CN101225876A - Double-moment action gear train method and device - Google Patents
Double-moment action gear train method and device Download PDFInfo
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- CN101225876A CN101225876A CNA2008100141748A CN200810014174A CN101225876A CN 101225876 A CN101225876 A CN 101225876A CN A2008100141748 A CNA2008100141748 A CN A2008100141748A CN 200810014174 A CN200810014174 A CN 200810014174A CN 101225876 A CN101225876 A CN 101225876A
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Abstract
The invention relates to a method and device for double torque action gear trains, belonging to mechanical transmission, comprising a meshing differential gear train and a double torque transmission device. Under the constant power, a power supply torque bends the shaft through a lever which is pivoted on a universal transmission bearing pedestal, enabling the central input gear to be equipped with an instantaneous input torque and a power supply torque. The mutual balancing action between the action force by the instantaneous input torque on the planetary gear and the action force by the outside load on the planetary gear enables the central output gear to turn around and work outwards. The central input gear keeps the angular velocity of the power supply torque. The transmission ratio of the double torque action gear trains is the product of the transmission ratio of the meshing differential gear train, the action radius ratio and the lever ratio. The double-torque continuously variator produced by the double torque action gear train achieves continuously variable speed change through regulating the lever ratio. The method and device for double torque action gear trains has the advantages of saving steel and energy, having low noise, protecting environment, and being applicable for various mechanical devices such as automobiles and various mechanical equipment as a speed change device.
Description
Technical field
The present invention relates to the method and the device thereof of mechanically operated a kind of double-moment action gear train.
Background technique
The existing mechanical drive technology by the moment of torsion and the speed of the power source of certain power output, generally all is moment of torsion is amplified or to dwindle through speed changer, to obtain output speeds different under the permanent power and moment of torsion; Power, the relation of moment of torsion and speed are that power equals the product of moment of torsion and transmission angle speed.Under permanent power, change the speed and the moment of torsion of output, will change the radius of drive wheel in the driving mechanism, as retarder, be exactly by changing the radius of each gear in the transmission process, in the mode of engagement, make that the speed after the output reduces, moment of torsion increases; For belt transmission, be by changing the radius of belt pulley each other equally, in the mode of friction, change the speed and the moment of torsion of output; Equally, chain-driven also is by changing the radius of sprocket wheel each other, in the mode of engagement, changes the speed and the moment of torsion of output.More than several under permanent power, the mechanical transmission mode of speed and moment of torsion all is by changing in the driving mechanism radius of drive wheel each other, change the velocity ratio of system, in their reducing gear, all be to do work each other, with transmitting torque and speed by the mode of moment of torsion.
This by the radius transport velocity of drive wheel and the mode of moment of torsion in the change mechanical transmission mechanism, the shortcoming that exists is: for gear reducer with fixed drive ratio or gear stepless speed variator, it all is the purpose that reaches speed change by the radius that changes driving gear, because gear transmission is the engagement driving between a kind of gear, the a pair of gear ratio of every increase, the transmission efficiency of gear reducer system will lower once, gear-driven each grade all needs the bearing of carrier gear, and the casing of carrier bearing, will expend the certain raw material resources and the energy, the material of gear generally all is to be made by the alloy that adds rare metal, and gear surface also need quench, roll flute, for this reason, wasted manpower, the resource and the energy, in order to reduce wear and to guarantee transmission efficiency, gear transmission must have the pond oil lubrication, has produced the leakage waste of lubricant oil thus and pollutes, between gear during transmission, influence because of engagement transmission and machining accuracy presents transmission noise in various degree.For the friction driving or the friction stepless gearbox of belt pulley, be to change the radius of friction wheel each other equally, because the generation of friction, its transmission efficiency is low.
Summary of the invention
The method and the device thereof that the objective of the invention is a kind of double-moment action gear train, the method of described double-moment action gear train, under the permanent power, in the double-moment action gear train that constitutes by engagement differential gear train and two square transmission devices, the lever cambered axle is done fulcrum with the universal drive shaft bearing, and do rotation motion thereon, the power source moment of torsion passes through the driving wheel wobbler action on the driving arm of lever cambered axle, produce an instantaneous input moment of flexure, instantaneous input moment of flexure is by the lever cambered axle, resistance arm output terminal at the lever cambered axle, form an instantaneous output moment of flexure, the direction of instantaneous input moment of flexure and instantaneous output moment of flexure is always vertical mutually with the direction of power source moment of torsion, instantaneous output moment of flexure acts on the input central gear by driven wheel, produce one and the always orthogonal instantaneous input torque of its direction, the input end of input central gear exists an instantaneous input torque and a moment of torsion identical with the power source moment of torsion, active force that instantaneous input torque produces planet wheel and external load are to the mutual balanced action of the active force of planet wheel, make the output center wheel do rotation motion, externally acting, have on the engagement differential gear train of two degrees of freedom, the angular velocity of input central gear is identical with power source moment of torsion angular velocity, the angular velocity of output center wheel is that the angular velocity by instantaneous input torque forms, the angular velocity of instantaneous input torque is formed by instantaneous output moment of flexure angular velocity and power source moment of torsion angular velocity, the velocity ratio of double-moment action gear train is the velocity ratio of engagement differential gear train, the product of action radius ratio and bar ratio.
