CN101905651A - Differential-twist driving device - Google Patents
Differential-twist driving device Download PDFInfo
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- CN101905651A CN101905651A CN2009100625064A CN200910062506A CN101905651A CN 101905651 A CN101905651 A CN 101905651A CN 2009100625064 A CN2009100625064 A CN 2009100625064A CN 200910062506 A CN200910062506 A CN 200910062506A CN 101905651 A CN101905651 A CN 101905651A
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Abstract
The invention provides a differential-twist driving device consisting of a main speed reducer, an inter-axle differential A, a front differential B, a rear differential C, an intermediate differential D, an anti-skid composite differential D, and a clutch H. By connecting the differentials, the power is distributed to singly drive each wheel. The clutch is used for forcibly engaging (locking) or separating under the action of the external force. By connecting the differentials, the power is distributed to singly drive each wheel, and the problem on the nonuniform distribution of torque and rotation speed of front and rear wheels of the vehicle according to the attachment change on the ground is solved, and the torque and the rotation speed of front and rear wheels can be automatically adjusted so that the speed difference and the skid prevention between front and rear axles, wheels and diagonal wheels can be realized. The invention is used for various full-driving and full-time vehicles with large and small tonnage.
Description
Technical field
The present invention relates to a kind of differential-twist driving device, is to finish vehicle to run with the means of pure machinery, finishes according to the speed difference of required propulsive effort of state of ground and Ackermann steer angle that differential, difference are turned round, skidproof a kind of transmission field.
Background technology
Up to the present, automobile adopts the mode that installs diff on propons or back axle additional to carry out torsion and differentia transmission usually, and this type of automobile is in muddy highway, ice and snow road, rugged location, and wheel is easy to skid, and can't walk.For this reason, many bridges multiple-wheel drive occurs, but also can only be a plurality of and ground-surface condition of adhering to, do not solved between the wheel power distribution Problem of Failure that under the very poor condition of road conditions, produces equally, i.e. the character 2n=n of diff
1+ n
2, as a side n
1Or n
2There is adhesive ability not have rotating speed when being zero, the n of opposite side
1Or n
2Fast idle does not have adhesive ability, and automobile just can't be walked.
Granted publication is number for the patent of invention of CN 1225374C discloses a kind of frequently interlocked universal differential driver, and it mainly is to be made of four difies: middle central composite differential, and each connects its two ends with a diff; One of two semiaxis of diff are solid semiaxis, and another is a hollow half axle, and wherein hollow half axle and hollow half axle, solid semiaxis and solid semiaxis link to each other with wheel on the diagonal line respectively; The solid semiaxis of two a difies end separately connects together by the two-semiaxle gear of differential in the central authorities; The series connected differential casing engagement in outer differential side gear of central authorities and two ends, it is characterized in that: described device also comprises two power distribution devices, the two ends diff links to each other with wheel by described power distribution device, central authorities' composite differential is sleeved on together by an outer differential of a shared bearing pin and an interior differential and constitutes, two semiaxis link to each other with two axle side gears respectively, solid semiaxis is connected with solid axle side gear, hollow half axle is with after the hollow half axle gear is connected, pass solid axle side gear by solid semiaxis and be nested together, and draw from the outside, two ends respectively.This device inactivity circulation, in the desert, the location, marsh travels, the opportunity of wheel slip is few, can obviously improve the crossing ability of vehicle.But when walking, still there is the problem of tyre skidding in the most extreme Wu Lu location.
Summary of the invention
Adhere to condition automobile problem of skidding when minimum in order to solve existing frequently interlocked universal differential driver front and rear wheel and monolateral wheel in the one side, the present invention proposes differential-twist driving device.
