CN102384240B - Infinitely variable speed self-locking differential - Google Patents
Infinitely variable speed self-locking differential Download PDFInfo
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- CN102384240B CN102384240B CN201110204346.XA CN201110204346A CN102384240B CN 102384240 B CN102384240 B CN 102384240B CN 201110204346 A CN201110204346 A CN 201110204346A CN 102384240 B CN102384240 B CN 102384240B
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Abstract
The invention discloses an infinitely variable speed self-locking differential, aiming to provide the infinitely variable speed self-locking differential which has an anti-skidding self-locking function, and simultaneously not only can carry out passive differential, but also can carry out active differential. The self-locking differential comprises a driving shaft, a left driven shaft, a right driven shaft and a differential regulating rod with parallel arranged axes; two V-shaped metal belts are bridged with V-shaped grooves on the left driven shaft, the right driven shaft and the driving shaft; the axes of the left driven shaft and the right driven shaft are collinear; the left end of the right driven shaft is inserted into an inner hole of the left driven shaft through the support of a needle roller bearing; the left driven shaft is connected with a spline of a left half shaft; the right driven shaft is connected with a spline of the right half shaft; a left driving fixed plate and a right driving fixed plate, a left driving shift plate and a right driving shift plate, a left pretightening spring and a right pretightening spring as well as two spring seats and two locking nuts are symmetrically arranged on the driving shaft; the left driven shaft is provided with a left driven fixed plate and a left driven shift plate; the right driven shaft is provided with a right driven fixed plate and a right driven shift plate; and a thrust bearing is arranged between the left driven shift plate and the right driven shift plate.
Description
Technical field
The present invention relates to a kind of differential mechanism, particularly a kind of initiatively stepless speed change type no-spin lockup of differential, passive differential and self-locking skidproof function that has that adopts stepless speed changes devices, belongs to technical field of automobile parts.
Background technique
The function of differential mechanism is in the time that automobile turning travels or travel on uneven road surface, left and right driving wheel is rolled, to ensure two side drive wheels and ground intercropping PURE ROLLING with different angular velocity.The differential mechanism using at present mainly comprises Symmetric Cone compensating gear and limited slip differential.
Symmetric Cone compensating gear is made up of planetary pinion, planet pin, differential gear and differential carrier etc., pass to differential carrier, planet pin, planetary pinion and differential gear from the power of main reducing gear, reach driving wheel through left and right two-semiaxle again, according to left and right two differences that drive wheel to meet obstructions, Symmetric Cone compensating gear can make left and right two to drive wheel constant speed to rotate or variable speed rotation.The defect of Symmetric Cone compensating gear is: the automobile of assembling Symmetric Cone compensating gear effect when straight line or turning driving in good road surface is satisfactory, but while travelling on bad road surface, while differing greatly due to the condition of adhering between driving wheels and ground, one side is adhered to the poor driving wheel of condition can produce skid, the driving wheel that it is good that opposite side adheres to condition stops operating, and therefore automobile cannot advance.
In order to improve the passing capacity of automobile, a side drive vehicle wheel rotational speed that solves the existence of Symmetric Cone compensating gear is the problem that zero-sum opposite side drives wheel fast idle, on differential mechanism, increase anti-skidding self-locking device, occurred comprising the limited slip differential of the multiple patterns such as locking differential, high friction self-locking formula differential mechanism, dental formula differential, Torsen differential mechanism, viscosity connecting shaft differential mechanism.In the time of a side drive wheel-slip, limited slip differential limits by anti-slipping mechanism or stops differential working procedure, limit the driving vehicle wheel rotation of skid with this, most of or whole driving moments are passed on to non-slip driving wheel, make automobile running to utilize non-slip driving wheel to produce enough driving moments.The defect of limited slip differential is: existing limited slip differential all belongs to passive type differential mechanism, can only carry out passive differential in the size of road surface turning driving radius according to driving wheel, and can not ensure to carry out active differential according to the corner displacement of automotive steering structure in realizing anti-skidding self-locking.
Summary of the invention
The object of the invention is to overcome the deficiencies in the prior art, a kind of stepless speed change type no-spin lockup that not only can carry out passive differential when having anti-skidding auto-lock function but also can carry out differential initiatively simultaneously having concurrently speed changing function is provided.This device adopts the stepless speed changing mechanism being made up of driving shaft, driven shaft, metal cone dish and metal tape (or belt) and the principal moment being made up of differential adjustable lever, shift fork and shift fork head speed controlling mechanism to combine, carry out differential and anti-skidding self-locking work, and by left and right half by transmission of power to automobile two side drive wheel, can carry out passive differential and anti-skidding self-locking work after cancelling principal moment speed controlling mechanism.
