CN102588553A - Self-locking differential containing spatial wedged mechanisms - Google Patents

Abstract

The invention relates to a self-locking differential containing spatial wedged mechanisms, which is characterized in that at least one spatial wedged mechanism is coaxially arranged between two rotary parts of an existing differential mechanism, a rotary guide mechanism G comprises an intermediate part and a guide part as same as one rotary part, both the intermediate part and the guide part are provided with guide teeth, a traction friction mechanism F1 comprises the intermediate part and the other rotary part, and at least one of two torque output parts is an intermediate part. Therefore, the wedged state of the spatial wedged mechanisms can be critically released to realize differential rotation by using steering torque transferred by a driving wheel coupled with the intermediate part instead of using driving torque from a planetary gear when in steering. However, during trackslip, due to absence of sufficient wedge releasing torque from the driving wheel, the wedged state of the spatial wedged mechanisms cannot be released, and the driving torque of a trackslip is completely transferred to the driving wheel on one non-slip side through a wedging friction pair. The torque-sensing self-locking differential is simple in structure, superior in performance, fully mechanical and completely superior to a Torsen differential, and has infinite locking coefficient.

Description

Include the no-spin lockup of space wedge mechanism

Related application

The application is the one Chinese patent application 201010222712.X of the space by name insertion type friction free wheel device that proposes of the applicant and 201020186785.3 dependent patent application.The full content that is somebody's turn to do open two patent applications formerly is incorporated into this by reference.

Technical field

The present invention relates to a kind of differential driver in the mechanical transmission fields, particularly but not only relate to the differential mechanism that driving wheel skids that prevents of a kind of wheeled motor vehicle use.

Background technique

From Frenchman Bei Gelieer invention differential mechanism in 1825 so far, the antislip problem of differential mechanism is just perplexing people always, becomes a big technology barrier that promotes vehicle handling quality and the full-time full wheel drive of realization etc.All there is detailed description " four-wheel drive car tectonogram " ([day] Zhuan Yexin department work, Liu Yin etc. translate, Jilin science tech publishing house, 1995, p143～159) and " automotive axle design " (Liu Weixin, publishing house of Tsing-Hua University, 2004, p214～283) to this.Over more than 100 year; People have proposed various improvement projects for this reason; But do not find one all the time and have reliable, slip-resistant/self-lock ability concurrently, be quick on the draw and need not the improvement project of any control (no response gap or hysteresis in time,, adaptively change over to self-locking working state), volume simple in structure is little, processing and assembling is easy, cheap Purely mechanical.

However, as the representative of no-spin lockup, invention is used the dental formula differential and the high friction of the turbo type differential mechanism of the history that all has more than 70 year so far and has still been obtained success to a certain degree.The former is fully adaptively in response to differential change in rotational speed, though possess infinitely-great locking coefficient, it is not a differential mechanism truly; Because in the differential operating mode, its whole driving forces can only be distributed to single output shaft; Cause it but can only one-sidedly drive forever during the differential driving, destroyed the continuity that drives, it is discontinuous unbalanced to work; Dynamic load is bigger on the transmission shaft, and Vehicular turn is heavy and tire wear is too fast.And the latter; Comprise non-planet gear type Torsen (Torsen) differential mechanism wherein, drive two output shafts respectively, cause its space meshing relation and structure and become too complicated because of adopting many worm-and-wheel gears to coupling; Too high to accuracy of manufacturing and material performance requirement; Not only be difficult to make, more be difficult to assembling, rare producer can be competent at.And high cost has more directly hindered its possibility that popularizes.What form contrast therewith is though such differential mechanism fully adaptively in response to the variation of differential torque, is worked very smoothly, not have machinery and impact.But its performance does not reach the height that matches with expensive price, does not perhaps reach the level that can remedy the high price defective.