A kind of pair of square stepless speed changer that the method for a kind of double-moment action gear train of described usefulness forms, constitute by engagement differential gear train and two square transmission device, described engagement differential gear train is by the input central gear, planet wheel, the output center wheel, pivoted arm constitutes, input central gear and input shaft become one, input shaft is installed on the bearing support, the output center wheel becomes one with output shaft, output shaft is installed on the bearing support, pivoted arm one end of axle and bearing is installed, coaxial line with input central gear and output center wheel is an axis, be axis perhaps with input central gear axis, be axis perhaps with the output center wheel axis, relatively rotate with input central gear and output center wheel, the other end of pivoted arm is equipped with axle, bearing and planet wheel, input central gear and planet wheel engagement driving, planet wheel and output center wheel engagement driving, the engagement differential gear train has two degrees of freedom, described pair of square transmission device is by driving wheel, live axle, the lever cambered axle, the universal drive shaft bearing, resistance shaft, stepless speed-regulating device, driven wheel constitutes, the lever cambered axle is by driving arm, jack shaft, resistance arm constitutes, the lever cambered axle is installed on the universal drive shaft bearing of fixedlying connected with the external world, resistance arm is installed together by resistance shaft and driven wheel, driving arm is provided with live axle, live axle is connected with stepless speed-regulating device by driving wheel, stepless speed-regulating device and live axle can driving arm axially on and driving wheel axially on axially move back and forth, perhaps opposite, driving arm is installed together by live axle and driving wheel, resistance shaft is set on the resistance arm, resistance shaft is connected with stepless speed-regulating device by driven wheel, stepless speed-regulating device and resistance shaft can resistance arm axially on and driven wheel axially on axially move back and forth, driving wheel links together with the input shaft that is installed on the bearing support, the rotational axis of lever cambered axle is by the central point of universal drive shaft bearing, and driven wheel links together with the input central gear by the input shaft or the input transmission device of input central gear.In the described pair of square transmission device, the live axle that setting and driving arm and driving wheel are installed together is to the invariant position of universal drive shaft bearing central point, the resistance shaft that setting and resistance arm and driven wheel are installed together is to the invariant position of the central point of universal drive shaft bearing, and two square stepless speed changers can become a kind of pair of square speed reducer.Described engagement differential gear train can be, and the gear differential gear train is with differential gear train synchronously, the chain differential gear train.With the setting of can connecting of described pair of square transmission device, perhaps described pair of square transmission device can be arranged in parallel.Described engagement differential gear train can be arranged in parallel, and described pair of square transmission device linked together by input shaft or input transmission device and input central gear in the engagement differential gear train that is arranged in parallel.
A kind of pair of square transmission device in the double-moment action gear train, by driving wheel, live axle, the lever cambered axle, the universal drive shaft bearing, resistance shaft, driven wheel constitutes, it is characterized in that the lever cambered axle is by driving arm, jack shaft, resistance arm constitutes, the lever cambered axle is installed on the universal drive shaft bearing of fixedlying connected with the external world, and driven wheel links together with the output shaft that is installed on the bearing support, and resistance arm is installed together by resistance shaft and driven wheel, driving arm is installed together by live axle and driving wheel, driving wheel links together with the input shaft that is installed on the bearing support, and the rotational axis of lever cambered axle passes through the central point of universal drive shaft bearing, and overlaps with the coaxial line of driving wheel and driven wheel.
A kind of universal drive shaft bearing in the double-moment action gear train, by fork ring in universal, universal outer fork ring, the external support ring, rolling bearing constitutes, it is characterized in that, universal interior fork encircles radially, and two ends are provided with two fork shafts, two fork shaft coaxial lines, universal outer fork encircles radially, and two ends are provided with two fork shafts, two fork shaft coaxial lines, on fork encircles outside universal, be provided with two axis holes with the orthogonal radial line of the axis of two fork shafts two ends, the axis coaxle of two axis holes also intersects vertically mutually with the axis of two fork shafts, external support ring radially two ends is provided with two axis holes, the axis coaxle of two axis holes, rolling bearing single-row or be fixedly mounted on side by side universal on the center hole of fork ring, two fork shafts of fork ring are installed on two axis holes of universal outer fork ring in universal, two fork shafts of universal outer fork ring are installed on two axis holes of external support ring, the external support ring and the external world are fixedly connected, the coaxial line of the coaxial line of two fork shafts of fork ring and two fork shafts of universal outer fork ring intersects vertically mutually in universal, and its crosspoint is the central point of universal drive shaft bearing.Between the axis hole that the fork shaft of described universal interior fork ring and universal outer fork encircle, rolling bearing can be installed, and use the positioning device axially locating, between the fork shaft of described universal outer fork ring and the axis hole of external support ring, rolling bearing can be installed, and use the positioning device axially locating.Described a kind of universal drive shaft bearing can be a kind of bearing support that holds with expansion mandrel.
The present invention can more effective saving steel on making than existing stepless speed changer and speed reducer, save the energy, low noise during operation, environmental protection, middle gear as the outside acting of power source moment of torsion, can be widely used in the various mechanical devices, as automobile, and various mechanized equipments etc.
Description of drawings
Fig. 1 is the plan view of a kind of pair of square gear stepless speed variator of the present invention.
Fig. 2 is that the A-A of Fig. 1 of the present invention is to view.
Fig. 3 is the stressed schematic diagram of solid of the present invention.
Fig. 4 is that a kind of pair of square of the present invention is synchronously with the plan view of stepless speed changer.
Fig. 5 is the plan view of a kind of pair of square chain stepless speed changer of the present invention.
Fig. 6 is the kind of drive schematic representation of a kind of specific embodiment of the present invention.
Fig. 7 is the kind of drive schematic representation of a kind of specific embodiment of the present invention.
Fig. 8 is the sectional view of a kind of universal drive shaft bearing of the present invention.
Embodiment
With reference to Fig. 1, Fig. 2 is the concrete structure of a kind of pair of square gear stepless speed variator of the present invention, it is made of gear differential gear train 1 and two square transmission device 2 two-part, and the formation of its middle gear differential gear train 1 is input central gear 3, planetary pinion 5, output center gear 4, pivoted arm 27; One end of pivoted arm 27 is provided with rotatingshaft 29, bearing 28 and bearing 35 have been installed in rotatingshaft 29 two ends, bearing 28 is installed in the inboard center of output center gear 4, bearing 35 is installed in the center, upper end of input central gear 3, and pivoted arm 27 is rotated relative to input central gear 3 and output center gear 4; The other end of pivoted arm 27 is provided with stationary axle 30, and an end of stationary axle 30 is equipped with bearing 31, and planetary pinion 5 is installed on the bearing 31, and bearing 31 is fixed on the stationary axle 30 by gland 32 and retaining screw 33; The lower end input shaft of input central gear 3 is input shafts of this gear differential gear train 1, and is installed on the bearing 6, and bearing 6 is installed on the bearing support; The lower end of output center gear 4 is provided with end cap 34, and the upper end of output center gear 4 is output shafts of this gear differential gear train 1, and is installed on the bearing 36, and bearing 36 is installed on the bearing support; Input central gear 3 is coaxial with output center gear 4, input central gear 3 and planetary pinion 5 outer gearings, planetary pinion 5 and output center gear 4 interior engagements.For the axis of input central gear 3 and the orthogonal gear differential gear train of axis of output center gear 4, pivoted arm 27 is an axis with the axis of input central gear 3, perhaps the axis with output center gear 4 is an axis, relatively rotates with input central gear gear 3 and output center gear 4.
