CN102384240A - Infinitely variable speed self-locking differential - Google Patents
Infinitely variable speed self-locking differential Download PDFInfo
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- CN102384240A CN102384240A CN201110204346XA CN201110204346A CN102384240A CN 102384240 A CN102384240 A CN 102384240A CN 201110204346X A CN201110204346X A CN 201110204346XA CN 201110204346 A CN201110204346 A CN 201110204346A CN 102384240 A CN102384240 A CN 102384240A
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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 when automobile turning goes or on uneven road surface, go, and the left and right driving wheel is rolled with different angular velocity, to guarantee both sides driving wheel and ground intercropping PURE ROLLING.The differential mechanism that uses at present mainly comprises symmetrical bevel differential and limited slip differential.
The symmetry bevel differential 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 the difference that left and right two driving wheel meet obstructions, symmetrical bevel differential is rotated by left and right two driving wheel constant speed or variable speed rotates.The defective of symmetry bevel differential is: the automobile that assembles symmetrical bevel differential effect when straight line or turning driving on good road surface is satisfactory; But when on bad road surface, going; Because when the condition of adhering between right wheels and the ground differs greatly; One side is adhered to the relatively poor driving wheel of condition can produce skid, and the driving wheel that it is good that opposite side adheres to condition then stops operating, and therefore automobile can't advance.
In order to improve the passing capacity of automobile; A side drive vehicle wheel rotational speed that solves symmetrical bevel differential existence is the problem of zero-sum opposite side driving wheel fast idle; On differential mechanism, increase anti-skidding self-locking device, the limited slip differential of multiple patterns such as locking differential, high friction self-locking formula differential mechanism, dental formula differential, Torsen differential mechanism, viscosity connecting shaft differential mechanism occurred comprising.When a side drive wheel-slip; Limited slip differential is through anti-skidding mechanics limit or stop the differential working procedure; Rotate with this driving wheel that limits skid; 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 defective of limited slip differential is: existing limited slip differential all belongs to the passive type differential mechanism; Can only carry out passive differential according to the size of driving wheel turning driving radius, and can not guarantee that the corner displacement according to automotive steering structure carries out the active differential when realizing anti-skidding self-locking on the road surface.
Summary of the invention
The objective of the invention is to overcome the deficiency of existing technology, provide a kind of and not only can carry out passive differential when having anti-skidding auto-lock function but also can carry out the stepless speed change type no-spin lockup that differential initiatively has speed changing function simultaneously concurrently.This device adopts stepless speed changing mechanism of being made up of driving shaft, driven shaft, metal awl dish and metal tape (or belt) and the principal moment velocity modulation of being made up of differential adjustable lever, shift fork and shift fork head to save mechanism and combines; Carry out differential and anti-skidding self-locking work; And pass through left and right half and give automobile two side drive wheel with transmission of power, then can carry out passive differential and anti-skidding self-locking work after the cancellation principal moment velocity modulation joint mechanism.
Working principle of the present invention is: driving force inputs to the driving shaft 1 that is connected with cone gear 9 through two semicircle lands 8 through cone gear 9, makes driving shaft 1 rotation that gains impetus, and the rotating speed of driving shaft 1 is N; The right driven shaft 13 of the V-arrangement metal tape 10 of the power of driving shaft 1 through cross-over connection V-shaped groove V1 and V-shaped groove V2 ' pass to '; Make right driven shaft 13 ' with the right axle shaft 12 that is connected with its spline ' rotation gains impetus; Right driven shaft 13 ' with right axle shaft 12 ' rotating speed be N1, right axle shaft 12 ' give the right side driving wheel with transmission of power; Simultaneously; The power of driving shaft 1 passes to left driven shaft 13 through the V-arrangement metal tape 10 of cross-over connection V-shaped groove V4 and V-shaped groove V3; Make the rotation that gains impetus of left driven shaft 13 and the left half axle 12 that is connected with its spline; The rotating speed of left side driven shaft 13 and left half axle 12 is N2, and left half axle 12 is given the left side driving wheel with transmission of power.According to the belt wheel transmission principle in the mechanical transmission theory; Driven rotating speed equals driven engagement radius and the inverse ratio that initiatively meshes radius with the ratio of active rotating speed, then obtains N1=N (R1/R2), N2=N (R4/R3); In the formula R1 be V-arrangement metal tape 10 ' with the engagement radius of V-shaped groove V1; R2 be V-arrangement metal tape 10 ' with the engagement radius of V-shaped groove V2, R3 is a V-arrangement metal tape 10 and the engagement radius of V-shaped groove V3, R4 is a V-arrangement metal tape 10 and the engagement radius of V-shaped groove V4.Relation according to above-mentioned N1 and N2 and N can obtain following result: when R1=R2=R3=R4, and N1=N2=N, this moment, differential mechanism was carried out constant speed work; When R1/R2 ≠ R4/R3, N1 ≠ N2, this moment, differential mechanism was carried out differential work; When R1/R2 ≠ R4/R3 ≠ 0, N1 ≠ N2 ≠ 0, this moment, differential mechanism was carried out anti-skidding self-locking work.