Technical scheme of the present invention is: differential-twist driving device is characterized in that: be made up of main reduction gear, interaxle differential A, preceding diff B, back diff C, the diff D of intermediary and anti-skidding composite differential E, a power-transfer clutch H;
Interaxle differential A is given in the driving gear of main reduction gear and ring gear engagement power transmission, and this interaxle differential A is made up of housing, planetary wheel, center cross, half front axle gear ring, half-rear axle gear ring; Housing and the half front axle gear ring among the interaxle differential A of preceding diff B are shared, the cross frame of preceding diff B is fixed on the half front axle gear ring, bevel planet gear before the suit on the preceding cross frame, and with preceding hollow drive shaft gear and preceding solid drive shafts gear constant-mesh simultaneously, a front-wheel walking of solid drive shafts gear, driving automobile before preceding solid drive shafts is connected, another front-wheel walking of hollow drive shaft gear drive;
Be provided with female splines and cylindrical spline in the tail end circular groove of the solid drive shafts gear among the preceding diff B, overriding clutch ring, internal overrunning coupler ring outside female splines in circular groove and cylindrical spline place are set with respectively, an end of overriding clutch ring, internal overrunning coupler ring is provided with compression spring I, compression spring II outside, and compression spring I, compression spring II are contained in the tail end circular groove of solid drive shafts gear; The other end of overriding clutch ring, internal overrunning coupler ring is provided with unidirectional power transmission tooth outside, respectively with anti-skidding composite differential E in compound power transmission gear ring and the unidirectional power transmission dental articulation of compound unofficial biography powershift gear one end; Half-rear axle gear ring among the housing of back diff C and the interaxle differential A is shared, back cross frame is fixed on the half-rear axle gear ring, bevel planet gear and mesh simultaneously behind the suit on the back cross frame with two-sided finishing bevel gear cuter and back hollow drive shaft gear, solid drive shafts after two-sided finishing bevel gear cuter is connected drives the rear flank wheel walking of automobile; The opposite side trailing wheel walking of back hollow drive shaft gear drive automobile; The anti-skidding composite differential E that contains in the interaxle differential A constitutes compound cross bar by inner ring sleeve, outer ring set, bearing pin, it is a rigid body that inner planet finishing bevel gear cuter among the anti-skidding composite differential E and outer planet finishing bevel gear cuter are connected, be sleeved on the compound cross bar, the endoporus spline of compound cross bar is connected with an end of back solid drive shafts; One end of compound unofficial biography powershift gear is tapered gear and outer planet finishing bevel gear cuter constant-mesh, its other end is unidirectional power transmission tooth and the interlock of internal overrunning coupler ring, one end of compound power transmission gear ring is tapered gear and outer planet finishing bevel gear cuter constant-mesh, and its other end is unidirectional power transmission tooth and the interlock of outer overriding clutch ring; Inner planet finishing bevel gear cuter and compound interior power transmission gear constant-mesh, it is a rigid body that compound interior power transmission gear and intermediary's axle side gear are connected by the spline hollow shaft; Middle poor bevel planet gear constant-mesh among intermediary's axle side gear and the diff D of intermediary, middle poor bevel planet gear among the diff D of intermediary and two-sided finishing bevel gear cuter constant-mesh; Two-sided finishing bevel gear cuter again with back diff C in back bevel planet gear constant-mesh, the back bevel planet gear among the back diff C again with back hollow half axle gear mesh;
The diff D of intermediary by middle poor cross frame with in being sleeved on difference on the cross frame middle poor bevel planet gear and constituted with the intermediary's axle side gear and the two-sided finishing bevel gear cuter of middle poor bevel planet gear constant-mesh, in the difference cross frame be fixed on the half-rear axle gear ring among the interaxle differential A, with the shared housing of back diff C; Two-sided finishing bevel gear cuter promptly is the end axle side gear of the diff D of intermediary, is again the axle side gear of back diff C, and is fixed together with the back solid drive shafts; Then the compound cross bar among an end of solid drive shafts and the anti-skidding composite differential E is affixed is a rigid body;
Power-transfer clutch H is positioned at the front portion of interaxle differential A, and be provided with the square tooth of clutch at the front end of the housing of interaxle differential A, the tail end of the half front axle gear ring in interaxle differential A is provided with spline, power-transfer clutch H is sleeved on the spline, and the square tooth of clutch of the front end setting of the housing among power-transfer clutch H and the interaxle differential A is separated or interlock by the external force effect.
The sliding mechanism of control: the unidirectional power transmission dental articulation control front-wheel of the unidirectional power transmission tooth of compound unofficial biography powershift gear one end of anti-skidding composite differential E and the solid axle side gear among the preceding diff B skids, and its another compound in the power transmission gear link to each other with intermediary's axle side gear of D in the intermediary differential, by the back hollow drive shaft gear of two-sided finishing bevel gear cuter control back diff C, control a rear wheels slip; Two-sided finishing bevel gear cuter, compound cross bar link to each other another rear wheels slip of Control of Automobile with the solid semiaxis in back.
