being mounted with switching reciprocal imperfect non-circular gear transmission and its transmission mechanism, by
The commutation function of the reciprocal imperfect non-circular gear transmission implementation up-down stroke of reliable switching is employed in its changement, is made
The conventional insecure technical barrier of vertical oil-pumping machine commutation function is overcome.
Claims (11)
1. the reciprocal imperfect non-circular gear transmission of one kind switching, including input shaft (1) and the master on the input shaft (1)
Dynamic switching imperfect non-circular gear (5), the first power transmission shaft (2) and the first driven switching on first power transmission shaft (2)
Imperfect non-circular gear (4) and the first roller gear (8), second driving shaft (3) and on the second driving shaft (3)
Two imperfect non-circular gear (6) and the second roller gears (7) of driven switching, casing (11) and case lid (12), described first is driven
Switch imperfect non-circular gear (4), the second imperfect non-circular gear (6) of driven switching positioned at it is described actively switch it is imperfect not rounded
The both sides of gear (5) and side by side engagement installation, the first imperfect non-circular gear (4) of driven switching, the second driven switching are imperfect
The rotary speed change of non-circular gear (6) be from slowly to it is fast, at the uniform velocity quick, near it is slow, again to switching rotation direction,
It is characterized in that：
Actively switch imperfect non-circular gear (5) to turn clockwise and start and the second driven imperfect non-circular gear (6) of switching
When thering is the parts of tooth to enter intermeshing, the second imperfect non-circular gear (6) of driven switching be connected with coaxial power second
Roller gear (7) starts to make rotate counterclockwise, the first roller gear (8) for being engaged with the second roller gear (7) and with first
The first driven imperfect non-circular gear (4) of switching of roller gear (8) coaxial power connection turns clockwise, when active switches
Imperfect non-circular gear (5) engaged with the second imperfect non-circular gear (6) of driven switching and turned clockwise 180 degree when, the
Two power transmission shafts (3) and the disposed thereon second imperfect non-circular gear (6) of driven switching and the second roller gear (7) then inverse time
Pin have rotated once, the first power transmission shaft (2) and the disposed thereon first imperfect non-circular gear (4) of driven switching, the first circle
Stud wheel (8) has then turned clockwise once；
Continue to turn clockwise and start and the first imperfect non-knuckle-tooth of driven switching when actively switching imperfect non-circular gear (5)
When having parts of tooth entrance intermeshing of wheel (4), what the first driven imperfect non-circular gear (4) of switching was connected with coaxial power
First roller gear (8) makees rotate counterclockwise, the second roller gear (7) for being engaged with the first roller gear (8) and with
The second imperfect non-circular gear (6) of driven switching of two roller gears (7) coaxial power connection turns clockwise, when actively cutting
Imperfect non-circular gear (5) is changed to engage with the first driven imperfect non-circular gear (4) of switching and continue to have rotated 180 degree clockwise
When, second driving shaft (3) and the disposed thereon second imperfect non-circular gear (6) of driven switching and the second roller gear (7)
Turn clockwise once, the first power transmission shaft (2) and the disposed thereon first imperfect non-circular gear (4) of driven switching, the
Then rotate counterclockwise is once for one roller gear (8).
2. the reciprocal imperfect non-circular gear transmission of switching according to claim 1, it is characterised in that it also has output
Axle 10 and the output shaft roller gear (9) on the output shaft (10), the output shaft roller gear (9) and described first
Roller gear (8) engages with the second roller gear (7), or is justified using 2 groups of output shafts (10) and output shaft disposed thereon
Stud wheel (9) engages with the first roller gear (8) and the second roller gear (7) respectively.