Working principle of the present invention is: driving force inputs to the driving shaft 1 being connected with cone gear 9 by two semicircle lands 8 through cone gear 9, make driving shaft 1 obtain powered rotation, and the rotating speed of driving shaft 1 is N; The power of driving shaft 1 passes to right driven shaft 13 ＇ by the right main V-shaped groove V1 of cross-over connection and the right side from right V-arrangement metal tape 10 ＇ of V-shaped groove V2, make right driven shaft 13 ＇ and obtain powered rotation with right axle shaft 12 ＇ of its spline joint, the rotating speed of right driven shaft 13 ＇ and right axle shaft 12 ＇ is N1, and right axle shaft 12 ＇ drive wheel by transmission of power to right side; Simultaneously, the power of driving shaft 1 passes to left driven shaft 13 by the left main V-shaped groove V4 of cross-over connection and a left side from the left V-arrangement metal tape 10 of V-shaped groove V3, make left driven shaft 13 and obtain powered rotation with the left half axle 12 of its spline joint, the rotating speed of left driven shaft 13 and left half axle 12 is N2, and left half axle 12 drives wheel by transmission of power to left side.According to the belt wheel transmission principle in mechanical transmission theory, driven rotating speed equals driven radius and the inverse ratio that initiatively engages radius of engaging with the ratio of active rotating speed, obtain N1=N(R1/R2), N2=N(R4/R3), in formula, R1 is right V-arrangement metal tape 10 ＇ and the radius that engages of right main V-shaped groove V1, R2 is left V-arrangement metal tape 10 ＇ and the right radius that engages from V-shaped groove V2, R3 is left V-arrangement metal tape 10 and the left radius that engages from V-shaped groove V3, and R4 is left V-arrangement metal tape 10 and the radius that engages of left main V-shaped groove V4.According to the relation of above-mentioned N1 and N2 and N, can obtain following result: in the time of R1=R2=R3=R4, N1=N2=N, now differential mechanism is carried out constant speed work; In the time of R1/R2 ≠ R4/R3, N1 ≠ N2, now differential mechanism is carried out differential work; In the time of R1/R2 ≠ R4/R3 ≠ 0, N1 ≠ N2 ≠ 0, now differential mechanism is carried out anti-skidding self-locking work.
According to stepless change theory, because the length of metal tape is fixed, when R2 increases or reduces, R1 must reduce or increase, and R2 and R1 are inverse relation; When R3 increases or reduces, R4 must reduce or increase, and R3 and R4 are inverse relation.The molded breadth of engagement radius and the V-shaped groove relation that is inversely proportional to, i.e. the molded breadth L1 of right main V-shaped groove V1 increase or while reducing, R1 reduces or increases; When the right molded breadth L2 from V-shaped groove V2 increases or reduces, R2 reduces or increases; When the left molded breadth L3 from V-shaped groove V3 increases or reduces, R3 reduces or increases; When the molded breadth L4 of left main V-shaped groove V4 increases or reduces, R4 reduces or increases.Because a left side is integrated part from fixed tray 15 and left driven shaft 13, the right side is integrated part from fixed tray 15 ＇ and right driven shaft 13 ＇, so a left side is fixed value from fixed tray 15 and the right side from the molded breadth L between fixed tray 15 ＇.Meanwhile, left is also fixed value from displacement disc 16 and the right side from the mobile molded breadth L0 facing left between 16 ＇.Because L=L0+L2+L3, and L and L0 be fixed value, so L2 and L3 are inverse relation.
Differential mechanism electronic control system regulates power F according to the corner displacement of steering equipment, power F promotes differential adjustable lever 18 and moves axially, left shift fork head 22 on differential adjustable lever 18 and right shift fork head 22 ＇ can promote respectively left from displacement disc 16, left bearing seat ring 21, thrust-bearing 17, right bearing seat ring 21 ＇ and right from moving the 16 ＇ integral left of facing left, moving right, and L2 and L3 size are changed; Due to the inverse relation of engagement radius and V-shaped groove molded breadth, L2 and the change of L3 size cause R2 and R3 that size change also occurs; Due to the inverse relation between engagement radius, R2 and the change of R3 size cause R1 and R4 that size change also occurs.Above process finally causes the relationship change of R1/R2 and R4/R3, and the relation of N1, N2 and N is changed, thereby realizes the various working procedure under the active mode of this device, its essence is the relation that is changed N1, N2 and N by the size variation of L2 and L3.
On the basis of active differential structure, cancel differential adjustable lever 18, shift fork 20, left shift fork head 22, right shift fork head 22 ＇ and adjustable lever bearing 19, other part remains unchanged, and can be changed into the stepless speed change type differential mechanism under passive differential pattern.Left half axle 12 acquisition left sides in device after variation drive the rotational speed N 2 of wheel and pass to left driven shaft 13, and right axle shaft 12 ＇ obtain right sides and drive the rotational speed N 1 of wheels also to pass to right driven shaft 13 ＇, and the rotating speed that driving shaft 1 obtains power source driving is N.Carry out the passive adjusting each size that engage radius with the inverse relation and the engagement radius that engage the equation relation of radius and engage between radius with the molded breadth of the V-shaped groove relation that is inversely proportional to according to rotating speed, the big or small change of engagement radius makes differential mechanism can ensure that passive differential regulates, and its essence is by the relationship change of N1, N2 and N and comes passive change R1 and the variation relation of R2 and R4 and R3.
Speed changing function can be realized by changing the outside dimension of initial disk and changing two kinds of modes of initial L0 length, change the outside dimension of initial disk and change initial L0 length and finally make each engagement change in radius, in the time of R4=R1 < R3=R2, N > N1=N2, has reduction of speed function; In the time of R4=R1 > R3=R2, N1=N2 > N, has raising speed function.