Beneficial effect: described differential-twist driving device is by a plurality of diff interconnection, each wheel of difference power distribution independent drive, according to ground-surface adhering to changing moment of torsion, rotating speed unequal distribution and the energy automatic compensation that solves the forward and backward wheel of vehicle, can realize differential between forward and backward bridge, differential between wheel is to the horn ring differential; Anti-skidding between forward and backward bridge, to anti-skidding between the horn ring, the wheel between anti-skidding.This differential-twist driving device is at multiple complex-terrain, can both give full play to each wheel drive force and turns to freely as express highway and ice, snow, muddy water ground straight line or the walking of turning, and is applicable to that various large and small tonnages drive full-time vehicle entirely.
Description of drawings
Fig. 1 is the structure cutaway view of differential-twist driving device.
Fig. 2 is that the J place refers to the partial enlarged drawing that square frame is interior among Fig. 1.
Fig. 3 is that the K place refers to the partial enlarged drawing that square frame is interior among Fig. 1.
Fig. 4 is the cutaway view of the differential-twist driving device of Fig. 1 along A-A.
Fig. 5 is the drive connection sketch of differential-twist driving device.
The specific embodiment
Shown in Fig. 1,2,3,4, description the present invention is as follows: differential-twist driving device is characterized in that: be made up of main reduction gear, interaxle differential A, preceding diff B, back diff C, the diff D of intermediary and anti-skidding composite differential E, several parts of power-transfer clutch H;
The driving gear 1 of main reduction gear is given interaxle differential A with ring gear 2 engagement power transmissions, and this interaxle differential A is made up of housing 3, planetary wheel 4, center cross 5, half front axle gear ring 6, half-rear axle gear ring 7; Housing and the half front axle gear ring 6 among the interaxle differential A of preceding diff B are shared, preceding cross frame 8 among the preceding diff B is fixed on the half front axle gear ring 6, bevel planet gear 9 before the suit on the preceding cross frame 8, and with preceding hollow drive shaft gear 10 and preceding solid drive shafts gear 11 constant-mesh simultaneously, a front-wheel walking of solid drive shafts gear 11, driving automobile before preceding solid drive shafts 12 is connected, hollow drive shaft gear 10 drives another front-wheels and walks; Be provided with female splines F and cylindrical spline G in the tail end circular groove of the solid drive shafts gear 11 among the preceding diff B, overriding clutch ring 13, internal overrunning coupler ring 14 outside female splines F place in circular groove and cylindrical spline G place are set with respectively, an end of overriding clutch ring 13, internal overrunning coupler ring 14 is provided with compression spring I 15, compression spring II 16 outside, and compression spring I 15, compression spring II16 are contained in the tail end circular groove of solid drive shafts gear 11; The other end of overriding clutch ring 13, internal overrunning coupler ring 14 is provided with unidirectional power transmission tooth outside, respectively with anti-skidding composite differential E in compound power transmission gear ring 29 and the unidirectional power transmission dental articulation of compound unofficial biography powershift gear 27 1 ends; Half-rear axle gear ring 7 among the housing of back diff C and the interaxle differential A is shared, back cross frame 17 is fixed on the axle side gear ring 7, on the back cross frame 17 behind the suit bevel planet gear 18 and with two-sided finishing bevel gear cuter 19 and back hollow drive shaft gear 20 constant-mesh simultaneously, solid drive shafts 21 after two-sided finishing bevel gear cuter 19 is connected, drive the rear flank wheel walking of automobile, back hollow drive shaft gear 20 drives the trailing wheel walking of automobile opposite side; The anti-skidding composite differential E that contains in the interaxle differential A constitutes compound cross bar by inner ring sleeve 22, outer ring set 23, bearing pin 24, it is a rigid body that inner planet finishing bevel gear cuter 25 among the anti-skidding composite differential E is connected with outer planet finishing bevel gear cuter 26, be sleeved on the compound cross bar, the endoporus spline of compound cross bar is connected with an end of back solid drive shafts 21; One end of compound unofficial biography powershift gear 27 is tapered gear and outer planet finishing bevel gear cuter 26 constant-meshes, and the other end of compound