In fact, in the high friction of the turbo type differential mechanism, transmitting torque, differential rotate and self-locking three functions are accomplished by Worm gear mechanism all singlely, and no matter whether self-locking, the worm gear higher pair of its line contact all has high contact strength and friction intensity all the time.More disadvantageous is that Worm gear mechanism does not also have metastable force-bearing situation.When differential mechanism self-lock, in response to the variation of driving wheel adhesion/ground friction coefficient, this Worm gear mechanism will bear bigger pulsed torque shock ends, and locking coefficient is big more, and driving wheel adhesion changes soon more, and this impacts just serious more.Simultaneously, this torque shock ends also can not get slowing down of any mechanism, until arriving driving wheel.Therefore, the structure characteristic of such differential mechanism has directly determined its bearing capacity not high, and the lower result of specified bearing capacity.In addition, limit by self-locking mechanism, its lead angle that is used for the Worm gear mechanism of self-locking is changeless (0.1 the friction factor of being approximately by rigidity limits), does not possess controllability.Degree of freedom in design is too little.So, such differential mechanism easy abrasion, it is too big to be difficult to possess the bigger locking coefficient or the cost of wearing and tearing, and more difficulty has extreme cross-country power concurrently.

For example; At manoeuvring performance, self-lock ability and the result who compromises between reducing to wear and tear with life-saving be; The locking coefficient of such differential mechanism generally is no more than 6～9, and for wherein non-planet gear type worm gear differential mechanism (Torsen), more need be reduced to 3～3.5 level.And structural type is single to be limit owing to receiving, and such differential mechanism is difficult to possess the torque distribution ability of asymmetric formula differential mechanism, is difficult to be applicable between the bridge such as multiple perforation bridge wait the differential position.In the using process, difficulty, trouble, the M R in being unfavorable for using are changed in its easily damaged parts wearing and tearing back.

Summary of the invention

The present invention is devoted to eliminate or alleviate at least the above-mentioned deficiency that exists in the existing technology.

The purpose of this invention is to provide a kind of anti-skidding reliably/self-lock ability that has; Be quick on the draw and need not any control; The no-spin lockup that includes the space wedge mechanism of the Purely mechanical that volume simple in structure is little, processing and assembling is easy, cheap, it has the characteristics of torque induction.

For reaching the foregoing invention purpose, the no-spin lockup that contains the space wedge mechanism within the present invention comprises, can be around rotating relatively two revolving mebers of same axis; And being arranged between these two revolving mebers, and rotating at least one space wedge mechanism of coaxial line.

With improvement, this space wedge mechanism comprises, but around the traction friction mechanism of same axis revolution and axial engagement, it has around said axis revolution and is provided with the intermediate piece and the friction member of rubbing surface, between this two member, to transmit friction torque; And this friction member is one in the intermediate piece of two said revolving mebers and another space wedge mechanism; And friction mechanism provides engaging force and around rotating at least one the rotation guide mechanism of said axis, it has guiding element and the above-mentioned intermediate piece that turns round and be provided with corresponding guide surface around said axis in order to draw; Wherein, the lift angle λ at the mutual conflict position between guiding element and intermediate piece both sides' the guide surface is greater than 0 degree and less than 90 degree.

Further; When guiding element and friction member can be connected into a friction piece drivingly by intermediate piece, the lift angle λ at the mutual conflict position between guiding element and intermediate piece both sides' the guide surface was greater than zero and smaller or equal to ξ; Promptly; 0＜λ≤ξ, wherein, ξ is the maximum value that can make the lift angle λ of the guiding friction pair self-locking that is formed at this conflict position.

Preferably, the guide surface of guiding element and intermediate piece is the screw type flank of tooth, and it is arranged on the surface that comprises end face, inner peripheral surface and outer circumferential face that both face mutually; In axial plane, the angle between this screw type flank of tooth and the said axis is greater than 0 degree, less than 180 degree.

Best, also be provided with the elasticity pre-tightening mechanism that has an elastic element at least, it is used for keeping constantly intermediate piece to be connected with indirect at least friction between the friction member.