The present invention is achieved by following technical proposals:
A kind of stepless speed change type no-spin lockup, it comprises the driving shaft 1 being arranged in parallel with left driven shaft 13 and right driven shaft 13 ＇ axis, left main fixed tray 7 ＇ and right main fixed tray 7 on driving shaft 1, are arranged symmetrically with, left main displacement disc 6 ＇ and right main displacement disc 6, left preloading spring 5 ＇ and right preloading spring 5, left spring seat 4 ＇ and right spring seat 4 and left locking nut 3 ＇ and right locking nut 3, left main displacement disc 6 ＇ and right main displacement disc 6 also can move axially along driving shaft 1 with driving shaft 1 spline joint, right spring seat 4 and left spring seat 4 ＇ and driving shaft 1 spline joint, left preloading spring 5 ＇ are between left spring seat 4 ＇ and left main displacement disc 6 ＇, right preloading spring 5 is between right spring seat 4 and right main displacement disc 6, left main fixed tray 7 ＇ are connected with cone gear 9 by two semicircle lands 8, the axis of the axis of described left driven shaft 13 and right driven shaft 13 ＇ is on same straight line, the left end of right driven shaft 13 ＇ inserts by the support of needle bearing 11 in the endoporus of left driven shaft 13, left driven shaft 13 and left half axle 12 spline joints, right driven shaft 13 ＇ and right axle shaft 12 ＇ spline joints, on left driven shaft 13, be furnished with left from fixed tray 15 and left from displacement disc 16, a left side also can move axially along left driven shaft 13 from displacement disc 16 and left driven shaft 13 spline joints, on right driven shaft 13 ＇, be furnished with right from fixed tray 15 ＇, right from displacement disc 16 ＇, the right side also can move axially along right driven shaft 13 ＇ from displacement disc 16 ＇ and right driven shaft 13 ＇ spline joints, a left side is left bearing seat ring 21 from the right-hand member of displacement disc 16, the right side is right bearing seat ring 21 ＇ from the left end of displacement disc 16 ＇, thrust-bearing 17 is between left bearing seat ring 21 and right bearing seat ring 21 ＇, described left main fixed tray 7 ＇ and left main displacement disc 6 ＇ form left main V-shaped groove V4, right main fixed tray 7 and right main displacement disc 6 form right main V-shaped groove V1, left from fixed tray 15 and left left from V-shaped groove V3 from displacement disc 16 formation, the right side forms right from V-shaped groove V2 from fixed tray 15 ＇ and the right side from displacement disc 16 ＇, left V-arrangement metal tape 10 cross-over connection left sides are from V-shaped groove V3 and left main V-shaped groove V4, the right main V-shaped groove V1 of right V-arrangement metal tape 10 ＇ cross-over connection and right from V-shaped groove V2, differential adjustable lever 18 is through the metal strip loop of left V-arrangement metal tape 10 and right V-arrangement metal tape 10 ＇, the axis of differential adjustable lever 18 and driving shaft 1, left driven shaft 13 is parallel with the axis of right driven shaft 13 ＇, on differential adjustable lever 18, be provided with shift fork 20, the left shift fork head 22 of shift fork 20 on a left side between displacement disc 16 and left bearing seat ring 21, and between left shift fork head 22 and left bearing seat ring 21 exterior edge faces, be the smooth matching relationship of relative movement, right shift fork head 22 ＇ on the right side between displacement disc 16 ＇ and right bearing seat ring 21 ＇, it between right shift fork head 22 ＇ and right bearing seat ring 21 ＇ exterior edge faces, is also the smooth matching relationship of relative movement, the smooth matching relationship of its relative movement is in order to transmit the F thrust from adjustable lever 18 left and right directions, not only can transmitting thrust F but also can keep relative movement between two parts.
Described left main fixed tray 7 ＇ and right main fixed tray 7 are integrated part with driving shaft 1, and a left side is integrated part from fixed tray 15 and left driven shaft 13, and the right side is integrated part from fixed tray 15 ＇ and right driven shaft 13 ＇; Described driving shaft 1 is supported on differential casing by the deep groove ball bearing 2 that is positioned at driving shaft 1 two ends, left driven shaft 13 and right driven shaft 13 ＇ are supported on differential casing by the circular cone roller bearing 14 of outer end separately, and differential adjustable lever 18 is supported on differential casing by the adjustable lever bearing 19 at its two ends; Described driving shaft 1 both can be connected with power source and be obtained motivational drive by cone gear 9, also can adopt key Placement to obtain motivational drive by the axle head at driving shaft 1; Described left half axle 12 is for connecting automobile left driving wheel, and right axle shaft 12 ＇ are used for connecting Automobile Right driving wheel; The existence of described differential adjustable lever 18, shift fork 20, left shift fork head 22, right shift fork head 22 ＇ and adjustable lever bearing 19, can realize principal moment velocity modulation joint, cancel differential adjustable lever 18, shift fork 20, left shift fork head 22, right shift fork head 22 ＇ and adjustable lever bearing 19, can realize passive differential and regulate; Described left V-arrangement metal tape 10 and right V-arrangement metal tape 10 ＇ also can be replaced by vee-belt.
The invention has the beneficial effects as follows: (1) adopts the stepless speed changing mechanism being made up of driving shaft, driven shaft, metal cone dish and metal tape (or belt) to realize the stepless speed regulation of differential process, has improved the continuity of differential process; (2) when thering is anti-skidding auto-lock function, can carry out active differential according to the corner displacement of automotive steering structure; (3) both can also can, for passive differential, have speed changing function concurrently, applied range for principal moment speed simultaneously; (4) simple in structure, cost of production is low.
Brief description of the drawings
Fig. 1 is initiatively differential structural representation of stepless speed change type no-spin lockup;
Fig. 2 is the passive differential structural representation of stepless speed change type no-spin lockup;
Fig. 3 is initiatively differential A-A sectional view of stepless speed change type no-spin lockup;
Fig. 4 is the passive differential B-B of stepless speed change type no-spin lockup sectional view;
Fig. 5 is the driving shaft structural representation that adopts the input of cone gear power;
Fig. 6 is the driving shaft structural representation that adopts the input of axle head power;
Fig. 7 is driven shaft structural representation;
Fig. 8 is stepless speed change type no-spin lockup left-hand rotation differential principle figure;
Fig. 9 is stepless speed change type no-spin lockup right-hand rotation differential principle figure.