unofficial biography powershift gear 27 is unidirectional power transmission tooth and the interlock of internal overrunning coupler ring; One end of compound power transmission gear ring 29 is tapered gear and outer planet finishing bevel gear cuter 26 constant-meshes, and the other end of compound power transmission gear ring 29 is unidirectional power transmission tooth and the interlock of outer overriding clutch ring; Inner planet finishing bevel gear cuter and 25 compound interior power transmission gear 28 constant-meshes, it is a rigid body that compound interior half power transmission gear 28 is connected by spline hollow shaft 30 with intermediary's axle side gear 31, the bevel planet gear constant-mesh among intermediary's axle side gear 31 and the diff D of intermediary; Bevel planet gear among the diff D of intermediary and two-sided finishing bevel gear cuter 19 constant-meshes, two-sided finishing bevel gear cuter 19 again with back diff C in back bevel planet gear 18 constant-meshes, the back bevel planet gear 18 among the back diff C meshes with back hollow half axle gear 20 again;
The diff D of intermediary is the middle poor bevel planet gear 33 on the difference cross frame 32 and constituted with the intermediary's axle side gear 31 and the two-sided finishing bevel gear cuter 19 of middle poor bevel planet gear 33 constant-meshes by middle poor cross frame 32 with in being sleeved on, and middle poor cross bar is fixed on the half-rear axle gear ring 7 among the interaxle differential A; Two-sided finishing bevel gear cuter 19 promptly is the end axle side gear of the diff D of intermediary, it is again the axle side gear of back diff C, and with the back solid drive shafts 21 be fixed together, then the compound cross frame of an end of solid drive shafts 21 and anti-skidding composite differential E is affixed is a rigid body, front end at the housing 3 of interaxle differential A is provided with the square tooth of power-transfer clutch, the tail end of the half front axle gear ring 6 in interaxle differential A is provided with spline, power-transfer clutch H34 is sleeved on the spline, and the square tooth of clutch of the front end setting of the housing among power-transfer clutch H34 and the interaxle differential A is separated or interlock by the external force effect;
The unidirectional power transmission dental articulation control front-wheel of the unidirectional power transmission tooth of compound unofficial biography powershift gear 27 1 ends of anti-skidding composite differential E and solid drive shafts gear 11 1 ends among the preceding diff B skids, and its another compound in power transmission gear 28 link to each other with intermediary's axle side gear 31 among the differential D of intermediary, by the back hollow drive shaft gear 20 among the two-sided finishing bevel gear cuter 19 control back diff C, control a rear wheels slip; And two-sided finishing bevel gear cuter 19, compound cross bar link to each other another rear wheels slip of Control of Automobile with back solid drive shafts 21.
In conjunction with shown in Figure 5, the anti-skidding principle of work of differential-twist driving device is described:
1, establishing automobile left side wheel sky trackslips and is example:
The rotation speed n of off front wheel
3=0, the rotation speed n of off hind wheel
4=0;
The rotation speed n of the near front wheel
7=2n, the rotation speed n of left rear wheel
8=2n.
As shown in Figure 3, whether just can prove the one-sided sky of the automobile problem of trackslipping by the principle of work of anti-skidding composite differential E.Owing to impose a condition is n
4=0, n
3=0, n
4Be again the revolution speed in the anti-skidding composite differential, then have:
n
4/ n
6=k (k＞1), 2n
4=n
8+ kn
5, 2n
4=2n+kn
5, because n
4=0, then have:
n
5=-2n/k is opposite with the off front wheel hand of rotation, makes the speed discrepancy compressing compression spring II of the unidirectional power transmission tooth of internal overrunning coupler ring and its interlock that the interlock of compound unofficial biography powershift gear and internal overrunning coupler ring is broken away from, and does not produce rotating speed and interferes.Because of n
8With n
6Be positioned at same direction, so the two rotating speed in the same way, the speed discrepancy between them is multiple relation, i.e. n
8/ n
6=k (k＞1) is because n
8=2n, then: n
6=n
8/ k=2n/k; n
6Greater than the n that sets
3=0, because of compound power transmission gear ring and preceding solid axle side gear are combined as a whole, force n
6=n
3, they are to finish n by the preceding solid axle side gear that compression spring I compresses outer overriding clutch ring and its interlock
3≠ 0 makes off front wheel produce propulsive effort.