Theoretical according to stepless change, because the length of metal tape fixes, R2 increases or when reducing, R1 must reduce or increase, and R2 and R1 are inverse relation; R3 increases or when reducing, R4 must reduce or increase, and R3 and R4 are inverse relation.The molded breadth relation of being inversely proportional to of engagement radius and V-shaped groove, i.e. the molded breadth L1 of V-shaped groove V1 increase or when reducing, R1 reduces or increases; The molded breadth L2 of V-shaped groove V2 increases or when reducing, R2 reduces or increases; The molded breadth L3 of V-shaped groove V3 increases or when reducing, R3 reduces or increases; The molded breadth L4 of V-shaped groove V4 increases or when reducing, R4 reduces or increases.Because a left side be integral piece from fixed tray 15 with left driven shaft 13, right from fixed tray 15 ' with right driven shaft 13 ' be integral piece, so left from fixed tray 15 and the right side from fixed tray 15 ' between molded breadth L be fixed value.Simultaneously, a left side from displacement disc 16 with right face left 16 from moving ' between molded breadth L0 also be fixed value.Because L=L0+L2+L3, and L and L0 be fixed value, so L2 and L3 are inverse relation.
The differential mechanism electronic control system is regulated power F according to the corner displacement of steering equipment; Power F promotes differential adjustable lever 18 and moves axially; Shift fork head 21 and 21 on the differential adjustable lever 18 ' can promote a respectively left side makes the change of L2 and L3 size from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and right from moving the 16 ' integral left of facing left, moving right; Because changing, the inverse relation of engagement radius and V-shaped groove molded breadth, L2 and L3 size cause R2 and R3 that big or small the change also taken place; Because changing, the inverse relation between the engagement radius, R2 and R3 size cause R1 and R4 that big or small the change also taken place.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.
Cancellation differential adjustable lever 18, shift fork 20, shift fork head 22, shift fork head 22 on the basis of active differential structure ' and adjustable lever bearing 19, other part remains unchanged, and promptly can be changed into the stepless speed change type differential mechanism under the passive differential pattern.The rotational speed N 2 that left half axle 12 in the device after the change obtains the left side driving wheel also passes to left driven shaft 13, the rotational speed N 1 of right axle shaft 12 ' acquisitions right side driving wheel and pass to right driven shaft 13 ', the gain impetus rotating speed of source driving of driving shaft 1 is N.Come passive adjusting respectively to mesh the size of radius according to the equality relation of rotating speed and engagement radius and the molded breadth relation of being inversely proportional to of the inverse relation between the engagement radius and engagement radius and V-shaped groove; The change of the size of engagement radius makes differential mechanism can ensure passive differential adjusting, 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 through the two kinds of modes of outside dimension and the initial L0 length of change that change initial disk; The outside dimension that changes initial disk finally makes with the initial L0 length of change and respectively meshes radius change; When R4=R1＜R3=R2, N＞N1=N2 has the reduction of speed function; When R4=R1＞R3=R2, N1=N2＞N has the raising speed function.