Preferably, the guide surface of guiding element and intermediate piece is the screw type flank of tooth, and it is arranged on the surface that comprises end face, inner peripheral surface and outer circumferential face of this two member; In axial plane, the angle between this screw type flank of tooth and the above-mentioned axis is greater than 0 degree, less than 180 degree.

Alternatively, at least one in traction friction mechanism and the power transmission friction mechanism, its two corresponding rubbing surfaces be the half cone drift angle greater than 0 degree less than 180 frusto-conical surfaces of spending.

For increasing ζ and ξ, the traction friction mechanism can be many friction disk types friction mechanism, and it has and friction member and axially staggered each at least one friction plate of non-rotatable two groups of linking to each other of intermediate piece difference.

For increasing torque capacity, the power transmission friction mechanism can be many friction disk types friction mechanism, and it has and friction member and axially staggered each at least one friction plate of non-rotatable two groups of linking to each other of guiding element difference.What need special instruction is that the implication of used related notion of present specification or noun is following:

Rotate guide mechanism: circumference is relatively rotated to convert into comprise at least and axially relatively moving or the guide mechanism of mobile trend.For example lead angle strict conformance and not slides/rolls formula spiral or part screw mechanism, radial peg groove mechanism, end face wedge mechanism, the chimeric mechanism of end face, end ratchet mechanism and the cylinder/end cam mechanism of strict conformance.

Space wedge mechanism: by rotating guide mechanism and drawing the mechanism that friction mechanism is formed.

Wedging: be weighed into also that wedge, wedging are lived, wedging or wedging; A kind of working state or the process of space wedge mechanism; Wedge/go wedge/disengagement is opposite with separating, and refers to that intermediate piece can be combined into a coupled condition or a connection procedure that turns round friction piece drivingly with guiding element and friction member.

Driving torque more than needed: the input torque that imports differential mechanism into; Be assigned to the output member that is coupled respectively through output shaft and driving wheel through its box of tricks; When not considering transmission loss; In the driving torque that this output member obtains, comparing ground effects is many that part of in the friction torque with the driving wheel of its coupling, is known as driving torque more than needed.Obviously, when above-mentioned friction torque equals zero, the driving torque that above-mentioned distribution comes will be driving torque more than needed all, and driving torque more than needed is greater than zero the time, respective drive wheel has the trend of trackslipping in relative ground.

ζ and ξ: the important limiting angle of space wedge mechanism; Like Fig. 1～2, the intermediate piece 100 shown in 4; On the one hand; For example 110 at least axially conflicts with its traction rubbing surface 42 of friction member 40 of axially support through its revolution rubbing surface, one one group of comprising at least that is not orthogonal to the rotary type traction friction mechanism F1 of rotational axis X with the W that makes a concerted effort of the normal pressure that forms the conflict position draws friction pair; On the other hand; Through it towards the guide surface of a certain circumferencial direction 104a for example; With the corresponding guide surface of guiding element 90 for example 94a at least axially conflict, be not orthogonal to the N that makes a concerted effort of the normal pressure that forms the conflict position rotational axis X rotation guide mechanism G comprise one group of guiding friction pair of one at least; The common tangent at this conflict position and the mean value that hangs down as for the angle on the plane of rotational axis X are called the lift angle λ at this conflict position; On the one hand, also can act on such as other active forces such as axial elasticity pretightening force Q again, for example pass through the peripheral force/drag torque of the internal spline flank of tooth effect among Fig. 1,9,11,14 through other surface; In rotating the rotation guiding operating mode of guide mechanism G; Just guiding element 90 causes intermediate piece 100 to be followed the usual practice like arrow S direction with in the operating mode of rotating more than or equal to the relative friction member 40 of zero speed; The minimum lift angle at conflict position, both sides surface of friction pair self-locking of can guaranteeing to lead is defined as ζ, and maximum lift angle then is defined as ξ.Every forms of motion that these two limiting angles have then defined intermediate piece 100 relative guiding element 90 rotations forward, transfixion fully and rotated backward.Concrete implication is following:

1, when ξ＜λ＜90 are spent, the guiding friction pair all can not self-locking with the traction friction pair, through the normal pressure N of guiding friction pair, perhaps its component T and P, guiding element 90 can cause intermediate piece 100 relative its forward that is the arrow P direction trackslip/extrude.Therefore, guiding element 90 can not be become a friction piece by intermediate piece 100 wedgings with friction member 40.Just, just cause intermediate piece 100 only to be directed to part 90 and promoting relative friction member 40 and rub and trackslip and do not extruded by actual because pressure N is derived from non-resilient power or limit by element structure.

2, when ζ＜λ≤ξ and λ＞0, the guiding friction pair is in constant self-locking state, the traction friction pair be in can not self-locking general static friction state.The traction friction torque of at this moment, the transmission capacity of space wedge mechanism the is unique time traction friction pair that is decided by wedging.Therefore; Although intermediate piece 100 can become a friction piece with friction member 40 wedgings with guiding element 90; But when relative guiding elements 90 overloads of friction member 40, the traction friction pair still can change the sliding friction state over to and the friction pair that leads still can be kept self-locking by the static friction state naturally.Accordingly, the space wedge mechanism is in half wedging state, and differential mechanism is in non-complete self-locking state.

3, as 0＜λ≤ζ when (to the situation of ζ＞0), the traction friction pair is in constant self-locking state, and the guiding friction pair is in general static friction state.Maximum static friction torque/guiding the friction torque of the transmission capacity of space wedge mechanism the is unique time guiding friction pair that is decided by wedging.Therefore; Although intermediate piece 100 can become a friction piece with friction member 40 wedgings with guiding element 90; But when relative guiding elements 90 overloads of friction member 40, intermediate piece 100 will have the maximum static friction state of breaking through the guiding friction pair and guiding element 90 trend of trackslipping and climbing relatively, and just trend is stoped (remove non-pressure N and be derived from elastic force) by the axial force enclosed construction rigidity of wedge mechanism because this climbs; So the guiding friction pair just maintains to being forced property the general static friction state that is equal to self-locking.That is, intermediate piece 100, guiding element 90 and friction member 40 threes are forced one of wedging/be combined into and rotate wholely, are loaded onto damage and also do not trackslip each other and climb even cross.Space wedge mechanism thereby be in the absolute self-locking/wedging state of similar diagonal-bracing type free wheel device, its transmission capacity only is decided by structural strength.

Can know that by general knowledge λ equals the situation of ζ, only be present in theory and not and be present in the reality.That is to say that because of inevitable the trackslipped friction pair that exists one group of not self-locking all the time of self-locking simultaneously, the physical essence of space wedge mechanism transmitting torque can only be the friction self-locking that friction rather than existing technology are assert.But, can not more can not derive out by its structure by as kinematic relation enlightenment, the imagination of the plane wedge mechanism of special case or disclose because limiting angle ζ is not familiar with by existing technology is theoretical.Therefore; Do not know that the existing technology of existence and the physical meaning of limiting angle ζ just can't thoroughly be familiar with the actual physical implication of the limiting angle ξ that is the angle of wedge; Comprise the normality that friction is trackslipped; Friction is trackslipped and the direction of transmission of torque and the correlation of overload, also just can not find, discloses and confirm the physical essence of the circumferential wedging of space wedge mechanism naturally, thereby draw the application's technological scheme.