By n
6=n
3=2n/k, the differential of diff B relation before the substitution then has:
2n
6=n
3+ n
7, n
2=n substitution:
2n＝2n/k+n
7，n
7＝2n-2n/k，
Have by automobile four wheels rotating speed equilibrium conditions:
(n
3+ n
7+ n
4+ n
8)/4=n, (2n/k+2n-2n/k+0+2n)/4=4n/4=n, by calculating proof:
The rotation speed n of off front wheel
3=2n/k, the rotation speed n of off hind wheel
4=0;
The rotation speed n of the near front wheel
7=2n-2n/k, the rotation speed n of left rear wheel
8=2n,
N has taken place
3With n
7, n
8Mutual control, the rotation speed n of a wheel on same hard surfacing
3=2n/k, another wheel n
4=0 situation is false, so each wheel is arranged to the mutual action between the ground, controls each wheel normal rotation, and automobile is normally walked.
2, establish the idle running of automobile right side wheels and be example:
The rotation speed n of off front wheel
3=2n, the rotation speed n of off hind wheel
4=2n;
The rotation speed n of the near front wheel
7=0, the rotation speed n of left rear wheel
8=0.
Whether the proof automobile the one-sided sky problem of trackslipping, as follows:
Owing to impose a condition is n
7=0, n
4=2n concerns n to one group of differential among the anti-skidding composite differential E
8, n
4, n
5Analyze, then have:
Because n
8/ n
5=k (k＞1), so:
2n
4＝n
8+kn
5，
4n＝0+kn
5，
n
5=4n/k, n
5〉=n
3The time play a part control four wheel skies trackslip, then have:
n
5=n
3=n
7=4n/k＞n imposes a condition
7=0,
Concern n by another group differential among the anti-skidding composite differential E
8, n
4, n
6, and n
8, n
6Be in the same way, then have:
Kn
6=n
8, kn
6=0＜n imposes a condition
3=2n, kn
6Equal the n that imposes a condition
7=0, do not play the sky effect of trackslipping of four wheels of control, n
8With n
6Do not interfere, n is arranged
5=4n/k, the differential relation before the substitution among the diff B then has:
2n
2=n
3+ n
7, by n
2=n, n
3=n
5=4n/k, substitution gets:
2n＝4n/k+n
7，n
7＝2n-4n/k。
Calculate proof:
The rotation speed n of off front wheel
3=2n/k, the rotation speed n of off hind wheel
4=2n;
The rotation speed n of the near front wheel
7=2n-4n/k, the rotation speed n of left rear wheel
8=0, three wheels have propulsive effort,
Have by automobile traveling four-wheel rotating speed equilibrium conditions:
(n
3+ n
7+ n
4+ n
8)/4=n, the substitution computing value:
(4n/k+2n+2n-4n/k+0)/and 4=4n/4=n, satisfy equilibrium conditions,
By (n
3+ n
7+ n
4)/3=4n/3＞n, three have the vehicle wheel rotational speed of propulsive effort different separately, produce internal interference, so the cross complaint function is arranged, by the effect of ground in the face of wheel, produce balance, make n
3=n
7=n
4=n
8=n, automobile is normally walked, and one-sided wheel is non-slip.
3, establish the analysis of trackslipping of the forward and backward wheel sky of automobile:
(1), set:
The rotation speed n of off front wheel
3=0, the rotation speed n of off hind wheel
4=2n;
The rotation speed n of the near front wheel
7=0, the rotation speed n of left rear wheel
8=2n.
Be analyzed as follows by the anti-skidding composite differential E of Fig. 3:
Because n
8=2n, n
8/ n
5=k (k＞1), so:
2n
4＝n
8+kn
5，2(2n)＝2n+kn
5，
n
5=2n/k is because of n
5With n
7Be correlated with n
5＞n
7=0, again by n
5=n
3=2n/k＞n imposes a condition
3=0, concern n by another group differential among the anti-skidding composite differential E
6=n
8/ k＞n imposes a condition
3=0, n
6, n
5All than the n that sets
3Greatly, this be by the unidirectional power transmission tooth of the compound unofficial biography powershift gear in the anti-skidding composite differential, compound power transmission gear ring respectively with the interlock of inside and outside overriding clutch ring, finish interlock by the rebound action of compression spring, produce the propulsive effort of front-wheel.So it is big to work as front-wheel adhesive ability, when trailing wheel adhesive ability was very little, front and rear wheel can normally be walked.