The present invention is achieved through following technical proposals:
A kind of stepless speed change type no-spin lockup; It comprises the driving shaft of arranging with left driven shaft 13 and right driven shaft 13 ' parallel axes 1; On driving shaft 1 symmetric arrangement have left main fixed tray 7 ' with 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, spring seat 4 ' and spring seat 4 and locking nut 3 ' and locking nut 3; The main displacement disc 6 in a left side ' be connected with driving shaft 1 spline also and can move axially along driving shaft 1 with right main displacement disc 6; Spring seat 4 and spring seat 4 ' be connected with driving shaft 1 spline; Left side preloading spring 5 ' spring seat 4 ' with left main displacement disc 6 ' between, right preloading spring 5 between spring seat 4 and right main displacement disc 6, left main fixed tray 7 ' pass through two semicircle lands 8 to be connected with cone gear 9; The axis of described left driven shaft 13 and right driven shaft 13 ' axis on same straight line; Right driven shaft 13 ' left end insert in the endoporus of left driven shaft 13 through the support of needle bearing 11; Left side driven shaft 13 is connected with left half axle 12 splines; Right driven shaft 13 ' be connected with right axle shaft 12 ' spline; On left driven shaft 13, be furnished with a left side from fixed tray 15 and a left side from displacement disc 16, a left side is connected with left driven shaft 13 splines and can moves axially along left driven shaft 13 from displacement disc 16, right driven shaft 13 ' on be furnished with the right side from fixed tray 15 ', the right side from displacement disc 16 '; The right connection also from displacement disc 16 ' with right driven shaft 13 ' spline can be along right driven shaft 13 ' move axially; A left side is a bearing race 21 from the right-hand member of displacement disc 16, right from displacement disc 16 ' left end be bearing race 21 ', thrust-bearing 17 bearing race 21 and bearing race 21 ' between; The main fixed tray 7 in a described left side ' and left main displacement disc 6 ' formation V-shaped groove V4; Right main fixed tray 7 forms V-shaped groove V1 with right main displacement disc 6; A left side forms V-shaped groove V3 from a fixed tray 15 and a left side from displacement disc 16, right from fixed tray 15 ' with right from displacement disc 16 ' formation V-shaped groove V2, V-arrangement metal tape 10 cross-over connection V-shaped groove V3 and V-shaped groove V4; V-arrangement metal tape 10 ' cross-over connection V-shaped groove V1 and V-shaped groove V2; Differential adjustable lever 18 pass V-arrangement metal tape 10 and V-arrangement metal tape 10 ' metal strip loop, the axis of differential adjustable lever 18 and driving shaft 1, left driven shaft 13 and right driven shaft 13 ' parallel axes, differential adjustable lever 18 is provided with shift fork 20; The shift fork head 22 of shift fork 20 on a left side between displacement disc 16 and the bearing race 21; And be the smooth matching relationship of relative movement between shift fork head 22 and bearing race 21 exterior edge faces, shift fork head 22 ' the right side from displacement disc 16 ' and bearing race 21 ' between, shift fork head 22 ' and bearing race 21 ' exterior edge face between also be the smooth matching relationship of relative movement; The smooth matching relationship of its relative movement not only can transmit thrust F but also can keep relative movement between two parts in order to transmit the F thrust from adjustable lever 18 left and right directions.
The main fixed tray 7 in a described left side ' with right main fixed tray 7 be integral piece with driving shaft 1, a left side is integral piece from fixed tray 15 with left driven shaft 13, the right side from fixed tray 15 ' with right driven shaft 13 ' be integral piece; Described driving shaft 1 is supported on the differential casing through the deep groove ball bearing 2 that is positioned at driving shaft 1 two ends; Left side driven shaft 13 and right driven shaft 13 ' be supported on the differential casing through the circular cone roller bearing 14 of outer end separately, differential adjustable lever 18 is supported on the differential casing through the adjustable lever bearing 19 at its two ends; Described driving shaft 1 both can be connected the driving that gains impetus through cone gear 9 with power source, driving also can gain impetus through the axle head employing key Placement at driving shaft 1; Described left half axle 12 is used to connect the automobile left driving wheel, the right driving wheel of right axle shaft 12 ' be used to connect automobile; Described differential adjustable lever 18, shift fork 20, shift fork head 22, shift fork head 22 ' and the existence of adjustable lever bearing 19; Can realize principal moment velocity modulation joint; Cancellation differential adjustable lever 18, shift fork 20, shift fork head 22, shift fork head 22 ' and adjustable lever bearing 19 can realize that then passive differential regulates; Described V-arrangement metal tape 10 and 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 of being made up of driving shaft, driven shaft, metal awl dish and metal tape (or belt) to realize the stepless speed regulation of differential process, has improved the continuity of differential process; Can carry out the active differential according to the corner displacement of automotive steering structure when (2) having anti-skidding auto-lock function; (3) both can be used for the active differential and also can be used for passive differential, have speed changing function, applied range simultaneously concurrently; (4) simple in structure, cost of production is low.