In figure: 1. right locking nut 3 ＇ of driving shaft 2. deep groove ball bearing 3.. right spring seat 4 ＇ of left locking nut 4.. right preloading spring 5 ＇ of left spring seat 5.. right main displacement disc 6 ＇ of left preloading spring 6.. right main fixed tray 7 ＇ of left main displacement disc 7.. left V-arrangement metal tape 10 ＇ of left main fixed tray 8. semicircle land 9. cone gear 10.. right V-arrangement metal tape 11. needle bearing 12. left half axle 12 ＇. left driven shaft 13 ＇ of right axle shaft 13.. right driven shaft 14. circular cone roller bearing 15. left sides are from fixed tray 15 ＇. and right from fixed tray 16. left sides from displacement disc 16 ＇. right from displacement disc 17. thrust-bearing 18. differential adjustable lever 19. adjustable lever bearing 20. shift fork 21. left bearing seat ring 21 ＇. left shift fork head 22 ＇ of right bearing seat ring 22.. right shift fork head
V1. right main V-shaped groove, the V2. right side are from V-shaped groove, a V3. left side from V-shaped groove, the left main V-shaped groove of V4.
Embodiment
Further illustrate with reference to the accompanying drawings particular content of the present invention and embodiment thereof.
Fig. 1 is initiatively differential structural representation of stepless speed change type no-spin lockup, Fig. 3 is initiatively differential A-A sectional view of stepless speed change type no-spin lockup, driving shaft 1 is arranged in parallel with left driven shaft 13 and right driven shaft 13 ＇ axis, the axis of the axis of left driven shaft 13 and right driven shaft 13 ＇ is on same straight line, the left end of right driven shaft 13 ＇ inserts by the support of needle bearing 11 in the endoporus of left driven shaft 13, left driven shaft 13 and left half axle 12 spline joints, right driven shaft 13 ＇ and right axle shaft 12 ＇ spline joints.
Left main fixed tray 7 ＇ and right main fixed tray 7, left main displacement disc 6 ＇ and right main displacement disc 6, left preloading spring 5 ＇ and right preloading spring 5, left spring seat 4 ＇ and right spring seat 4 and left locking nut 3 ＇ and right locking nut 3 are arranged symmetrically with on driving shaft 1, left main fixed tray 7 ＇ and right main fixed tray 7 are integrated part with driving shaft 1, left main displacement disc 6 ＇ and right main displacement disc 6 also can move axially along driving shaft 1 with driving shaft 1 spline joint, the large I of spring force of left preloading spring 5 ＇ and right preloading spring 5 regulates through left locking nut 3 ＇ and right locking nut 3 respectively, right spring seat 4 and left spring seat 4 ＇ and driving shaft 1 spline joint, can prevent adjusting lock nut time, spring seat rotates with locking nut, left preloading spring 5 ＇ are between left spring seat 4 ＇ and left main displacement disc 6 ＇, right preloading spring 5 is between right spring seat 4 and right main displacement disc 6, left main fixed tray 7 ＇ are connected with cone gear 9 by land 8, driving shaft 1 is connected with power source and is obtained power by cone gear 9.
On left driven shaft 13, be furnished with left from fixed tray 15 and left from displacement disc 16, a left side is integrated part from fixed tray 15 and left driven shaft 13, a left side also can move axially along left driven shaft 13 from displacement disc 16 and left driven shaft 13 spline joints, on right driven shaft 13 ＇, be furnished with right from fixed tray 15 ＇, right from displacement disc 16 ＇, the right side is integrated part from fixed tray 15 ＇ and right driven shaft 13 ＇, the right side also can move axially along right driven shaft 13 ＇ from displacement disc 16 ＇ and right driven shaft 13 ＇ spline joints, a left side is left bearing seat ring 21 from the right-hand member of displacement disc 16, the right side is right bearing seat ring 21 ＇ from the left end of displacement disc 16 ＇, thrust-bearing 17 is between left bearing seat ring 21 and right bearing seat ring 21 ＇, thrust-bearing 17 ensures leftly can relatively rotate and can bearing axial pushing force from displacement disc 16 ＇ with right from displacement disc 16.
Left main fixed tray 7 ＇ and left main displacement disc 6 ＇ form left main V-shaped groove V4, the width of left main V-shaped groove V4 is L4, right main fixed tray 7 and right main displacement disc 6 form right main V-shaped groove V1, the width of right main V-shaped groove V1 is L1, left from fixed tray 15 and left left from V-shaped groove V3 from displacement disc 16 formation, a left side is L3 from the width of V-shaped groove V3, and the right side forms the right side from V-shaped groove V2 from fixed tray 15 ＇ and the right side from displacement disc 16 ＇, and the right side is L2 from the width of V-shaped groove V2.
Left V-arrangement metal tape 10 cross-over connection left sides are from V-shaped groove V3 and left main V-shaped groove V4, left V-arrangement metal tape 10 is R3 with a left side from the radius that engages of V-shaped groove V3, left V-arrangement metal tape 10 is R4 with the radius that engages of left main V-shaped groove V4, the right main V-shaped groove V1 of right V-arrangement metal tape 10 ＇ cross-over connection and right from V-shaped groove V2, right V-arrangement metal tape 10 ＇ are R1 with the radius that engages of right main V-shaped groove V1, right V-arrangement metal tape 10 ＇ are R2 with the right side from the radius that engages of V-shaped groove V2, the spring force of left preloading spring 5 ＇ ensures left V-arrangement metal tape 10 and left from V-shaped groove V3 and the tight mesh of left main V-shaped groove V4 and the power of delivery request, the spring force of right preloading spring 5 ensures right V-arrangement metal tape 10 ＇ and right main V-shaped groove V1 and right from the tight mesh of V-shaped groove V2 and the power of delivery request.