The formation of two square transmission devices 2 is, the lower end input shaft of driving wheel 25 is input shafts of this pair square gear stepless speed variator, and is installed on the bearing 26, and bearing 26 is installed on the bearing support; Corresponding with driving wheel 25 is driven wheel 7, and their axis coaxle, driven wheel 7 are assemblied on the lower end input shaft of input central gear 3 of gear differential gear train 1; Between driving wheel 25 and driven wheel 7, be provided with universal drive shaft bearing 37 and lever cambered axle 39; Universal drive shaft bearing 37 is by fork ring 12 in universal, universal outer fork ring 13, external support ring 14, bearing gland 40, and rolling bearing 11 constitutes, in universal on the fork ring 12 radially two ends be provided with two fork shafts 19, the axis coaxle of two fork shafts 19 and with universal in the radial line of fork ring 12 overlap, on the universal outer fork ring 13 radially two ends be provided with two fork shafts 16, the axis coaxle of two fork shafts 16 also overlaps with the radial line of universal outer fork ring 13, fork encircles on 13 outside universal, be provided with two axis holes 42 with the orthogonal radial line of the axis of two fork shafts 16 two ends, the axis coaxle of two axis holes 42 also intersects vertically mutually with the axis of two fork shafts 16, on the external support ring 14 radially two ends be provided with the axis coaxle of 43, two axis holes 43 of two axis holes and overlap with the radial line of external support ring 14, rolling bearing 11 is installed on the center hole of universal interior fork ring 12, fixing by bearing gland 40, in order to improve bearing capacity, can universal in, pitch installation rolling bearing 11 arranged side by side on the center hole of ring 12; Two fork shafts 19 of fork ring 12 are installed on two axis holes 42 of universal outer fork ring 13 in universal, two fork shafts 16 of universal outer fork ring 13 are installed on two axis holes 43 of external support ring 14, external support ring 14 is fixedly connected with the external world, in order to reduce friction and wear, improve transmission efficiency, in universal the fork shaft 19 of fork ring 12 with universal outer pitch to encircle between 13 the axis hole 42 needle bearing 20 is installed, and with back-up ring 17 axially locating, equally, outside universal, between the axis hole 43 of the fork shaft 16 of fork ring 13 and external support ring 14 needle bearing 15 is installed, and with back-up ring 17 axially locating, in order to improve lubricating ability, can be on fork shaft 16 and fork shaft 19 axle center machining hole by fork ring 13 outside universal and universal in fork ring 12 communicate with the external world, with convenient adding lubricant oil; The coaxial line of two fork shafts 16 on the coaxial line of two fork shafts 19 in universal on the fork ring 12 and the universal outer fork ring 13 intersects vertically mutually, its crosspoint is the central point of universal drive shaft bearing 37, also be the fulcrum of lever cambered axle 39, the coaxial line of driving wheel 25 and driven wheel 7 is by the central point of universal drive shaft bearing 37;
Lever cambered axle 39 is by driving arm axle 38, resistance arm axle 8, jack shaft 10 constitutes, jack shaft 10 is assemblied on the rolling bearing 11, the coaxial line of the axis of jack shaft 10 and driving wheel 25 and driven wheel 7 intersects, its crosspoint overlaps with the central point of universal drive shaft bearing 37, and the upper end of jack shaft 10 fixedly is assemblied in the lower end of resistance arm axle 8, and the lower end of jack shaft 10 fixedly is assemblied in the upper end that drives arm axle 38; Drive arm axle 38 and be provided with live axle 23, live axle 23 1 ends are installed on the dovetail groove 18 that drives arm axle 38, and the other end is installed on the stepless speed-regulating device 24 by the regulating tank 41 on the driving wheel 25; Resistance arm axle 8 is provided with resistance shaft 9, and the other end of resistance shaft 9 is installed on the driven wheel 7, and the rotational axis of lever cambered axle 39 overlaps with the coaxial line of driving wheel 25 and driven wheel 7; It is a kind of reinforced arm axles that this example drives arm axle 38, and it can prevent to rotate imbalance and the seismism that causes because of eccentric drive, and resistance arm axle 8 also is a kind of reinforced arm axle; In order to strengthen the bearing capacity of rolling bearing 11, the bearing inner race of jack shaft 10 and rolling bearing 11 can be made into an integral body.
The course of action of two square transmission devices 2, on universal drive shaft bearing 37, driving wheel 25 drives arm axle 38 by live axle 23 eccentric drive and makes 39 rotation motions of lever cambered axle, being installed in the axis of the jack shaft 10 on the rolling bearing 11 and the rotational axis of lever cambered axle 39 intersects, the axis of the both sides jack shaft 10 of its crosspoint rotates around the rotational axis of lever cambered axle 39, fork ring 12 swung back and forth around the coaxial line any directions of two fork shafts 19 in jack shaft 10 drives were universal, two universal outer forks of fork shaft 19 drives encircle the 13 coaxial line any directions around two fork shafts 16 and swing back and forth, external support ring 14 by two fork shafts 16 of two axis holes, 43 carryings maintains static with the external world, lever cambered axle 39 is done fulcrum by universal drive shaft bearing 37, realize lever cambered axle 39 around its rotational axis rotation motion, the resistance arm axle 8 on the lever cambered axle 39 drives driven wheel 7 rotation motions by resistance shaft 9.