Obviously, above-mentioned lift angle λ is exactly the angle of wedge of space wedge mechanism, also claims the wedging angle, and only when 0＜λ≤ξ, and the space wedge mechanism can wedging, and differential mechanism can be by locking/friction self-locking.And, ζ and ξ be one with the relevant dynamic parameters of above-mentioned drag torque size, and when this drag torque equals zero (when driving wheel is unsettled), obtain only relevant minimum value ζ respectively with geometric parameter and friction factor _MinAnd ξ _Min

The no-spin lockup that contains the space wedge mechanism within the present invention has simple and reasonable, cheap; The cordwood assembling, superior performance, high reliability; High responsiveness weares and teares little and can compensate the long lifetime automatically; Full machinery is adaptive to torque and changes, and locking coefficient can reach advantages such as infinity, operation and maintenance be simple and convenient.Can be applicable to all differential positions of wheeled vehicle best, cost performance is superior to existing technology comprehensively, particularly is superior to the high friction of worm-gear type differential mechanism.By following embodiment's explanation and accompanying drawing, it is more clear and clear that objects and advantages of the present invention will seem.

Description of drawings

Fig. 1 is the schematic diagram of each flank profil correlation in the rotation guide mechanism of representing with the form of radially projecting's unfolded drawing, in order to the relation of lift angle and friction self-locking that the tooth/face that leads in this mechanism is described.

Fig. 2 is the axial section according to common symmetric type cone gear no-spin lockup of the present invention.

Fig. 3 A and Fig. 3 B, be respectively include among Fig. 2 intermediate piece output member right elevation axially partly cut open figure and plan view.

Fig. 4 A～4C is respectively that the differential mechanism among Fig. 2 is in the non-differential driving operating mode; Each flank profil of its two rotation guide mechanisms and traction friction mechanism is to the local unfolded drawing of same external cylindrical surface radially projecting; Fig. 4 A is the profile of tooth schematic representation that each member of guide mechanism is rotated in the left side among Fig. 4 B that representes separately; Fig. 4 B is the plan view of flank profil relation, and Fig. 4 C is the profile of tooth schematic representation that each member of guide mechanism is rotated on the right side among Fig. 4 B that representes separately.

Fig. 5 is the schematic diagram of differential mechanism shown in Figure 2, the bang path of the respective torque of first half when wherein dotted line represents the right-hand member output shaft unsettled.

Fig. 6 is the schematic diagram that has changed after the guiding element Connecting format of differential mechanism shown in Figure 2.

Fig. 7 is the schematic diagram that has changed behind the output member composition form of differential mechanism shown in Figure 2.

Fig. 8 is the schematic diagram that has changed after the guiding element Connecting format of differential mechanism shown in Figure 7.

Fig. 9 is the axial section according to another symmetric type cone gear no-spin lockup of the present invention.

Figure 10 is the schematic diagram of differential mechanism shown in Figure 9.

Figure 11 is the rotation profile corresponding to H-H cross section among Figure 12 according to symmetric type cylindrical gears no-spin lockup of the present invention.

Figure 12 is the sectional drawing in Y-Y cross section among Figure 11.

Figure 13 is the schematic diagram of differential mechanism shown in Figure 11, wherein, is convenient mapping, and circumferentially planet gear meshed 50a and 50b are separated originally, and with the form that dotted line links to each other two the position Z and the Z ' of engagement originally are shown.

Figure 14 is the axial section according to another symmetric type cone gear no-spin lockup of the present invention.

Figure 15 is the schematic diagram of differential mechanism shown in Figure 14.

Figure 16 is the axial section that has changed behind the output member composition form of differential mechanism shown in Figure 14.

Figure 17 is the schematic diagram of differential mechanism shown in Figure 16.

Figure 18 is the schematic diagram according to single cylindrical planetary gear formula no-spin lockup of the present invention.

Figure 19 is the schematic diagram according to bicylindrical planetary gear type no-spin lockup of the present invention, wherein, is convenient mapping, and non-radially planet gear meshed 50a and 50b are drawn as radially engagement each other.

Figure 20 is the schematic diagram according to bicylindrical dual planetary gear formula no-spin lockup of the present invention.