Differential adjustable lever 18 is through the metal strip loop of left V-arrangement metal tape 10 and right V-arrangement metal tape 10 ＇, differential adjustable lever 18 is supported on differential casing by the adjustable lever bearing 19 at its two ends, the axis of differential adjustable lever 18 and driving shaft 1, left driven shaft 13 is parallel with the axis of right driven shaft 13 ＇, differential adjustable lever 18 can move along its axis, on differential adjustable lever 18, be provided with shift fork 20, the left shift fork head 22 of shift fork 20 on a left side between displacement disc 16 and left bearing seat ring 21, right shift fork head 22 ＇ on the right side between displacement disc 16 ＇ and right bearing seat ring 21 ＇, when the velocity modulation of being on duty pole 18 moves along its axis left or right under power F effect, left shift fork head 22 and right shift fork head 22 ＇ act on respectively on the outer side surface of left bearing seat ring 21 and right bearing seat ring 21 ＇, in promoting left bearing seat ring 21 or right bearing seat ring 21 ＇, drive left from displacement disc 16, left bearing seat ring 21, thrust-bearing 17, right bearing seat ring 21 ＇ and right from displacement disc 16 ＇ entirety left or move right, power F can be electronic or hydraulic pressure or Mechanical Driven power form, these driving forces are all decided by the corner displacement amount of automotive steering structure, differential mechanism electronic control system regulates size and the movement direction of power F according to the corner displacement of steering equipment, realize the inversely prroportional relationship size that changes L2 and L3.
Fig. 2 is the passive differential structural representation of stepless speed change type no-spin lockup, Fig. 4 is the passive differential B-B of stepless speed change type no-spin lockup sectional view, on the basis of active differential structure, cancel differential adjustable lever 18, shift fork 20, left shift fork head 22, right shift fork head 22 ＇ and adjustable lever bearing 19, other part remains unchanged, and the device after variation is for passive differential.
Fig. 5 is the driving shaft structural representation that adopts the input of cone gear power, left main fixed tray 7 ＇ are connected with cone gear 9 by two semicircle lands 8, driving shaft 1 is connected with power source and is obtained power by cone gear 9, and driving shaft 1 is supported on differential casing by the deep groove ball bearing 2 that is positioned at driving shaft 1 two ends.
Fig. 6 is the driving shaft structural representation that adopts the input of axle head power, and this is the another kind of mode of structure that driving shaft 1 obtains power, and driving shaft 1 adopts key Placement to be connected with power source by its axle head and obtains power.
Fig. 7 is driven shaft structural representation, left driven shaft 13 and right driven shaft 13 ＇ are supported on differential casing by the circular cone roller bearing 14 of outer end separately, left driven shaft 13 and right driven shaft 13 ＇ are subject to the axially support of radial support, needle bearing 11 radial support and the thrust-bearing 17 of circular cone roller bearing 14 simultaneously, and making between left driven shaft 13 and right driven shaft 13 ＇ can separate rotation time again can bearing radial force and axial force; A left side is L0 from displacement disc 16, left bearing seat ring 21, thrust-bearing 17, right bearing seat ring 21 ＇ and the right side from the overall calculation width of displacement disc 16 ＇, and a left side is L from fixed tray 15 and the right side from the molded breadth between fixed tray 15 ＇; Left half axle 12 is for connecting automobile left driving wheel, and right axle shaft 12 ＇ are used for connecting Automobile Right driving wheel.
Fig. 8 is stepless speed change type no-spin lockup left-hand rotation differential principle figure, no matter be while adopting active differential structure or passive differential structure to turn left differential work, relation between engagement radius R 1, R2, R3 and R4 all meets the relation shown in Fig. 8, be that R1 increases, R2 reduces, R3 increases and R4 reduces, between engagement radius, such relation meets N1 > N > N2.
Fig. 9 is stepless speed change type no-spin lockup right-hand rotation differential principle figure, no matter be while adopting active differential structure or passive differential structure to turn right differential work, relation between engagement radius R 1, R2, R3 and R4 all meets the relation shown in Fig. 9, be that R1 reduces, R2 increases, R3 reduces to increase with R4, between engagement radius, such relation meets N2 > N > N1.
Embodiment 1:
Stepless speed change type no-spin lockup active differential and self-locking working procedure are as follows.
Driving shaft 1 is connected with cone gear 9 by land 8, and driving force inputs to driving shaft 1 through cone gear 9, and the rotating speed of driving shaft 1 is N; The power of driving shaft 1 passes to right driven shaft 13 ＇ by the right main V-shaped groove V1 of cross-over connection and the right side from right V-arrangement metal tape 10 ＇ of V-shaped groove V2, make right driven shaft 13 ＇ and obtain powered rotation with right axle shaft 12 ＇ of its spline joint, the rotating speed of right driven shaft 13 ＇ and right axle shaft 12 ＇ is N1, and right axle shaft 12 ＇ drive wheel by transmission of power to right side; Simultaneously, the power of driving shaft 1 passes to left driven shaft 13 by the left main V-shaped groove V4 of cross-over connection and a left side from the left V-arrangement metal tape 10 of V-shaped groove V3, make left driven shaft 13 and obtain powered rotation with the left half axle 12 of its spline joint, the rotating speed of left driven shaft 13 and left half axle 12 is N2, and left half axle 12 drives wheel by transmission of power to left side.
Regulate respectively the initial tension of spring of right preloading spring 5 and left preloading spring 5 ＇ by locking nut 3 and locking nut 3 ＇, make L1=L2=L3=L4, the original state value of each engagement radius is R1=R2=R3=R4, according to N1=N(R1/R2) and N2=N(R4/R3), can obtain N1=N2=N, now differential mechanism is carried out constant speed work.