With reference to Fig. 3, be the stressed schematic diagram of solid of the present invention, in the transmission system that constitutes by gear differential gear train 1 and two square transmission device 2, axis X
1-X
1Be the rotational axis of lever cambered axle 39 and the coaxial line of input central gear 3 and output center gear 4, on lever cambered axle 39, drive the effect axis of arm axle 38, the effect axis of resistance arm axle 8 and the axis of jack shaft 10 are in one plane, live axle 23 wobbler actions are on the effect axis that drives arm axle 38, and active force is F
1, directed force F
1With axis X
1-X
1The gyroscopic action radius be r
1, the moment of torsion of generation is M
1, being called the power source moment of torsion again, output power is P
1The angle of revolution speed of driving wheel 25 is ω
1, be called power source moment of torsion angular velocity
M
1＝F
1×r
1 (1-1)
P
1＝F
1×r
1×ω
1 (1-2)
Lever cambered axle 39 is done fulcrum with universal drive shaft bearing 37, and does rotation motion thereon, when the directed force F of live axle 23
1Wobbler action is on driving arm axle 38 time, and lever cambered axle 39 is around axis X
2-X
2An instantaneous input moment M and instantaneous input moment of flexure angular velocity omega are arranged at an arbitrary position, axis X
2-X
2With axis X
1-X
1Intersect vertically mutually, its crosspoint is the central point of universal drive shaft bearing 37, the direction of instantaneous input moment M and moment of torsion M
1Direction always mutually vertical
M＝F
1×L
1 (1-3)
L
1It is directed force F
1To axis X
2-X
2Distance;
Instantaneous input moment M makes that the active force of resistance arm axle 8 wobbler actions on resistance shaft 9 is F
2, directed force F
2To axis X
2-X
2Distance be L
2, with directed force F
2The reaction force of opposite sign but equal magnitude is a directed force F
2a
F
2＝-F
2a
According to lever principle: F
2a* L
2=F
1* L
1(1-4)
F
2＝-F
1×L
1/L
2
Directed force F
2aRelative axis X
2-X
2Produce an instantaneous output moment M a, its angular velocity is instantaneous output moment of flexure angular velocity omega a.ω a and ω opposite sign but equal magnitude,
On lever cambered axle 39, directed force F
2As use one and M are arranged
1The identical moment of torsion M of size direction
2, its angle of revolution speed omega
2, ω
2Also be the angular velocity of input central gear 3, ω
2With ω
1The equal and opposite in direction direction is identical, moment of torsion M
2The direction of direction and instantaneous output moment M a always vertical mutually; Directed force F
2Around axis X
1-X
1Produce an instantaneous input torque M
2A, its revolution instantaneous angular velocity is ω
2a, instantaneous input torque M
2The direction of a is always vertical mutually with the direction of instantaneous output moment M a
M
2a＝F
2×r
2 (1-5)
r
2Be directed force F
2With axis X
1-X
1The gyroscopic action radius; Instantaneous input torque M
2A acts on the input central gear 3 by driven wheel 7.
The output center gear 4 externally moment of torsion of output is M
4, angular velocity is ω
4, have the directed force F of a pair of opposite sign but equal magnitude between output center gear 4 and the planetary pinion 5
4A and F
4, F
4A is the active force of external load, by F
4To axis X
1-X
1Action radius be r
4,
M
4Reaction torque be M
4A,
M
4＝F
4×r
4 (1-6)
M
4a＝F
4a×r
4
M
4A is F by the active force of 5 pairs of inputs of planetary pinion central gear 3
3, F
3With F
4The a opposite sign but equal magnitude, directed force F
3To axis X
1-X
1Action radius be r
3, moment of torsion is M
3, moment of torsion M
3Reaction torque be M
3A, M
3A is the action torque of 3 pairs of planetary pinions 5 of input central gear, directed force F
3A and F
3Opposite sign but equal magnitude, F
3A is by planetary pinion 5 and F
4A equal and opposite in direction direction is identical
M
3＝F
3×r
3
M
3a＝-F
3×r
3 (1-7)
By formula (1-4) and formula (1-1), work as L
1Be equal to or less than L
2The time
F
2＝-F
1×r
1/r
2
M
2＝M
2a
At this moment, by moment of torsion M
2Perhaps instantaneous input torque M
2A outwards acts on;
For gear differential gear train 1, work as L
1Be equal to or less than L
2, M
3Greater than M
2, M
3Greater than M
2During a, output center gear 4 maintains static, and gear differential gear train 1 is a planetary gear train, does not externally do work; Work as L
1Be equal to or less than L
2, M
3Equal M
2, M
3Equal M
2During a, gear differential gear train 1 has two degrees of freedom, and gear differential gear train 1 is a differential gear train at this moment, by moment of torsion M
2Perhaps instantaneous input torque M
2A externally does work, and the velocity ratio of gear differential gear train 1 is
Work as L
1Greater than L
2, M
3Greater than M
2, M
2A is greater than M
2, M
3Equal M
2During a, gear differential gear train 1 presents a kind of novel motion state:
On gear differential gear train 1, input central gear 3 is being subjected to the moment of torsion M of a pair of opposite sign but equal magnitude
3With instantaneous input torque M
2In the time of a balanced action, still keep the angle of revolution speed omega
2Do rotation motion, instantaneous input torque M
2The directed force F that a produces planetary pinion 5
3A and external load are to the directed force F of planetary pinion 5
4aBalanced action mutually makes output center gear 4 do rotation motion, externally acting.This pair of square transmission device 2 combines the novel motion mode that produces with gear differential gear train 1, be called double-moment action gear train.The motion state of double-moment action gear train comprises the motion state of aforesaid planetary gear train and differential gear train.
By instantaneous input moment M, the instantaneous power of instantaneous output moment M a output keeps equating with output power of power source, by formula (1-2) and formula (1-4)
F
1×r
1×ω
1＝F
2a×L
2×ωa
ωa＝ω
1×r
1/L
1
The instantaneous power of instantaneous output moment M a output keeps and instantaneous input torque M
2The instantaneous output of a equates, by formula (1-5)
F
2a×L
2×ωa＝F
2×r
2×ω
2a
ω
2a＝ω
1×r
1×L
2/r
2×L
1
Instantaneous angular velocity ω
2aAlso be the instantaneous angular velocity of input central gear 3, by formula (1-6) and formula (1-7)
F
4×r
4×ω
4＝-F
3×r
3×ω
2a
F
4With F
3The equal and opposite in direction direction is identical
ω
4＝-ω
1×r
1×r
3×L
2/r
2×r
4×L
1
ω
4With ω
1Gyratory directions opposite, establish
Will
Be called the action radius ratio,
Be called the bar ratio,
With
Product be the velocity ratio of two square transmission devices 2, by formula (1-8), the velocity ratio of double-moment action gear train is
,
(1-9)
The angle of revolution speed of double-moment action gear train is,
(1-10)
The moment of torsion of double-moment action gear train output,
The velocity ratio of double-moment action gear train is the velocity ratio of gear differential gear train 1, the product of action radius ratio and bar ratio.By formula (1-9), change r
1And r
2And L
1And L
2, in conjunction with changing velocity ratio
, all can change velocity ratio
For example, change L
1Length, work as L
1Greater than L
2The time, L
1Big more, Ma is just big more, velocity ratio
Just more little, M
4Just big more.Change radius r
1Or change radius r
2, or change L
1Length, or change L
2Length, ω
2Can not change.
The double-moment action gear train transport characteristics is, in this transmission system with two degrees of freedom of gear differential gear train, there are two moments of torsion respectively to present different motion states respectively, a power source moment of torsion makes the angle of revolution speed of input central gear keep identical with power source moment of torsion angular velocity, other has an instantaneous input torque that is formed by instantaneous output moment of flexure, affacts on the input central gear, passes through planetary pinion, make the output center gear rotation motion, externally acting.