(2), set:
The rotation speed n of off front wheel
3=2n, the rotation speed n of off hind wheel
4=0;
The rotation speed n of the near front wheel
7=2n, the rotation speed n of left rear wheel
8=0.
Under these road conditions, the revolution of anti-skidding composite differential, autobiography are zero, and front wheel rotation speed at this moment is higher than trailing wheel, and the compound unofficial biography powershift gear in the anti-skidding composite differential, compound power transmission gear ring will break away from inside and outside overriding clutch ring respectively, can not drive back-wheel drive, produce and skidded.By shown in Figure 1, by power-transfer clutch H the housing of interaxle differential A and the half front axle gear ring of interaxle differential A are combined, make n
1=n
2, automobile is normally walked.
4, behind the between centers locking, during automobile turning, the movement interference analysis:
If the automobile turnon left, n
1=n
2The time:
The rotation speed n of off front wheel
3=n+ Δ n, the rotation speed n of off hind wheel
4=n+ Δ n,
The rotation speed n of the near front wheel
7=n-Δ n, the rotation speed n of the near front wheel
8=n-Δ n.
By anti-skidding composite differential as can be known:
2n
4=n
8+ kn
52 (n+ Δ n)=(n-Δ n)+kn then
5,
n
5＝(n+3Δn)/k＜n
7＝n-Δn。
By above-mentioned analysis, work as n
5＜n
7The time, inside and outside overriding clutch ring breaks away from automatically, does not produce movement interference, and front-wheel is free driven state during turning, turns to freely.
5, by shown in Figure 3, motion interference analysis when describing automobile turning:
(1), between centers does not have locking, free front and back differential n
1≠ n
2The time, establish the automobile turnon left:
The rotation speed n of off front wheel
3=n+ Δ n+ Δ n ', the rotation speed n of off hind wheel
4=n+ Δ n-Δ n ',
The rotation speed n of the near front wheel
7=n-Δ n+ Δ n ', the rotation speed n of the near front wheel
8=n-Δ n-Δ n '.
By anti-skidding composite differential analysis:
2n
4=n
8+ kn
5, 2 (n+ Δ n-Δ n ')=(n-Δ n-Δ n ')+kn then
5,
Δ n＞Δ n ' wherein, then:
n
5＝(n+Δn-Δn′)/k＜n
3＝n+Δn+Δn′，
n
5＜n
3The time, front-wheel is free driven state during turning, turns to freely.
(2), establish automobile right-hand corner, n
1≠ n
2:
The rotation speed n of off front wheel
3=n-Δ n+ Δ n ', the rotation speed n of off hind wheel
4=n-Δ n-Δ n ',
The rotation speed n of the near front wheel
7=n+ Δ n+ Δ n ', the rotation speed n of the near front wheel
8=n+ Δ n-Δ n '.
By anti-skidding composite differential analysis:
2n
4=n8
4+ kn
5, 2 (n-Δ n-Δ n ')=(n+ Δ n-Δ n ')+kn then
5,
Δ n＞Δ n ' wherein, then:
n
5＝(n-3Δn-Δn′)/k＜n
7。
Calculating according to (1), (2) proves, during the left and right turning of automobile, the inactivity circulating motion that four wheels of automobile are realized ideal by the interaction energy of interaxle differential A, preceding diff B, back diff C, and the differential in the anti-skidding composite differential E is not interfered the rotating speed of four wheels.
Work as n
5＞n
7The time, break away from automatically with the unidirectional power transmission tooth of inside and outside overriding clutch ring respectively by the unidirectional power transmission tooth of the compound unofficial biography powershift gear among the anti-skidding composite differential E, compound power transmission gear ring one end, finish This move by the compression of compression spring.When certain wheel does not change, the compression spring resilience, the unidirectional power transmission tooth of inside and outside overriding clutch ring respectively with the unidirectional power transmission dental articulation of compound unofficial biography powershift gear, compound power transmission gear ring, force wheel to obtain propulsive effort.