When automobile turns left, differential mechanism electronic control system regulates power F that differential adjustable lever 18 is axially moved to the left according to the corner displacement of steering equipment, left shift fork head 22 ＇ on differential adjustable lever 18 promote right bearing seat ring 21 ＇ and are moved to the left, thereby drive a left side to be moved to the left from the mobile 16 ＇ entirety of facing left from displacement disc 16, left bearing seat ring 21, thrust-bearing 17, right bearing seat ring 21 ＇ and the right side, because L and L0 are fixed value and L=L0+L2+L3, so L2 increases when causing L3 to reduce.Have inverse relation owing to engaging radius and V-shaped groove molded breadth, so L3 reduces to cause R3 to increase, L2 increase causes R2 to reduce; Be inverse relation because R3 exists R4, cause R4 to reduce so R3 increases; Be inverse relation because R2 exists R1, so R2 reduces to cause R1 to increase.Result after adjusting is that R1 increases, R2 reduces, R3 increases and R4 reduces, because original state is R1=R2=R3=R4, so have R1/R2 > 1 and R4/R3 < 1, simultaneously according to N1=N(R1/R2) and N2=N(R4/R3), can obtain N1 > N and N2 < N, be N1 > N > N2, left side drives vehicle wheel rotational speed to be less than right side and drives vehicle wheel rotational speed, has realized initiatively differential.
When automobile is turned right, differential mechanism electronic control system regulates power F that differential adjustable lever 18 is axially moved right according to the corner displacement of steering equipment, left shift fork head 22 on differential adjustable lever 18 promotes left bearing seat ring 21 and moves right, thereby drive a left side to move right from the mobile 16 ＇ entirety of facing left from displacement disc 16, right bearing seat ring 21, thrust-bearing 17, left bearing seat ring 21 ＇ and the right side, when causing L3 to increase, L2 reduces; Have inverse relation owing to engaging radius and V-shaped groove molded breadth, cause R3 to reduce so L3 increases, L2 reduces to cause R2 to increase; Be inverse relation because R3 exists R4, so R3 reduces to cause R4 to increase; Be inverse relation because R2 exists R1, cause R1 to reduce so R2 increases.Result after adjusting is that R1 reduces, R2 increases, R3 reduces to increase with R4, because original state is R1=R2=R3=R4, so have R1/R2 < 1 and R4/R3 > 1, simultaneously according to N1=N(R1/R2) and N2=N(R4/R3), can obtain N1 < N and N2 > N, be N2 > N > N1, right side drives vehicle wheel rotational speed to be less than left side and drives vehicle wheel rotational speed, has realized the initiatively differential of turning right.
Because the actual size of engagement radius R 1, R2, R3 and R4 can not equal zero also impossible infinitely great, therefore in the time of differential, certainly exist 0 < R1/R2 ≠ R4/R3 <+∞, can obtain 0 < N1 ≠ N2 <+∞, neither fast idle can be not slack yet completely for two side drive wheels, can keep both sides wheel all to there is turning power, realize the anti-skidding self-locking of differential mechanism.
Embodiment 2:
The passive differential of stepless speed change type no-spin lockup and self-locking working procedure are as follows.
Driving shaft 1 is connected with cone gear 9 by land 8, and driving force inputs to driving shaft 1 through cone gear 9, and the rotating speed of driving shaft 1 is N; Left side drives the rotating speed of wheel to pass to and the left driven shaft 13 of left half axle 12 spline joints by left half axle 12, and the rotating speed of left driven shaft 13 is N2; Right side drives the rotating speed of wheel to pass to and right driven shaft 13 ＇ of right axle shaft 12 ＇ spline joints by right axle shaft 12 ＇, and the rotating speed of right driven shaft 13 ＇ is N1.The initial tension of spring that regulates respectively right preloading spring 5 and left preloading spring 5 ＇ by locking nut 3 and locking nut 3 ＇, makes L1=L2=L3=L4, and the original state value that respectively engages radius is R1=R2=R3=R4.
In the time of automobile two side drive wheel constant-speed driving, have N1=N2, according to N1=N(R1/R2) and N2=N(R4/R3), can obtain R1=R2=R3=R4, this original state value that is just engaging radius with differential mechanism is coincide, and now differential mechanism can ensure automobile two side drive wheel constant-speed drivings.
In the time that automobile turns left, left side drives vehicle wheel rotational speed to be less than right side and drives vehicle wheel rotational speed, i.e. N2 < N < N1.Now, the rotational speed N 1 of right driven shaft 13 ＇ is greater than the rotational speed N of driving shaft 1, according to N1=N(R1/R2) > N has R1/R2 > 1, this causes R1 to increase and R2 reduces, R2 reduces to cause L2 to increase, be that the right V-arrangement metal tape 10 ＇ extruding right sides are moved to the left from displacement disc 16 ＇, thereby drive left from displacement disc 16, left bearing seat ring 21, thrust-bearing 17, right bearing seat ring 21 ＇ and the right side are moved to the left from the mobile 16 ＇ entirety of facing left, after mobile, L3 reduces, L3 reduces to cause R3 to increase, be inverse relation because R3 exists R4, so increasing, R3 cause R4 to reduce, result after adjusting is that R1 increases, R2 reduces, R3 increases and R4 reduces.Because original state is R1=R2=R3=R4, engagement radius value after adjusting meets R1/R2 > 1 and R4/R3 < 1, meet N1 > N and N2 < N, ensured automobile left-hand rotation differential.
In the time that automobile is turned right, right side drives vehicle wheel rotational speed to be less than left side and drives vehicle wheel rotational speed, i.e. N1 < N < N2.Now, the rotational speed N 2 of left driven shaft 13 is greater than the rotational speed N of driving shaft 1, according to N2=N(R4/R3) > N has R4/R3 > 1, this causes R4 to increase and R3 reduces, R3 reduces to cause L3 to increase, being that left V-arrangement metal tape 10 extruding are left moves right from displacement disc 16, thereby drive left from displacement disc 16, left bearing seat ring 21, thrust-bearing 17, right bearing seat ring 21 ＇ and the right side move right from the mobile 16 ＇ entirety of facing left, after mobile, L2 reduces, L2 reduces to cause R2 to increase, be inverse relation because R2 exists R1, so increasing, R2 cause R1 to reduce, result after adjusting is that R1 reduces, R2 increases, R3 reduces to increase with R4.Because original state is R1=R2=R3=R4, engagement radius value after adjusting meets R1/R2 < 1 and R4/R3 > 1, meet N1 < N and N2 > N, ensured Automobile Right slip speed.