Description of drawings
Fig. 1 is an 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 an initiatively differential A-A sectional view of stepless speed change type no-spin lockup;
Fig. 4 is the passive differential B-B of a 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 the driven shaft structural representation;
Fig. 8 is a stepless speed change type no-spin lockup left-hand rotation differential schematic diagram;
Fig. 9 is a stepless speed change type no-spin lockup right-hand rotation differential schematic diagram.
Figure: 1. Driving shaft 2. Deep groove ball bearings 3. Lock nut 3 'nuts 4 spring seat 4' spring seat 5. Right preload spring 5 'left spring preload 6. right main removable disk 6' left main removable disk 7 right main fixed disk 7 'left main fixed disk 8. semicircle connection disk 9. bevel gears 10.V shaped metal band 10 '. V-shaped metal strip 11. needle roller bearings 12 left Axle 12' Right Axle 13. left driven shaft 13 'Right driven shaft 14. tapered Gunzi bearings 15 left from the fixed disk 15' Right from the fixed disk 16 left from the removable disk 16 '. Right from the removable disk 17. thrust bearing 18. differential speed adjusting lever 19. adjustment lever bearing 20. forks 21. bearing ring 21 'bearing ring 22 . fork head 22 'fork head
V1, V2, V3, V4.V shape groove
Embodiment
Further specify particular content of the present invention and embodiment thereof with reference to the accompanying drawings.
Fig. 1 is an initiatively differential structural representation of stepless speed change type no-spin lockup; Fig. 3 is an initiatively differential A-A sectional view of stepless speed change type no-spin lockup; Driving shaft 1 is arranged with left driven shaft 13 and right driven shaft 13 ' parallel axes; Axis and the right driven shaft 13 of left side driven shaft 13 ' axis on same straight line; Right driven shaft 13 ' left end insert through the support of needle bearing 11 in the endoporus of left driven shaft 13, left driven shaft 13 is connected with left half axle 12 splines, right driven shaft 13 ' be connected with right axle shaft 12 ' spline.
The main fixed tray 7 in a left side ' with 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, spring seat 4 ' and spring seat 4 and locking nut 3 ' and locking nut 3 symmetric arrangement on driving shaft 1; The main fixed tray 7 in a left side ' with right main fixed tray 7 be integral piece with driving shaft 1; The main displacement disc 6 in a left side ' be connected with driving shaft 1 spline also and can move axially along driving shaft 1 with right main displacement disc 6; Left side preloading spring 5 ' with the big I of spring force of right preloading spring 5 respectively through locking nut 3 ' regulate with locking nut 3; Spring seat 4 and spring seat 4 ' be connected with driving shaft 1 spline; Spring seat rotates with locking nut in the time of can preventing the adjusting lock nut, left preloading spring 5 ' spring seat 4 ' and left main displacement disc 6 ' between, right preloading spring 5 is between spring seat 4 and right main displacement disc 6; The main fixed tray 7 in a left side ' be connected with cone gear 9 through land 8, driving shaft 1 are connected with power source through cone gear 9 and gain impetus.
On left driven shaft 13, be furnished with a left side from fixed tray 15 and left from displacement disc 16; A left side is integral piece from fixed tray 15 with left driven shaft 13; A left side is connected with left driven shaft 13 splines also and can moves axially along left driven shaft 13 from displacement disc 16; Right driven shaft 13 ' on be furnished with right from fixed tray 15 ', right from displacement disc 16 ', right from fixed tray 15 ' with right driven shaft 13 ' be integral piece, the right side is connected also from displacement disc 16 ' with right driven shaft 13 ' spline can be along right driven shaft 13 ' move axially; A left side is a bearing race 21 from the right-hand member of displacement disc 16; Right from displacement disc 16 ' left end be bearing race 21 ', thrust-bearing 17 bearing race 21 and bearing race 21 ' between, but thrust-bearing 17 guarantee a left side from displacement disc 16 with right from displacement disc 16 ' can relatively rotate and bearing axial pushing force.
The main fixed tray 7 in a left side ' and left main displacement disc 6 ' formation V-shaped groove V4; The width of V-shaped groove V4 is L4, and right main fixed tray 7 forms V-shaped groove V1 with right main displacement disc 6, and the width of V-shaped groove V1 is L1; A left side forms V-shaped groove V3 from a fixed tray 15 and a left side from displacement disc 16; The width of V-shaped groove V3 is L3, right from fixed tray 15 ' with right from displacement disc 16 ' formation V-shaped groove V2, the width of V-shaped groove V2 is L2.