More than a kind of pair of square gear stepless speed variator illustrated in figures 1 and 2, be a kind of concrete device of double-moment action gear train, the concrete working procedure of two square gear stepless speed variators is as follows:
On universal drive shaft bearing 37, the power source moment of torsion drives arm axle 38 by driving wheel 25 and live axle 23 and makes lever cambered axle 39 rotation motion on the universal drive shaft bearing, resistance arm axle 8 on the lever cambered axle 39 drives driven wheel 7 rotation motions by resistance shaft 9, driven wheel 7 drives input central gear 3, input central gear 3 makes output center gear 4 do rotation motion by planetary pinion 5.Two square gear stepless speed variators are by the adjustable lever ratio
Reach infinite variable speed purpose, utilize stepless speed-regulating device 24, make live axle 23 be in the arbitrary position of regulating tank 41 and dovetail groove 18, live axle 23 point of action are to the distance L at universal drive shaft bearing 37 centers
1Change, resistance shaft 9 point of action are to the distance L at universal drive shaft bearing 37 centers
2Constant, the L of different sizes
1Make the bar ratio
The change that varies in size, the angle of revolution speed of output center gear 4 changes thereupon, and this process is recently to realize infinite variable speed by the transmission that changes two square transmission devices 2; This pair square gear stepless speed variator also can be provided with dovetail groove 18 and regulating tank 41 with resistance arm axle 8 and driven wheel 7, utilizes stepless speed-regulating device 24 to regulate L
2The arbitrary position, keep the distance L of live axle 23 to universal drive shaft bearing 37 centers
1Constant, also can realize stepless change; In two square transmission devices 2, the invariant position that the live axle 23 that is installed together with driving arm axle 38 and driving wheel 25 arrives universal drive shaft bearing central point is set, L
1Be a definite value, the invariant position that the resistance shaft 9 that is installed together with resistance arm axle 8 and driven wheel 7 arrives universal drive shaft bearing central point be set, L
2Be a definite value, the velocity ratio of two square transmission devices 2 is a fixed drive ratio, and two square gear stepless speed variators become a kind of two square gear reducers that all stable drive ratios are arranged.
Two square gear stepless speed variators, it is the velocity ratio of gear differential gear train, product with bar ratio and action radius ratio, its transmission efficiency is synthetic with the transmission efficiency of two square transmission devices 2 by the transmission efficiency of gear differential gear train 1, because be recently to reach infinite variable speed requirement by changing bar, the transmission efficiency of two square gear stepless speed variators after speed change can remain unchanged; Can only compare by changing the gear reducer that tooth radius obtains various velocity ratios with traditional, two square gear reducers can obtain various velocity ratios by increase or the minimizing to bar ratio and action radius ratio, two square gear reducers with single-stage meshed gears differential gear train 1, compare traditional gear engagement to many gear reducers, saved the consumption of gear, also saved relevant supporting casing, bearing, the consumption of lubricated wet goods.
With reference to Fig. 4 is that a kind of pair of square of the present invention is synchronously with the plan view of stepless speed changer, it is a kind of concrete device of double-moment action gear train, constitute by synchronous band differential gear train 45 and two square transmission device 2 two-part, wherein two square transmission devices 2 are identical with above-mentioned structure, two square transmission devices 2 shown in Figure 4 are a kind of simple and easy techniques of painting, are with differential gear train 45 to be constructed as follows synchronously:
Input central synchronous belt wheel 46, planet synchronous pulley 47, planet synchronous pulley 48, output center synchronous pulley 49, pivoted arm 50; One end of pivoted arm 50 is provided with rotatingshaft 51, the two ends of rotatingshaft 51, bearing 52 and bearing 53 have been installed respectively, bearing 52 is installed in the inboard center of output center synchronous pulley 49, bearing 53 is installed in the center, upper end of input central synchronous belt wheel 46, and pivoted arm 50 is rotated relative to input central synchronous belt wheel 46 and output center synchronous pulley 49; The other end of pivoted arm 50 is provided with rotatingshaft 54, the centre of rotatingshaft 54 is equipped with two bearings 55, two end rings 56, planet synchronous pulley 47 is assembled together with rotatingshaft 54 lower ends, planet synchronous pulley 48 is assembled together with rotatingshaft 54 upper ends, between input central synchronous belt wheel 46 and the planet synchronous pulley 47 timing belt 59 is installed, between output center synchronous pulley 49 and the planet synchronous pulley 48 timing belt 60 is installed, the lower end input shaft of input central synchronous belt wheel 46 is assembled together with the driven wheel 7 of two square transmission devices 2, the lower end input shaft of input central synchronous belt wheel 46 is installed on the bearing 58, bearing 58 is installed on the bearing support, the output shaft of output center synchronous pulley 49 upper ends is installed on the bearing 57, and bearing 57 is installed on the bearing support.Two squares concrete working procedure with stepless speed changer synchronously are as follows:
On universal drive shaft bearing 37, the power source moment of torsion drives arm axle 38 by driving wheel 25 and live axle 23 and makes lever cambered axle 39 rotation motion on the universal drive shaft bearing, resistance arm axle 8 on the lever cambered axle 39 drives driven wheel 7 rotation motions by resistance shaft 9, driven wheel 7 drives input central synchronous belt wheel 46, input central synchronous belt wheel 46 drives planet synchronous pulley 47 by timing belt 59, drive planet synchronous pulley 48 simultaneously, planet synchronous pulley 48 drives synchronous pulley 49 by timing belt 60 and rotates, externally acting.
Two squares are synchronously with the velocity ratio of differential gear train 45 with the velocity ratio of stepless speed changer synchronously, the product of action radius ratio and bar ratio, it also is recently to realize infinite variable speed by the transmission that changes two square transmission devices 2, equally, the velocity ratio that two square transmission devices 2 are set is a fixed drive ratio, and two squares can become with stepless speed changer synchronously a kind ofly has two squares of fixed drive ratio to be with speed reducer synchronously.
Above-mentioned synchronous band differential gear train 45 critical pieces are synchronous pulley and timing belt, timing belt is made of rubber and fiber, synchronous pulley with its engagement driving, to the requirement of material generally by low carbon steel, alloy aluminum or plastics just can be accomplished, the processing of synchronous pulley is easier than Gear Processing, and synchronous pulley and timing belt engagement do not need to lubricate, and rotational noise is low; With the gear reduction unit ratio, under the situation of same transmission power and same velocity ratio, two squares are with speed reducer to save steel synchronously, save the processing resource, save the energy, environmental protection, and noise is low.