3. the reciprocal imperfect non-circular gear transmission of switching according to claim 1, it is characterised in that：
The pitch curve (28) for actively switching imperfect non-circular gear (5) by two radians be 60 degree speed-change area (29), one
At the uniform velocity area (30) that individual radian is 60 degree, a radian are that 180 degree is formed without tooth form area (31)；It is described actively switch it is imperfect non-
At the uniform velocity area (30) in the pitch curve (28) of Knucle-gear (5) corresponds to orthodrome region positioned at there is parts of tooth；The active switching
In the pitch curve (28) of imperfect non-circular gear (5) small arc-shaped region is corresponded to without tooth form area (31)；Actively switch imperfect non-
The center line of Knucle-gear (5) passes through a teeth groove among at the uniform velocity area (30)；The imperfect non-circular gear (5) of actively switching
The number of teeth is even number, and teeth groove number is odd number,
The first driven pitch curve (33) for switching imperfect non-circular gear (4) and the second driven imperfect non-circular gear (6) of switching
It is 60 degree anodontia by the speed-change area (35) of two 60 degree of angles, the at the uniform velocity area (37) that a radian is 180 degree, radian
Shape area (36) is formed；The first imperfect non-circular gear (4) of driven switching and second driven switches imperfect non-circular gear (6)
Pitch curve (33) at the uniform velocity area (37) positioned at there is a parts of tooth, corresponding small arc-shaped region；The first driven switching is endless
It is corresponding without tooth form area (36) in the pitch curve (33) of whole non-circular gear (4) and the second driven imperfect non-circular gear (6) of switching
Orthodrome region；The first driven rotation for switching imperfect non-circular gear (4) and the second driven imperfect non-circular gear (6) of switching
The gear teeth that center line passes through at the uniform velocity area (37) stage casing position；The first imperfect non-circular gear (4) of driven switching and the
The number of teeth of the two driven imperfect non-circular gears (6) of switching is odd number, and teeth groove number is then even number,
It is described actively to switch imperfect non-circular gear (5), the first imperfect non-circular gear (4) of driven switching and the second driven switching
The pivot " 0 " of imperfect non-circular gear (6), it is the geometric center of orthodrome and small arc-shaped,
Actively switch imperfect non-circular gear (5) and the first imperfect non-circular gear (4) of driven switching or the second driven switching not
During complete non-circular gear (6) engagement operating, when the imperfect non-circular gear engagement operation of driven switching is at the uniform velocity area, its gearratio
I coincidence formulas：
I=R1/R2,
I interval is：Greatest measure is Imax=R1：Minimum value is Imin=1/R1；
The pitch curve (32) for actively switching imperfect non-circular gear (5) speed-change area (29), the first driven switching are imperfect non-
The mathematic(al) representation F of Knucle-gear (4) and the pitch curve (34) of the second driven imperfect non-circular gear (6) speed-change area (35) of switching
(α) equal coincidence formula：
F (α)=R1*sin (α)/R2；
Wherein：
R1 be actively switch imperfect non-circular gear (5) pitch curve (28), first it is driven switch imperfect non-circular gear (4) and
The radius in the orthodrome region of the pitch curve (33) of the second driven imperfect non-circular gear (6) of switching；
R2 be actively switch imperfect non-circular gear (5) pitch curve (28), first it is driven switch imperfect non-circular gear (4) and
The radius in the small arc-shaped region of the pitch curve (33) of the second driven imperfect non-circular gear (6) of switching；
α be actively switch imperfect non-circular gear (5) speed-change area (29) pitch curve (32), first it is driven switch it is imperfect not rounded
Any point on gear (4) and speed-change area (35) pitch curve (34) of the second driven imperfect non-circular gear (6) of switching is at it
Each corresponding angle in complete pitch curve coordinate system.
4. the reciprocal imperfect non-circular gear transmission of switching according to one of claim 1-3, it is characterised in that described
2 speed-change areas (29) for actively switching imperfect non-circular gear (5) respectively have a deformation to cut close to the end without tooth form area (31)
Change tooth (39)；Switch imperfect non-circular gear (6) the described first imperfect non-circular gear (4) of driven switching and second are driven
2 speed-change areas (35) respectively have a deformation teeth change teeth groove (38) close to the end without tooth form area (36).
5. the reciprocal imperfect non-circular gear transmission of switching according to claim 4, it is characterised in that the active switching
The transverse tooth thickness of the deformation teeth change (39) of imperfect non-circular gear (5) is 3 times of gear teeth transverse tooth thickness adjacent thereto, deformation teeth change (39)
Whole depth be 1.0 times to 1.65 times of gear teeth whole depth adjacent thereto, the addendum line line segment shape of deformation teeth change (39) and
Pitch curve line segment adjacent thereto is parallel, and the flank profil of the deformation teeth change (39) is still involute profile.