Figure 21 is the schematic diagram according to another single cylindrical planetary gear formula no-spin lockup of the present invention.

Figure 22 is the schematic diagram according to the planetary no-spin lockup of circular cone of indifferential shell of the present invention.

Embodiment

Necessary explanation: in the text of this specification and the institute's drawings attached, same or analogous member and characteristic portion all adopt identical reference character, and only when they occur for the first time, give necessary explanation.Equally, the also working mechanism of the same or similar mechanism of not repeat specification or process.For difference is arranged on identical member or characteristic portion on symmetry or the corresponding position, this specification has added letter at the back at its reference character, and when general reference is explained or need not to distinguish, then additional any letter.

The differential mechanism D1 of embodiment's mutual direct friction self-locking of output terminal in: two

Present embodiment is in the common symmetric type cone gear box of tricks with common form, and the no-spin lockup D1 of gained behind the wedge mechanism of space is set.Referring to Fig. 2～4, differential carrier 72a and 72b are tightened to a complete differential carrier 72 by the bolt (not shown), thereby constitute the main revolving member that limits rotational axis X and reference for assembling among the differential mechanism D1.On the outer radial flange of differential carrier 72 1 ends, be formed with bolt hole 78, in order to through fixing tapered input ring gear 58 (not shown) used of input torque of bolt (not shown).The inboard of the torque delivery outlet that forms around axis X in differential carrier 72 both sides, radial location rotationally is useful on the tubular matrix 112 of output driving torque respectively, and it forms as one with two intermediate pieces 100 respectively, to constitute the output member of differential mechanism D1.This two tubular matrix 112 directly are coupled with two output shaft 74 (not shown) that are formed with complementary spline tooth respectively through the spline tooth 114 in the endoporus separately.

In the inside of differential carrier 72, be specially criss-cross planet pin 56 usually, be fastened in the radial hole that jointing end face surrounded of differential carrier 72a and 72b.At least the one group of tapered planetary pinion 50 that comprises is sleeved on the planet pin 56 rotationally, and with the meshing respectively of its both sides around rotating two differential 80a and the 80b of axis X with circular cone tooth.Differential 80a and 80b are driven by the input torque of differential mechanism D1 can and around rotating two revolving mebers of axis X differential.And; This differential 80 also is guiding element 90 simultaneously; The two is sleeved on the tubular matrix 112 rotationally; When the interior edge face that receives differential carrier 72 supports, and through the screw type that is formed on its interior edge face radially inner side two- way guiding tooth 92a and 92b, respectively and be located axially at that the footpath upwards is sheathed in the endoporus of planet pin 56 between two members; And the intermediate piece 100a and the 100b that are formed with complementary screw type two- way guiding tooth 102a and 102b are chimeric, to form two rotation guide mechanism Ga and Gb regularly.Simultaneously; The face type revolution rubbing surface 110a and the 110b that are arranged on intermediate piece 100a and 100b interior edge face conflict each other; When forming rotary type traction friction pair, also make the mode of this two member, forms one and draw friction mechanism F1 with the friction member 40 that serves as the other side each other.Traction friction mechanism F1 and rotation guide mechanism Ga and Gb are respectively with forming two the circumferential space of face type wedge mechanisms.Obviously, the axial force of these two face type space wedge mechanisms is closed in differential carrier 72.

Obviously; The chisel teeth that in fact a plurality of guiding teeth 92 on guiding element 90 end faces are exactly the space wedge mechanism; Its guide surface 94 upwards draws rubbing surface 110 or 42 near rotary type gradually towards a circumferential square shaft, and surrounds the circumferential wedge shape space of a plurality of face types along extending circumferentially respectively with the latter.And a plurality of guiding teeth 102 that are arranged in these a plurality of wedge shape spaces are exactly wedging, and it not be because of must radial motion be merged into a part best each other, i.e. the intermediate piece 100 of whole ring-type.