With reference to Fig. 5 is the plan view of a kind of pair of square chain stepless speed changer of the present invention, it is a kind of concrete device of double-moment action gear train, constitute by chain differential gear train 61 and two square transmission device 2 two-part, wherein two square transmission devices 2 are identical with above-mentioned structure, two square transmission devices 2 shown in Figure 5 are a kind of simple and easy techniques of painting, and chain differential gear train 61 is constructed as follows:
Chain differential gear train 61 is close with above-mentioned synchronous band differential gear train 45 structures, to be replaced as input center sprocket wheel 62 with the input central synchronous belt wheel 46 in the differential gear train 45 synchronously, planet synchronous pulley 47 is replaced as planet sprocket 63, planet synchronous pulley 48 is replaced as planet sprocket 64, output center synchronous pulley 49 is replaced as output center sprocket wheel 65, timing belt 59 displacement chainings 66, timing belt 59 displacement chainings 67, other structure is the same.
The working procedure with stepless speed variator is the same synchronously with two squares for the working procedure of two square chain stepless speed variators, the velocity ratio of two square chain stepless speed changers is velocity ratios of chain differential gear train 61, the product of action radius ratio and bar ratio, it also is recently to realize infinite variable speed by the transmission that changes two square transmission devices 2, equally, the velocity ratio that two square transmission devices 2 are set is a fixed drive ratio, and two square chain stepless speed changers can become a kind of two square chain speed reducers that fixed drive ratio is arranged.
Two square chain stepless speed variators or two square chain speed reducer have been opened up a new approach for the chain reduction machine, it can with some light-duty coordinative composition of equipments, as speed-changing driving device, or turn round device as a kind of increasing as LEV.
Above-described gear differential gear train 1, be with differential gear train 45 synchronously, chain differential gear train 61, a common characteristic is arranged, it all is the differential gear train that forms in the mode that meshes, they can be referred to as the engagement differential gear train, the engagement differential gear train has constituted double-moment action gear train jointly with two square transmission devices 2; With two square gear stepless speed variators, two squares are with stepless speed changer and two square chain stepless speed changer to be referred to as two square stepless speed changers synchronously; With two square gear reducers, two squares are with speed reducer and two square chain speed reducer to be referred to as two square speed reducers synchronously.
With reference to Fig. 6 is the kind of drive schematic representation of a kind of specific embodiment of the present invention, two square transmission devices 2 in this schematic representation are a kind of simple and easy techniques of painting, the formation of present embodiment is, the two square transmission devices 2 of two covers are cascaded, the driven wheel 7 of two square transmission devices 2 of lower end, by being assemblied in the axle 71 on the bearing support, interfix with the driving wheel 25 of two square transmission devices 2 of upper end and to be assembled together, the rotational axis of the lever cambered axle 39 of the two square transmission devices 2 of two covers is coaxial, the upper end two square transmission devices 2 driven wheel 7 by be assemblied on the bearing support the axle 72 and umbrella gear 68 mutual mounts together, umbrella gear 68 is meshed with umbrella gear 69, umbrella gear 69 is assembled together with the axle 73 that is assemblied on the bearing support, umbrella gear 69 can move axially on axle 73, if umbrella gear 68 is 1 with the velocity ratio of umbrella gear 69, corresponding with umbrella gear 69 is umbrella gear 70, umbrella gear 70 is assemblied on the axle 73, umbrella gear 70 can move axially on axle 73, axle 73 two end devices two sleeve gear differential gear trains 1, axle 73 two ends and two input central gears 3 are assembled together, umbrella gear 68, umbrella gear 69 and umbrella gear 70 constitute the input transmission device of importing central gear 3 with axle 73 and axle 72.
The implementation methods of present embodiment, process is as follows: the two square transmission devices 2 in lower end are on driven wheel 7, by the instantaneous input torque M of instantaneous output moment M a generation
2A, the driving wheel 25 of the two square transmission devices 2 by the upper end act on the lever cambered axle 39 of upper end, and the velocity ratio of the two square transmission devices 2 in upper end multiply by the instantaneous input torque M of the two square transmission devices 2 in lower end
2A, the instantaneous input torque of two square transmission devices 2 on can obtaining; The angular velocity of the driven wheel 7 of the two square transmission devices 2 in upper end is identical with the power source moment of torsion angular velocity of the two square transmission devices 2 in lower end, and the angular velocity of two input central gears 3 is identical with power source moment of torsion angular velocity; The umbrella gear 68 and umbrella gear 69 of the instantaneous input torque of the two square transmission devices 2 in upper end by being meshed, be delivered on two input central gears 3 at axle 73 two ends, two planetary pinions 5 are produced two active forces, with two external load to the mutual balanced action of the active force of two planetary pinions 5, make two output center gears 4 do rotation motion, externally acting; This embodiment is by the be cascaded gear differential gear train 1 of a pair of parallel connection of acting in conjunction of two two square transmission devices 2, its velocity ratio is the product of the product of the velocity ratio of the two square transmission devices 2 of the velocity ratio of the two square transmission devices 2 in upper end and lower end and the velocity ratio of a gear differential gear train 1; When two that are cascaded two square transmission devices 2 kept a direction to rotate, umbrella gear 69 exchanged with umbrella gear 70, can make the output terminal of two gear differential gear trains 1 realize the rotation of positive and negative both direction.
Because two output terminals of this embodiment are a pair of gear differential gear train 1, this embodiment is applicable to the motivational drive of automobile, and two gear differential gear trains 1 can drive two parallel car-wheel, can be a kind of novel automobile variable speed drive units.
With reference to Fig. 7 is the kind of drive schematic representation of a kind of specific embodiment of the present invention, two square transmission devices 2 in this schematic representation are a kind of simple and easy techniques of painting, the formation of present embodiment is, the two square transmission devices 2 of two covers are connected in parallel, the driven wheel 7 of two square transmission devices 2 of lower end, be connected with axle 76 assemblings on being assemblied in bearing support, axle 76 upper ends assembling connection gear 74, the driving wheel 25 of two square transmission devices 2 of upper end be assemblied in bearing support on spools 77 assemble and be connected, axle 77 lower ends are connected with gear 75 assemblings, gear 74 is meshing with each other with gear 75, if gear 74 is 1 with gear 75 intermeshing velocity ratios, the driven wheel 7 of two square transmission devices 2 of upper end is assembled together with synchronous pulley 79 mutually by the axle 78 that is assemblied on the bearing support, the upper end of axle 78 is connected with 3 assemblings of the input central gear of left side gear differential gear train 1, synchronous pulley 79 is connected with synchronous pulley 81 by the capable band 80 of synchronous tooth, if synchronous pulley 79 is 1 with the velocity ratio of synchronous pulley 81, synchronous pulley 81 is connected with the input central gear 3 mutual assemblings of right side gear differential gear train 1 by the axle 82 that is assemblied on the bearing support.