Because the actual size of engagement radius R 1, R2, R3 and R4 can not equal zero also impossible infinitely great, therefore in the time of differential, certainly exist 0 < R1/R2 ≠ R4/R3 <+∞, can obtain 0 < N1 ≠ N2 <+∞, neither fast idle can be not slack yet completely for two side drive wheels, can keep both sides wheel all to there is turning power, realize the anti-skidding self-locking of differential mechanism.
Embodiment 3:
Stepless speed change type no-spin lockup speed change working procedure is as follows.
Realize speed changing function and comprise outside dimension and two kinds of modes of the initial L0 length of change of changing initial disk.
The outside dimension that changes initial disk is realized speed-change process, the outside dimension of left main fixed tray 7 ＇ and left main displacement disc 6 ＇, right main fixed tray 7 and right main displacement disc 6 is less than left from fixed tray 15 and left from displacement disc 16, right from fixed tray 15 ＇ and the right outside dimension from displacement disc 16 ＇, meeting initial engagement radius relationship is: when R4=R1 < R3=R2, N > N1=N2, has reduction of speed function.
Change initial L0 length and realize speed-change process.Left main fixed tray 7 ＇ and left main displacement disc 6 ＇, right main fixed tray 7 and right main displacement disc 6, left from fixed tray 15 and left from displacement disc 16, the right side all equates from displacement disc 16 ＇ outside dimensions from fixed tray 15 ＇ and the right side, can make respectively the width of L3 and L2 all diminish through increasing L0 length, make respectively left V-arrangement metal tape 10 and right V-arrangement metal tape 10 ＇ all become large from V-shaped groove V3 and the right side from the kneading radius R 3 of V-shaped groove V2 and the radius of R2 with left, then through left V-arrangement metal tape 10 and right V-arrangement metal tape 10 ＇, R4 and R1 are diminished, meeting initial engagement radius relationship is: when R4=R1 < R3=R2, N > N1=N2, there is reduction of speed function, reconcile respectively preloading spring 5 ˊ and the preloading spring 5 initial action power size to left main displacement disc 6 ˊ and right main displacement disc 6 respectively through locking nut 3 ˊ and locking nut 3.
In like manner, reduce L0 length and make respectively L3 and L2 width all become greatly, the radius of R3 and R2 all diminishes, it is large that R4 and R1 become, meeting initial engagement radius relationship is: when R4=R1 > R3=R2, N1=N2 > N, has raising speed function.First reduce L0 length, rear according to transmitted power size conciliation spring 5 ˊ and spring 5 pretightening forces.
Claims (7)
1. a stepless speed change type no-spin lockup, comprise driving shaft, driven shaft, semiaxis and middle speed change gear, it is characterized in that, described driving shaft (1) is arranged in parallel with left driven shaft (13) and right driven shaft (13 ＇) axis, left main fixed tray (7 ＇) and right main fixed tray (7) on driving shaft (1), are arranged symmetrically with, left main displacement disc (6 ＇) and right main displacement disc (6), left preloading spring (5 ＇) and right preloading spring (5), left spring seat (4 ＇) and right spring seat (4) and left locking nut (3 ＇) and right locking nut (3), left main displacement disc (6 ＇) and right main displacement disc (6) also can move axially along driving shaft (1) with driving shaft (1) spline joint, right spring seat (4) and left spring seat (4 ＇) and driving shaft (1) spline joint, left preloading spring (5 ＇) is positioned between left spring seat (4 ＇) and left main displacement disc (6 ＇), right preloading spring (5) is positioned between right spring seat (4) and right main displacement disc (6), left main fixed tray (7 ＇) is connected with cone gear (9) by two semicircle lands (8), the axis of the axis of described left driven shaft (13) and right driven shaft (13 ＇) is on same straight line, the left end of right driven shaft (13 ＇) inserts in the endoporus of left driven shaft (13) by the support of needle bearing (11), left driven shaft (13) and left half axle (12) spline joint, right driven shaft (13 ＇) and right axle shaft (12 ＇) spline joint, on left driven shaft (13), be furnished with left from fixed tray (15) and left from displacement disc (16), a left side also can move axially along left driven shaft (13) from displacement disc (16) and left driven shaft (13) spline joint, on right driven shaft (13 ＇), be furnished with right from fixed tray (15 ＇), right from displacement disc (16 ＇), the right side also can move axially along right driven shaft (13 ＇) from displacement disc (16 ＇) and right driven shaft (13 ＇) spline joint, a left side is left bearing seat ring (21) from the right-hand member of displacement disc (16), the right side is right bearing seat ring (21 ＇) from the left end of displacement disc (16 ＇), thrust-bearing (17) is positioned between left bearing seat ring (21) and right bearing seat ring (21 ＇), the left main V-shaped groove of left V-arrangement metal tape (10) cross-over connection (V4) and left from V-shaped groove (V3), left main V-type groove (V4) is by forming between left main fixed tray (7 ＇) and left main displacement disc (6 ＇), a left side is formed between displacement disc (16) from fixed tray (15) and a left side by a left side from V-type groove (V3), right V-arrangement metal tape (10 ＇) the right main V-shaped groove of cross-over connection (V1) and right from V-shaped groove (V2), right main V-type groove (V1) is by forming between right main fixed tray (7) and right main displacement disc (6), the right side is formed between displacement disc (16 ＇) from fixed tray (15 ＇) and the right side by the right side from V-type groove (V2), differential adjustable lever (18) is through the metal strip loop of left V-arrangement metal tape (10) and right V-arrangement metal tape (10 ＇), the axis of differential adjustable lever (18) and driving shaft (1), left driven shaft (13) is parallel with the axis of right driven shaft (13 ＇), on differential adjustable lever (18), be provided with shift fork (20), the left shift fork head (22) of shift fork (20) is positioned at left between displacement disc (16) and left bearing seat ring (21), it between left shift fork head (22) and left bearing seat ring (21) exterior edge face, is the smooth matching relationship of relative movement, right shift fork head (22 ＇) is positioned at right between displacement disc (16 ＇) and right bearing seat ring (21 ＇), it between right shift fork head (22 ＇) and right bearing seat ring (21 ＇) exterior edge face, is the smooth matching relationship of relative movement.