V-arrangement metal tape 10 cross-over connection V-shaped groove V3 and V-shaped groove V4; V-arrangement metal tape 10 is R3 with the engagement radius of V-shaped groove V3; V-arrangement metal tape 10 is R4 with the engagement radius of V-shaped groove V4; V-arrangement metal tape 10 ' cross-over connection V-shaped groove V1 and V-shaped groove V2, V-arrangement metal tape 10 ' with the engagement radius of V-shaped groove V1 be R1, V-arrangement metal tape 10 ' with the engagement radius of V-shaped groove V2 be R2; Left side preloading spring 5 ' spring force guarantee metal tape 10 and the no gap engagement of V-shaped groove V3 and V-shaped groove V4 and the power of delivery request, the spring force of right preloading spring 5 guarantees that metal tape 10 ' with the no gap of V-shaped groove V1 and V-shaped groove V2 meshes and the power of delivery request.
Differential adjustable lever 18 pass V-arrangement metal tape 10 and V-arrangement metal tape 10 ' metal strip loop; Differential adjustable lever 18 is supported on the differential casing through the adjustable lever bearing 19 at its two ends; The axis of differential adjustable lever 18 and driving shaft 1, left driven shaft 13 and right driven shaft 13 ' parallel axes; Differential adjustable lever 18 can move along its axis; Differential adjustable lever 18 is provided with shift fork 20, the shift fork head 22 of shift fork 20 on a left side between displacement disc 16 and the bearing race 21, shift fork head 22 ' the right side from displacement disc 16 ' and bearing race 21 ' between; The velocity modulation of being on duty pole 18 is its axis left side or when moving right in power F effect lower edge; Shift fork head 22 and shift fork head 22 ' act on respectively bearing race 21 and bearing race 21 ' outer side surface on, promote bearing race 21 or bearing race 21 ' in, drive a left side from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and right from displacement disc 16 ' integral body 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, and the differential mechanism electronic control system is regulated size and the movement direction of power F according to the corner displacement of steering equipment, and it is big or small with the inversely prroportional relationship of L3 to realize changing L2.
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 a stepless speed change type no-spin lockup sectional view; Cancellation differential adjustable lever 18, shift fork 20, shift fork head 22, shift fork head 22 on the basis of active differential structure ' and adjustable lever bearing 19; Other part remains unchanged, and the device after the change is used for passive differential.
Fig. 5 is the driving shaft structural representation that adopts the input of cone gear power; The main fixed tray 7 in a left side ' be connected with cone gear 9 through two semicircle lands 8; Driving shaft 1 is connected with power source through cone gear 9 and gains impetus, and driving shaft 1 is supported on the differential casing through 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 gains impetus, and driving shaft 1 adopts the key Placement to be connected with power source through its axle head and gains impetus.
Fig. 7 is the driven shaft structural representation; Left side driven shaft 13 and right driven shaft 13 ' be supported on the differential casing through the circular cone roller bearing 14 of outer end separately; Left side driven shaft 13 and right driven shaft 13 ' receive the axially support of radial support, needle bearing 11 radial support and the thrust-bearing 17 of circular cone roller bearing 14 simultaneously, but make left driven shaft 13 and right driven shaft 13 ' between can be separate bearing radial force and axial force again rotation the time; A left side from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and right from displacement disc 16 ' the overall calculation width be L0, a left side from fixed tray 15 and right from fixed tray 15 ' between molded breadth be L; Left half axle 12 is used to connect the automobile left driving wheel, the right driving wheel of right axle shaft 12 ' be used to connect automobile.
Fig. 8 is a stepless speed change type no-spin lockup left-hand rotation differential schematic diagram; No matter be when adopting active differential structure or passive differential structure to turn left differential work; Relation between engagement radius R 1, R2, R3 and the R4 all meets relation shown in Figure 8; Be that R1 increases, R2 reduces, R3 increases and R4 reduces, such relation satisfies N1＞N＞N2 between the engagement radius.
Fig. 9 is a stepless speed change type no-spin lockup right-hand rotation differential schematic diagram; No matter be when adopting active differential structure or passive differential structure to turn right differential work; Relation between engagement radius R 1, R2, R3 and the R4 all meets relation shown in Figure 9; Be that R1 reduces, R2 increases, R3 reduces and R4 increases, such relation satisfies N2＞N＞N1 between the engagement radius.