Claims (1)
1. differential-twist driving device is characterized in that: be made up of main reduction gear, interaxle differential A, preceding diff B, back diff C, the diff D of intermediary and anti-skidding composite differential E, a power-transfer clutch H;
Interaxle differential A is given in the driving gear of main reduction gear and ring gear engagement power transmission, and this interaxle differential A is made up of housing, planetary wheel, center cross, half front axle gear ring, half-rear axle gear ring; Housing and the half front axle gear ring among the interaxle differential A of preceding diff B are shared, the cross frame of preceding diff B is fixed on the half front axle gear ring, bevel planet gear before the suit on the preceding cross frame, and with preceding hollow drive shaft gear and preceding solid drive shafts gear constant-mesh simultaneously, a front-wheel walking of solid drive shafts gear, driving automobile before preceding solid drive shafts is connected, another front-wheel walking of hollow drive shaft gear drive;
Be provided with female splines and cylindrical spline in the tail end circular groove of the solid drive shafts gear among the preceding diff B, overriding clutch ring, internal overrunning coupler ring outside female splines in circular groove and cylindrical spline place are set with respectively, an end of overriding clutch ring, internal overrunning coupler ring is provided with compression spring I, compression spring II outside, and compression spring I, compression spring II are contained in the tail end circular groove of solid drive shafts gear; The other end of overriding clutch ring, internal overrunning coupler ring is provided with unidirectional power transmission tooth outside, respectively with anti-skidding composite differential E in compound power transmission gear ring and the unidirectional power transmission dental articulation of compound unofficial biography powershift gear one end; Half-rear axle gear ring among the housing of back diff C and the interaxle differential A is shared, back cross frame is fixed on the half-rear axle gear ring, bevel planet gear and mesh simultaneously behind the suit on the back cross frame with two-sided finishing bevel gear cuter and back hollow drive shaft gear, solid drive shafts after two-sided finishing bevel gear cuter is connected drives the rear flank wheel walking of automobile; The opposite side trailing wheel walking of back hollow drive shaft gear drive automobile; The anti-skidding composite differential E that contains in the interaxle differential A constitutes compound cross bar by inner ring sleeve, outer ring set, bearing pin, it is a rigid body that inner planet finishing bevel gear cuter among the anti-skidding composite differential E and outer planet finishing bevel gear cuter are connected, be sleeved on the compound cross bar, the endoporus spline of compound cross bar is connected with an end of back solid drive shafts; One end of compound unofficial biography powershift gear is tapered gear and outer planet finishing bevel gear cuter constant-mesh, its other end is unidirectional power transmission tooth and the interlock of internal overrunning coupler ring, one end of compound power transmission gear ring is tapered gear and outer planet finishing bevel gear cuter constant-mesh, and its other end is unidirectional power transmission tooth and the interlock of outer overriding clutch ring; Inner planet finishing bevel gear cuter and compound interior power transmission gear constant-mesh, it is a rigid body that compound interior power transmission gear and intermediary's axle side gear are connected by the spline hollow shaft; Middle poor bevel planet gear constant-mesh among intermediary's axle side gear and the diff D of intermediary, middle poor bevel planet gear among the diff D of intermediary and two-sided finishing bevel gear cuter constant-mesh; Two-sided finishing bevel gear cuter again with back diff C in back bevel planet gear constant-mesh, the back bevel planet gear among the back diff C again with back hollow half axle gear mesh;
The diff D of intermediary by middle poor cross frame with in being sleeved on difference on the cross frame middle poor bevel planet gear and constituted with the intermediary's axle side gear and the two-sided finishing bevel gear cuter of middle poor bevel planet gear constant-mesh, in the difference cross frame be fixed on the half-rear axle gear ring among the interaxle differential A, with the shared housing of back diff C; Two-sided finishing bevel gear cuter promptly is the end axle side gear of the diff D of intermediary, is again the axle side gear of back diff C, and is fixed together with the back solid drive shafts; Then the compound cross bar among an end of solid drive shafts and the anti-skidding composite differential E is affixed is a rigid body;