6. the reciprocal imperfect non-circular gear transmission of switching according to claim 5, it is characterised in that：Described first is driven
Switch the tooth of imperfect non-circular gear (4) and the deformation teeth change teeth groove (38) of the second driven imperfect non-circular gear (6) of switching
Slot thickness is 3 times of gear teeth teeth groove thickness adjacent thereto, and the gullet depth of deformation teeth change teeth groove (38) is adjacent thereto
1.0 times to 1.75 times of gear teeth gullet depth, the line segment shape of dedendum line of deformation teeth change teeth groove (38) and adjacent thereto
Pitch curve line segment is parallel.
7. a kind of transmission mechanism, it is characterised in that the switching that the transmission mechanism is included as described in one of claim 1-6 is reciprocal not
Complete non-circular gear transmission.
8. transmission mechanism according to claim 7, it is characterised in that the switching in the transmission mechanism is reciprocal imperfect not rounded
The input shaft (1) of speed-changing gear box can pass through shaft coupling with the combination of one or more of sprocket wheel, belt pulley, all kinds of gear mechanisms
Implement power input after device connection.
9. the transmission mechanism according to claim 7 or 8, it is characterised in that the reciprocal imperfect non-circular gear of switching becomes
The output shaft (10) of fast case passes through shaft coupling and the 3rd power transmission shaft (21) and the 3rd roller gear (13) disposed thereon, the 4th
Power transmission shaft (15) and the 4th roller gear (14) disposed thereon connection, so as to realize power output.
10. the transmission mechanism according to claim 7 or 8, it is characterised in that the reciprocal imperfect non-circular gear of switching
The output shaft (10) of gearbox by shaft coupling can with one of sprocket system, belt train, Cylinder Gear train or combining connection, from
And realize power output.
11. a kind of vertical oil-pumping machine, it is characterised in that the changement of its sucker rod up and down reciprocatingly is mounted with such as claim
Transmission mechanism described in one of 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 |
Applications Claiming Priority (1)
| 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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104121338A CN104121338A (en) | 2014-10-29 |
| CN104121338B true CN104121338B (en) | 2018-04-10 |
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| CN201410093553.6A Expired - Fee Related CN104121338B (en) | 2014-03-14 | 2014-03-14 | One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism |
Country Status (2)
| Country | Link |
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| CN (1) | CN104121338B (en) |
| WO (1) | WO2015135400A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104121338B (en) * | 2014-03-14 | 2018-04-10 | 董剑 | One kind switching reciprocal imperfect non-circular gear transmission and its transmission mechanism |
| 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 |
| CN110030360B (en) * | 2019-04-11 | 2021-07-06 | 中国矿业大学 | Gear reversing mechanism and design method of gear pair thereof |
| 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 |
| CN110425377B (en) * | 2019-08-16 | 2020-08-11 | 燕山大学 | Bidirectional movement's inertial pipeline robot |
| CN110879910B (en) * | 2019-11-21 | 2023-05-26 | 燕山大学 | Closed non-circular gear pair with transmission ratio of Fourier series |
| CN112833141B (en) * | 2020-08-26 | 2023-05-12 | 辽宁石油化工大学 | Elliptic planetary gear train type spring tooth roller peanut pickup device |
| CN113693811B (en) * | 2021-08-09 | 2023-09-29 | 台州市驰丰电气科技有限公司 | Upper abdomen warming therapy device for clinical nursing of department of cardiology |
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| US3955887A (en) * | 1973-05-28 | 1976-05-11 | Canon Kabushiki Kaisha | Motion picture camera |
| 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 |
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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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| RU2082051C1 (en) * | 1994-07-20 | 1997-06-20 | Евгений Петрович Абрамцев | Device for conversion of rotary motion into compound motion |
| JPH09229157A (en) * | 1996-02-28 | 1997-09-02 | Rhythm Watch Co Ltd | Reciprocative rotation mechanism |
| 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 |
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- 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
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3955887A (en) * | 1973-05-28 | 1976-05-11 | Canon Kabushiki Kaisha | Motion picture camera |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104121338A (en) | 2014-10-29 |
| WO2015135400A1 (en) | 2015-09-17 |
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