Embodiment 1:
Stepless speed change type no-spin lockup active differential and self-locking working procedure are following.
Through the right preloading spring 5 of locking nut 3 and locking nut 3 ' regulate respectively and left preloading spring 5 ' initial tension of spring; Make L1=L2=L3=L4; Each original state value that meshes radius is R1=R2=R3=R4; According to N1=N (R1/R2) and N2=N (R4/R3), can obtain N1=N2=N, this moment, differential mechanism was carried out constant speed work.
When automobile turns left; The differential mechanism electronic control system is regulated power F according to the corner displacement of steering equipment axially is moved to the left differential adjustable lever 18; Shift fork head 22 on the differential adjustable lever 18 ' promotion bearing race 21 ' be moved to the left; Thereby drive a left side from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and rightly be moved to the left, because L is fixed value and L=L0+L2+L3 with L0, so L2 increase when causing L3 to reduce from moving the 16 ' integral body of facing left.Because there are inverse relation in engagement radius and V-shaped groove molded breadth, so L3 reduces to cause R3 to increase, the L2 increase causes R2 to reduce; Because it is inverse relation that there is R4 in R3,, R3 cause R4 to reduce so increasing; Because it is inverse relation that there is R1 in R2, so R2 reduces to cause R1 to increase.Result after the adjusting is for R1 increases, R2 reduces, R3 increases and R4 reduces; Because original state is R1=R2=R3=R4, thus R1/R2＞1 and R4/R3＜1 are arranged, 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 driving wheel rotating speed has realized initiatively differential less than right side driving wheel rotating speed.
When automobile is turned right; The differential mechanism electronic control system is regulated power F according to the corner displacement of steering equipment axially moves right differential adjustable lever 18; Shift fork head 22 on the differential adjustable lever 18 promotes bearing race 21 and moves right; Thereby drive a left side from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and rightly move right from moving the 16 ' integral body of facing left, L2 reduces when causing L3 to increase; Because there are inverse relation in engagement radius and V-shaped groove molded breadth, so increasing, L3 cause R3 to reduce, L2 reduces to cause R2 to increase; Because it is inverse relation that there is R4 in R3, so R3 reduces to cause R4 to increase; Because it is inverse relation that there is R1 in R2,, R2 cause R1 to reduce so increasing.Result after the adjusting is for R1 reduces, R2 increases, R3 reduces and R4 increases; Because original state is R1=R2=R3=R4, thus R1/R2＜1 and R4/R3＞1 are arranged, 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 driving wheel rotating speed has been realized initiatively differential of right-hand rotation less than left side driving wheel rotating speed.
Because the actual size of engagement radius R 1, R2, R3 and R4 promptly can not equal zero also can not be infinitely great; Therefore when differential; Certainly exist 0＜R1/R2 ≠ R4/R3＜+∞, can obtain 0＜N1 ≠ N2＜+∞, neither fast idle can be not slack yet fully for the both sides driving wheel; Can keep the both sides wheel all to have turning power, realize the anti-skidding self-locking of differential mechanism.
Embodiment 2:
Passive differential of stepless speed change type no-spin lockup and self-locking working procedure are following.
Driving shaft 1 is connected with cone gear 9 through 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 rotating speed of left side driving wheel passes to the left driven shaft 13 that is connected with left half axle 12 splines through left half axle 12, and the rotating speed of left driven shaft 13 is N2; The right driven shaft 13 that the rotating speed of right side driving wheel is connected with right axle shaft 12 ' spline through right axle shaft 12 ' pass to ', right driven shaft 13 ' rotating speed be N1.Through the right preloading spring 5 of locking nut 3 and locking nut 3 ' regulate respectively and left preloading spring 5 ' initial tension of spring, make L1=L2=L3=L4, each original state value that meshes radius is R1=R2=R3=R4.
When automobile two side drive wheel constant-speed drivings; N1=N2 is arranged,, can obtain R1=R2=R3=R4 according to N1=N (R1/R2) and N2=N (R4/R3); This just coincide with the original state value of differential mechanism engagement radius, and this moment, differential mechanism can ensure automobile two side drive wheel constant-speed drivings.