2. a kind of stepless speed change type no-spin lockup according to claim 1, it is characterized in that, described left main fixed tray (7 ＇) and right main fixed tray (7) are integrated part with driving shaft (1), a left side is integrated part from fixed tray (15) and left driven shaft (13), and the right side is integrated part from fixed tray (15 ＇) and right driven shaft (13 ＇).
3. a kind of stepless speed change type no-spin lockup according to claim 1, it is characterized in that, described driving shaft (1) is supported on differential casing by the deep groove ball bearing (2) that is positioned at driving shaft (1) two ends, left driven shaft (13) and right driven shaft (13 ＇) are supported on differential casing by the circular cone roller bearing (14) of outer end separately, and differential adjustable lever (18) is supported on differential casing by the adjustable lever bearing (19) at its two ends.
4. a kind of stepless speed change type no-spin lockup according to claim 1, it is characterized in that, described driving shaft (1) both can pass through cone gear (9) and be connected acquisition motivational drive with power source, also can adopt key Placement to obtain motivational drive by the axle head at driving shaft (1).
5. a kind of stepless speed change type no-spin lockup according to claim 1, is characterized in that, described left half axle (12) is for connecting automobile left driving wheel, and right axle shaft (12 ＇) is for connecting Automobile Right driving wheel.
6. a kind of stepless speed change type no-spin lockup according to claim 3, it is characterized in that, the existence of described differential adjustable lever (18), shift fork (20), left shift fork head (22), right shift fork head (22 ＇) and adjustable lever bearing (19), can realize principal moment velocity modulation joint; Cancel differential adjustable lever (18), shift fork (20), left shift fork head (22), right shift fork head (22 ＇) and adjustable lever bearing (19), can realize passive differential and regulate.
7. a kind of stepless speed change type no-spin lockup according to claim 1, is characterized in that, described left V-arrangement metal tape (10) and right V-arrangement metal tape (10 ＇) also can be replaced by vee-belt.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201110204346.XA CN102384240B (en) | 2011-07-21 | 2011-07-21 | Infinitely variable speed self-locking differential |
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| CN201110204346.XA CN102384240B (en) | 2011-07-21 | 2011-07-21 | Infinitely variable speed self-locking differential |
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| CN102384240B true CN102384240B (en) | 2014-07-09 |
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| CN201110204346.XA Expired - Fee Related CN102384240B (en) | 2011-07-21 | 2011-07-21 | Infinitely variable speed self-locking differential |
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| CN104747693A (en) * | 2013-12-26 | 2015-07-01 | 上海法赫桥梁隧道养护工程技术有限公司 | Power distribution device |
| CN112828095B (en) * | 2020-12-27 | 2023-03-28 | 河北华通重工机械制造有限公司 | Veneer reeling machine for machining |
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| FR2583127A1 (en) * | 1985-06-10 | 1986-12-12 | Monge Robert | Trapezoidal-belt drive device of the differential type |
| US5085107A (en) * | 1989-09-18 | 1992-02-04 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling hydraulically operated continuously variable vehicle transmission, having means for changing power transmitting capacity with input torque |
| CN201457046U (en) * | 2009-05-21 | 2010-05-12 | 蔡剑平 | Gear change mechanism of transporter |
| CN101718337A (en) * | 2009-12-22 | 2010-06-02 | 吉林大学 | Electricity-liquid integration control device for metal belt continuously variable transmission |
| CN101886696A (en) * | 2010-07-01 | 2010-11-17 | 吉林大学 | Differential and integral type differential power coupling device |
| CN201651201U (en) * | 2010-04-13 | 2010-11-24 | 吉林大学 | Metal toothed belt type stepless transmission |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080207363A1 (en) * | 2007-02-23 | 2008-08-28 | Gm Global Technology Operations, Inc. | Low cost torque vectoring system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2582966A (en) * | 1947-09-23 | 1952-01-22 | George W Curtis | Tractor having v-belt pulley control |
| FR2583127A1 (en) * | 1985-06-10 | 1986-12-12 | Monge Robert | Trapezoidal-belt drive device of the differential type |
| US5085107A (en) * | 1989-09-18 | 1992-02-04 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling hydraulically operated continuously variable vehicle transmission, having means for changing power transmitting capacity with input torque |
| CN201457046U (en) * | 2009-05-21 | 2010-05-12 | 蔡剑平 | Gear change mechanism of transporter |
| CN101718337A (en) * | 2009-12-22 | 2010-06-02 | 吉林大学 | Electricity-liquid integration control device for metal belt continuously variable transmission |
| CN201651201U (en) * | 2010-04-13 | 2010-11-24 | 吉林大学 | Metal toothed belt type stepless transmission |
| CN101886696A (en) * | 2010-07-01 | 2010-11-17 | 吉林大学 | Differential and integral type differential power coupling device |
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