Power-transfer clutch H is positioned at the front portion of interaxle differential A, and be provided with the square tooth of clutch at the front end of the housing of interaxle differential A, the tail end of the half front axle gear ring in interaxle differential A is provided with spline, power-transfer clutch H is sleeved on the spline, and the square tooth of clutch of the front end setting of the housing among power-transfer clutch H and the interaxle differential A is separated or interlock by the external force effect.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100625064A CN101905651A (en) | 2009-06-07 | 2009-06-07 | Differential-twist driving device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100625064A CN101905651A (en) | 2009-06-07 | 2009-06-07 | Differential-twist driving device |
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| Publication Number | Publication Date |
|---|---|
| CN101905651A true CN101905651A (en) | 2010-12-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009100625064A Pending CN101905651A (en) | 2009-06-07 | 2009-06-07 | Differential-twist driving device |
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| CN (1) | CN101905651A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102529578A (en) * | 2012-01-14 | 2012-07-04 | 郭保可 | Rear drive axle for paddy field machinery |
| CN102889358A (en) * | 2012-09-29 | 2013-01-23 | 盛阳 | Novel differential |
| CN104421380A (en) * | 2013-08-28 | 2015-03-18 | 阿文美驰技术有限责任公司 | Method of making a bevel gear system |
| CN107420517A (en) * | 2017-08-15 | 2017-12-01 | 十堰戎马汽车特种传动有限公司 | Rear wheel independent suspension vibration absorber in automobile |
| CN107757356A (en) * | 2017-11-07 | 2018-03-06 | 北京博格华纳汽车传动器有限公司 | A kind of automobile-used decelerator with differential lock |
| CN110410479A (en) * | 2019-07-03 | 2019-11-05 | 南昌大学 | A kind of superposition output transmission of different rotating speeds input |
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| US20030203783A1 (en) * | 2002-04-26 | 2003-10-30 | Sullivan William C. | Forward carrier assembly for tandem axle |
| CN201784461U (en) * | 2009-06-07 | 2011-04-06 | 周殿玺 | Differential torque transmission device |
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| DE10001842A1 (en) * | 1999-02-11 | 2000-08-17 | Meritor Heavy Vehicle Sys Ltd | Tandem drive unit for motor vehicles has front drive with interaxle differential with pair of external side gearwheels, primary differential and hollow pinion, and rear drive with rear pinion and rear differential |
| CN1397445A (en) * | 2001-07-13 | 2003-02-19 | 周殿玺 | Frequently interlocked universal differential driver |
| US20030203783A1 (en) * | 2002-04-26 | 2003-10-30 | Sullivan William C. | Forward carrier assembly for tandem axle |
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Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102529578A (en) * | 2012-01-14 | 2012-07-04 | 郭保可 | Rear drive axle for paddy field machinery |
| CN102529578B (en) * | 2012-01-14 | 2013-12-11 | 潍坊同方机械有限公司 | Rear drive axle for paddy field machinery |
| CN102889358A (en) * | 2012-09-29 | 2013-01-23 | 盛阳 | Novel differential |
| CN102889358B (en) * | 2012-09-29 | 2015-04-22 | 盛阳 | Novel differential |
| CN104421380A (en) * | 2013-08-28 | 2015-03-18 | 阿文美驰技术有限责任公司 | Method of making a bevel gear system |
| CN104421380B (en) * | 2013-08-28 | 2017-04-12 | 阿文美驰技术有限责任公司 | Method of making a bevel gear system |
| CN107420517A (en) * | 2017-08-15 | 2017-12-01 | 十堰戎马汽车特种传动有限公司 | Rear wheel independent suspension vibration absorber in automobile |
| CN107420517B (en) * | 2017-08-15 | 2023-11-07 | 十堰戎马汽车特种传动有限公司 | Independent suspension vibration damper for middle and rear wheels of automobile |
| CN107757356A (en) * | 2017-11-07 | 2018-03-06 | 北京博格华纳汽车传动器有限公司 | A kind of automobile-used decelerator with differential lock |
| CN107757356B (en) * | 2017-11-07 | 2023-12-19 | 北京博格华纳汽车传动器有限公司 | Speed reducer with differential lock for vehicle |
| CN110410479A (en) * | 2019-07-03 | 2019-11-05 | 南昌大学 | A kind of superposition output transmission of different rotating speeds input |
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Application publication date: 20101208 |