When automobile turned left, left side driving wheel rotating speed was less than right side driving wheel rotating speed, i.e. N2＜N＜N1.At this moment, right driven shaft 13 ' rotational speed N 1 greater than the rotational speed N of driving shaft 1, according to N1=N (R1/R2)＞N R1/R2＞1 is arranged; This causes R1 to increase with R2 reducing, and R2 reduces to cause L2 to increase, and promptly metal tape 10 ' extruding right side is from displacement disc 16 ' be moved to the left; Thereby drive a left side from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and rightly be moved to the left from moving the 16 ' integral body of facing left; Move back L3 and reduce, L3 reduces to cause R3 to increase, and is inverse relation because there is R4 in R3; Cause R4 to reduce so R3 increases, the result after the adjusting is for R1 increases, R2 reduces, R3 increases and R4 reduces.Because original state is R1=R2=R3=R4, the engagement radius value after the adjusting satisfies R1/R2＞1 and R4/R3＜1, satisfies N1＞N and N2＜N, has ensured automobile left-hand rotation differential.
When automobile was turned right, right side driving wheel rotating speed was less than left side driving wheel rotating speed, i.e. N1＜N＜N2.At this moment, the rotational speed N 2 of left driven shaft 13 has R4/R3＞1 greater than the rotational speed N of driving shaft 1 according to N2=N (R4/R3)＞N; This causes R4 to increase and R3 reduces, and R3 reduces to cause L3 to increase, and promptly metal tape 10 extruding left sides move right from displacement disc 16; Thereby drive a left side from displacement disc 16, bearing race 21, thrust-bearing 17, bearing race 21 ' and rightly move right from moving the 16 ' integral body of facing left; Move back L2 and reduce, L2 reduces to cause R2 to increase, and is inverse relation because there is R1 in R2; Cause R1 to reduce so R2 increases, the result after the adjusting is for R1 reduces, R2 increases, R3 reduces and R4 increases.Because original state is R1=R2=R3=R4, the engagement radius value after the adjusting satisfies R1/R2＜1 and R4/R3＞1, satisfies N1＜N and N2＞N, has ensured automobile right-hand rotation differential.
Because the actual size of engagement radius R 1, R2, R3 and R4 promptly can not equal zero also can not be infinitely great; Therefore when differential; Certainly exist 0＜R1/R2 ≠ R4/R3＜+∞, can obtain 0＜N1 ≠ N2＜+∞, neither fast idle can be not slack yet fully for the both sides driving wheel; Can keep the both sides wheel all to have 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 following.
Realize that speed changing function comprises the two kinds of modes of outside dimension and the initial L0 length of change that change initial disk.
The outside dimension that changes initial disk is realized speed-change process; The main fixed tray 7 in a left side ' with left main displacement disc 6 ', the outside dimension of right main fixed tray 7 and right main displacement disc 6 less than a left side from fixed tray 15 and a left side from displacement disc 16, right from fixed tray 15 ' and right from displacement disc 16 ' outside dimension; Satisfying the initial engagement radius relationship is: during R4=R1＜R3=R2; N＞N1=N2 has the reduction of speed function.
Change initial L0 length and realize speed-change process.The main fixed tray 7 in a left side ' with left main displacement disc 6 ', right main fixed tray 7 and right main displacement disc 6, a left side from fixed tray 15 and a left side from displacement disc 16, right from fixed tray 15 ' and rightly all equate from displacement disc 16 ' outside dimension; Can pass through increase L0 length makes the width of L3 and L2 all diminish respectively; Make V-arrangement metal tape 10 and V-arrangement metal tape 10 ' all become big respectively with the kneading radius R 3 of V-shaped groove V3 and V-shaped groove V2 and the radius of R2; Then through V-arrangement metal tape 10 and V-arrangement metal tape 10 ' R4 and R1 are diminished; Satisfying the initial engagement radius relationship is: during R4=R1＜R3=R2; N＞N1=N2 has the reduction of speed function, through locking nut 3 ' with locking nut 3 reconcile respectively preloading spring 5 ' with preloading spring 5 respectively to the main displacement disc 6 in a left side ' with the initial action power of right main displacement disc 6 size.
In like manner, reduce L0 length L3 and L2 width are all become greatly, the radius of R3 and R2 all diminishes, and R4 and R1 become greatly, satisfy the initial engagement radius relationship to be: during R4=R1＞R3=R2, N1=N2＞N has the raising speed function.Reduce earlier L0 length, the back according to the transmitted power size reconcile spring 5 ' with spring 5 pretightening forces.