The implementation methods of present embodiment, process is as follows: the two square transmission devices 2 in lower end are on driven wheel 7, by the instantaneous input torque M of instantaneous output moment M a generation
2A by the be meshing with each other driving wheel 25 of two square transmission devices 2 of being delivered to the upper end of gear 74 and gear 75, acts on the lever cambered axle 39 of upper end, and the velocity ratio of the two square transmission devices 2 in upper end multiply by the instantaneous input torque M of lower end pair square transmission devices 2
2A, the instantaneous input torque of two square transmission devices 2 on can obtaining; The angular velocity of the driven wheel 7 of the two square transmission devices 2 in upper end is identical with the power source moment of torsion angular velocity of the two square transmission devices 2 in lower end, and the angular velocity of two input central gears 3 is identical with power source moment of torsion angular velocity; The instantaneous input torque of the two square transmission devices 2 in upper end, synchronous pulley 79 and synchronous pulley 81 by the axle 78 and the transmission that is meshing with each other, import on the central gear 3 for two about affacting respectively, two planetary pinions 5 are produced two active forces, with two external load to the mutual balanced action of the active force of two planetary pinions 5, two output center gears 4 are done rotation motion about making, externally acting; This embodiment is by the be connected in parallel gear differential gear train 1 of a pair of parallel connection of acting in conjunction of two two square transmission devices 2, its velocity ratio is the product of the product of the velocity ratio of the two square transmission devices 2 of the velocity ratio of the two square transmission devices 2 in upper end and lower end and the velocity ratio of a gear differential gear train 1; This embodiment is applicable to the externally device of acting that is parallel to each other, and as propeller cavitation that can a pair of boats and ships of parallel drive, can be a kind of novel boats and ships speed-changing driving device.
With reference to Fig. 8 is the sectional view of a kind of universal drive shaft bearing of the present invention, this kind universal drive shaft bearing is a kind of bearing support 86 of the spherical bearing 85 of dribbling, it is a kind of bearing support that holds with expansion mandrel, spherical bearing 85 is made of with outer ball 84 interior ball 83, spherical bearing 85 uses on two square transmission devices 2 as follows: the outer ball 84 of spherical bearing 85 is connected with extraneous bearing support 86 assemblings, interior ball 83 is connected the rotational axis X of the axis of jack shaft 10 and lever cambered axle 39 with jack shaft 10 assemblings
1-X
1Intersect, its crosspoint is the central point of spherical bearing 85, and the axis of central point both sides jack shaft 10 is around the rotational axis X of lever cambered axle 39
1-X
1Rotate, ball 83 was around the rotation motion of central point any direction in jack shaft 10 drove, and the bearing support 86 of dribbling spherical bearing 85 can be realized the rotation motion of lever cambered axle 39, can be used as the fulcrum of lever cambered axle 39.
Claims (10)
1. the method for a double-moment action gear train, it is characterized in that, under the permanent power, in the double-moment action gear train that constitutes by engagement differential gear train and two square transmission devices, the lever cambered axle is done fulcrum with the universal drive shaft bearing, and do rotation motion thereon, the power source moment of torsion passes through the driving wheel wobbler action on the driving arm of lever cambered axle, produce an instantaneous input moment of flexure, instantaneous input moment of flexure is by the lever cambered axle, resistance arm output terminal at the lever cambered axle, form an instantaneous output moment of flexure, the direction of instantaneous input moment of flexure and instantaneous output moment of flexure is always vertical mutually with the direction of power source moment of torsion, instantaneous output moment of flexure acts on the input central gear by driven wheel, produce one and the always orthogonal instantaneous input torque of its direction, the input end of input central gear exists an instantaneous input torque and a moment of torsion identical with the power source moment of torsion, active force that instantaneous input torque produces planet wheel and external load are to the mutual balanced action of the active force of planet wheel, make the output center wheel do rotation motion, externally acting, have on the engagement differential gear train of two degrees of freedom, the angular velocity of input central gear is identical with power source moment of torsion angular velocity, the angular velocity of output center wheel is that the angular velocity by instantaneous input torque forms, the angular velocity of instantaneous input torque is formed by instantaneous output moment of flexure angular velocity and power source moment of torsion angular velocity, the velocity ratio of double-moment action gear train is the velocity ratio of engagement differential gear train, the product of action radius ratio and bar ratio.
2. two square stepless speed changer, constitute by engagement differential gear train and two square transmission device, it is characterized in that, described engagement differential gear train is by the input central gear, planet wheel, the output center wheel, pivoted arm constitutes, input central gear and input shaft become one, input shaft is installed on the bearing support, the output center wheel becomes one with output shaft, output shaft is installed on the bearing support, pivoted arm one end of axle and bearing is installed, coaxial line with input central gear and output center wheel is an axis, be axis perhaps with input central gear axis, be axis perhaps with the output center wheel axis, relatively rotate with input central gear and output center wheel, the other end of pivoted arm is equipped with axle, bearing and planet wheel, input central gear and planet wheel engagement driving, planet wheel and output center wheel engagement driving, the engagement differential gear train has two degrees of freedom, described pair of square transmission device is by driving wheel, live axle, the lever cambered axle, the universal drive shaft bearing, resistance shaft, stepless speed-regulating device, driven wheel constitutes, the lever cambered axle is by driving arm, jack shaft, resistance arm constitutes, the lever cambered axle is installed on the universal drive shaft bearing of fixedlying connected with the external world, resistance arm is installed together by resistance shaft and driven wheel, driving arm is provided with live axle, live axle is connected with stepless speed-regulating device by driving wheel, stepless speed-regulating device and live axle can driving arm axially on and driving wheel axially on axially move back and forth, perhaps opposite, driving arm is installed together by live axle and driving wheel, resistance shaft is set on the resistance arm, resistance shaft is connected with stepless speed-regulating device by driven wheel, stepless speed-regulating device and resistance shaft can resistance arm axially on and driven wheel axially on axially move back and forth, driving wheel links together with the input shaft that is installed on the bearing support, the rotational axis of lever cambered axle is by the central point of universal drive shaft bearing, and driven wheel links together with the input central gear by the input shaft or the input transmission device of input central gear.
3. a kind of pair of square stepless speed changer according to claim 2, it is characterized in that, in the described pair of square transmission device, the live axle that setting and driving arm and driving wheel are installed together is to the invariant position of universal drive shaft bearing central point, the resistance shaft that setting and resistance arm and driven wheel are installed together is to the invariant position of the central point of universal drive shaft bearing, and two square stepless speed changers can become a kind of pair of square speed reducer.
4. a kind of pair of square stepless speed changer according to claim 2 is characterized in that described engagement differential gear train can be, and the gear differential gear train is with differential gear train synchronously, the chain differential gear train.
5. a kind of pair of square stepless speed changer according to claim 2 is characterized in that, with the setting of can connecting of described pair of square transmission device, perhaps described pair of square transmission device can be arranged in parallel.
6. a kind of pair of square stepless speed changer according to claim 2, it is characterized in that, described engagement differential gear train can be arranged in parallel, and described pair of square transmission device linked together by input shaft or input transmission device and input central gear in the engagement differential gear train that is arranged in parallel.
7. two square transmission device, by driving wheel, live axle, the lever cambered axle, universal drive shaft bearing, resistance shaft, driven wheel constitutes, it is characterized in that the lever cambered axle is by driving arm, jack shaft, resistance arm constitutes, the lever cambered axle is installed on the universal drive shaft bearing of fixedlying connected with the external world, and driven wheel links together with the output shaft that is installed on the bearing support, and resistance arm is installed together by resistance shaft and driven wheel, driving arm is installed together by live axle and driving wheel, driving wheel links together with the input shaft that is installed on the bearing support, and the rotational axis of lever cambered axle passes through the central point of universal drive shaft bearing, and overlaps with the coaxial line of driving wheel and driven wheel.
8. universal drive shaft bearing, by fork ring in universal, universal outer fork ring, the external support ring, rolling bearing constitutes, it is characterized in that, universal interior fork encircles radially, and two ends are provided with two fork shafts, two fork shaft coaxial lines, universal outer fork encircles radially, and two ends are provided with two fork shafts, two fork shaft coaxial lines, on fork encircles outside universal, be provided with two axis holes with the orthogonal radial line of the axis of two fork shafts two ends, the axis coaxle of two axis holes also intersects vertically mutually with the axis of two fork shafts, external support ring radially two ends is provided with two axis holes, the axis coaxle of two axis holes, rolling bearing single-row or be fixedly mounted on side by side universal on the center hole of fork ring, two fork shafts of fork ring are installed on two axis holes of universal outer fork ring in universal, two fork shafts of universal outer fork ring are installed on two axis holes of external support ring, the external support ring and the external world are fixedly connected, the coaxial line of the coaxial line of two fork shafts of fork ring and two fork shafts of universal outer fork ring intersects vertically mutually in the direction, and its crosspoint is the central point of universal drive shaft bearing.
9. a kind of universal drive shaft bearing according to claim 8, it is characterized in that, between the axis hole that the fork shaft of described universal interior fork ring and universal outer fork encircle, rolling bearing can be installed, and use the positioning device axially locating, between the fork shaft of described universal outer fork ring and the axis hole of external support ring, rolling bearing can be installed, and use the positioning device axially locating.
10. a kind of universal drive shaft bearing according to claim 8 is characterized in that, described a kind of universal drive shaft bearing can be a kind of bearing support that holds with expansion mandrel.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008100141748A CN101225876A (en) | 2008-02-20 | 2008-02-20 | Double-moment action gear train method and device |
| CN 200910007328 CN101482162B (en) | 2008-02-20 | 2009-02-11 | Forward sleepless transmission device and method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008100141748A CN101225876A (en) | 2008-02-20 | 2008-02-20 | Double-moment action gear train method and device |
Publications (1)
| Publication Number | Publication Date |
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| CN101225876A true CN101225876A (en) | 2008-07-23 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008100141748A Pending CN101225876A (en) | 2008-02-20 | 2008-02-20 | Double-moment action gear train method and device |
| CN 200910007328 Expired - Fee Related CN101482162B (en) | 2008-02-20 | 2009-02-11 | Forward sleepless transmission device and method |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910007328 Expired - Fee Related CN101482162B (en) | 2008-02-20 | 2009-02-11 | Forward sleepless transmission device and method |
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| CN (2) | CN101225876A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010091601A1 (en) * | 2009-02-11 | 2010-08-19 | Chen Maosheng | Forward stepless speed changing device and method thereof |
| CN103411576A (en) * | 2012-11-22 | 2013-11-27 | 北京经纬恒润科技有限公司 | Method for determining angular accuracy of synchronous belt drive |
| CN105937554A (en) * | 2016-06-20 | 2016-09-14 | 苏州市灵通玻璃制品有限公司 | Parallel transmission power coupling |
| CN112888878A (en) * | 2018-10-10 | 2021-06-01 | 国立大学法人九州工业大学 | Parallel linkage and linkage actuating device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107110303A (en) * | 2014-12-08 | 2017-08-29 | 德纳有限公司 | 3 pattern front-wheel drives and the stepless planetary variable-speed device of rear wheel drive |
| EP3803161B1 (en) | 2018-05-30 | 2023-07-26 | Carrier Corporation | Energy management systems (ems) for transportation refrigeration units (tru) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1094574C (en) * | 1997-02-19 | 2002-11-20 | 周伟 | Differential gear transmission system stepless speed variator |
-
2008
- 2008-02-20 CN CNA2008100141748A patent/CN101225876A/en active Pending
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2009
- 2009-02-11 CN CN 200910007328 patent/CN101482162B/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010091601A1 (en) * | 2009-02-11 | 2010-08-19 | Chen Maosheng | Forward stepless speed changing device and method thereof |
| CN103411576A (en) * | 2012-11-22 | 2013-11-27 | 北京经纬恒润科技有限公司 | Method for determining angular accuracy of synchronous belt drive |
| CN103411576B (en) * | 2012-11-22 | 2016-02-10 | 北京经纬恒润科技有限公司 | A kind of method determining toothed belt transmission angular accuracy |
| CN105937554A (en) * | 2016-06-20 | 2016-09-14 | 苏州市灵通玻璃制品有限公司 | Parallel transmission power coupling |
| CN112888878A (en) * | 2018-10-10 | 2021-06-01 | 国立大学法人九州工业大学 | Parallel linkage and linkage actuating device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101482162A (en) | 2009-07-15 |
| CN101482162B (en) | 2013-04-17 |
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