Claims (7)
1. 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 with left driven shaft (13) and right driven shaft (13 ') parallel axes; Go up symmetric arrangement at driving shaft (1) 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), spring seat (4 ') and spring seat (4) and locking nut (3 ') and locking nut (3) are arranged; The main displacement disc in a left side (6 ') is connected with driving shaft (1) spline with right main displacement disc (6) and can moves axially along driving shaft (1), and spring seat (4) is connected with driving shaft (1) spline with spring seat (4 '), and left preloading spring (5 ') is positioned between spring seat (4 ') and the left main displacement disc (6 '); Right preloading spring (5) is positioned between spring seat (4) and the right main displacement disc (6), and left main fixed tray (7 ') is connected with cone gear (9) through 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) through the support of needle bearing (11); Left side driven shaft (13) is connected with left half axle (12) spline; Right driven shaft (13 ') is connected with right axle shaft (12 ') spline; On left driven shaft (13), be furnished with a left side from fixed tray (15) and left from displacement disc (16), a left side is connected with left driven shaft (13) spline also and can moves axially along left driven shaft (13) from displacement disc (16), on right driven shaft (13 '), is furnished with right from fixed tray (15 '), right from displacement disc (16 '); The right side is connected with right driven shaft (13 ') spline also and can moves axially along right driven shaft (13 ') from displacement disc (16 '); A left side is bearing race (21) from the right-hand member of displacement disc (16), and right left end from displacement disc (16 ') is bearing race (21 '), and thrust-bearing (17) is positioned between bearing race (21) and the bearing race (21 '); V-arrangement metal tape (10) cross-over connection V-shaped groove (V4) and V-shaped groove (V3); V-arrangement metal tape (10 ') cross-over connection V-shaped groove (V1) and V-shaped groove (V2); Differential adjustable lever (18) passes the metal strip loop of V-arrangement metal tape (10) and V-arrangement metal tape (10 '); The parallel axes of the axis of differential adjustable lever (18) and driving shaft (1), left driven shaft (13) and right driven shaft (13 '); Differential adjustable lever (18) is provided with shift fork (20), and the shift fork head (22) of shift fork (20) is positioned at a left side between displacement disc (16) and the bearing race (21), is the smooth matching relationship of relative movement between shift fork head (22) and bearing race (21) exterior edge face; Shift fork head (22 ') is positioned at right between displacement disc (16 ') and the bearing race (21 '), is the smooth matching relationship of relative movement between shift fork head (22 ') and bearing race (21 ') exterior edge face.
2. a kind of stepless speed change type no-spin lockup according to claim 1; It is characterized in that; Main fixed tray in a described left side (7 ') and right main fixed tray (7) are integral piece with driving shaft (1); A left side is integral piece from fixed tray (15) with left driven shaft (13), and right is integral piece from fixed tray (15 ') with 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 the differential casing through the deep groove ball bearing (2) that is positioned at driving shaft (1) two ends; A left side driven shaft (13) and right driven shaft (13 ') are supported on the differential casing through the circular cone roller bearing (14) of outer end separately, and differential adjustable lever (18) is supported on the differential casing through 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 be connected the driving that gains impetus through cone gear (9) with power source, driving also can gain impetus through the axle head employing key Placement 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 used to connect the automobile left driving wheel, and right axle shaft (12 ') is used to connect the right driving wheel of automobile.
6. a kind of stepless speed change type no-spin lockup according to claim 1 is characterized in that, the existence of described differential adjustable lever (18), shift fork (20), shift fork head (22), shift fork head (22 ') and adjustable lever bearing (19) can realize principal moment velocity modulation joint; Cancellation differential adjustable lever (18), shift fork (20), shift fork head (22), shift fork head (22 ') and adjustable lever bearing (19) then can be realized passive differential adjusting.
7. a kind of stepless speed change type no-spin lockup according to claim 1 is characterized in that, described V-arrangement metal tape (10) and V-arrangement metal tape (10 ') also can be replaced by vee-belt.
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| CN201110204346.XA CN102384240B (en) | 2011-07-21 | 2011-07-21 | Infinitely variable speed self-locking differential |
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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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| CN102384240B CN102384240B (en) | 2014-07-09 |
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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 |
| CN112828095A (en) * | 2020-12-27 | 2021-05-25 | 宋恒 | Veneer reeling machine for machining |
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| 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 |
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| Publication number | Publication date |
|---|---|
| CN102384240B (en) | 2014-07-09 |
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