Fig. 3～4 show the concrete structure and the relevant profile of tooth relation of intermediate piece 100 grades.The interior edge face of intermediate piece 100 is rotary type rubbing surface 110, circumferentially is evenly equipped with the face type spirally-guided tooth 102 that has trapezoidal cross-section and radially extend on its flange end face best.This guiding tooth 102 has Topland 106 and tooth bottom surface 108, and two lift angle λ _aAnd λ _bOr λ _cAnd λ _dAll be all λ and circumferentially symmetrical fully screw type guide surface 104 best.Accordingly, referring to Fig. 2,4, be evenly equipped with the complementary two-way guiding tooth 92 of equivalent amount on the corresponding end-faces of guiding element 90, it has Topland 96 and tooth bottom surface 98, and two all lift angles all are all λ and symmetrical fully screw type guide surface 94 best.Upwards fully chimeric to form when rotating guide mechanism G when this two members shaft, promptly at least one is when for example Topland 96 is axially conflicted with tooth bottom surface 108, and the G of this mechanism still has the circumferential degrees of freedom/clearance delta greater than zero, i.e. Δ >=0 best.

In addition, differential 80/ guiding element 90 in fact still by intermediate piece 100 as guiding element, differential carrier 72 is as the intermediate piece of another space wedge mechanism of friction member 40.Therefore, if the limiting angle of corresponding lift angle that will this another wedge mechanism is designated as ζ ' and ξ ' (definition is same as ζ and ξ), the best value of above-mentioned lift angle λ just should be ξ '＜λ＜ξ.Like this, do not have in the sliding state of driving action, rotate the inner wall friction self-locking that guide mechanism G just can not cause differential 80 relative differential carrier 72 at planetary pinion 50.Obviously, reduce between the two friction factor or at a distance from all being optional methods with the pad 124 of low coefficient of friction.Preferably, should cause ζ >=ξ ', to obtain bigger design freedom as far as possible.

Apparently, above-mentioned rotation guide mechanism G can have any form in the application's definition, comprises by ball the mechanism of the non-optimised form of members such as roller, voussoir.

Fig. 5 is the schematic diagram of Fig. 2, shows to this schematic diagram simple and clear the structure characteristic of differential mechanism D1.Wherein, rotate guide mechanism G and represent that with the two pairs of teeth of image and the reduced form of groove output shaft is with mark 74 expressions, fixed frame is represented with mark 70.In conjunction with Fig. 2～5, the working procedure of differential mechanism D1 can better be explained and understood.

The same with common symmetric type cone planetary gear differential mechanism, driving torque drives differential carrier 72 and rotates around axis X integratedly with planet pin 56 through input ring gear 58.The planetary pinion 50 that the gear shaft 56 of rotation drives on it rotates around axis X.This planetary pinion 50 drives differential 80a and the 80b that is engaged with, and back two members drive the intermediate piece 100a and the 100b of correspondence respectively again through engagement/wedging relation of guiding tooth 92 with 102, rotate around axis X thereby finally drive two output shafts 74.

When the vehicle linear drives is gone; And the needs that two output shafts 74 of its differential mechanism D1 do not exist differential to rotate; Do not exist external diameter to differ or when not running into situation such as concavo-convex ground such as driving wheel with this coupling; Differential mechanism D1 will present the engagement shown in Fig. 4 B, just follow the usual practice and rotate like arrow S direction.Promptly; When for example with differential the guiding element 90a that 80a is same; Beginning has the initial instant that rotates as the intermediate piece 100b of its friction member 40a relatively along arrow Sa direction among Fig. 4 B constantly; With the intermediate piece 100a of output shaft 74a coupling, with relative guiding element 90a along the arrow Ra direction guide movement that rotates.What this rotation guide movement was produced moves axially/tension force; To lead tooth 102a moment wedging in the circumferential wedge shape space of face type that guide surface 94a and traction rubbing surface 110b are surrounded; That is intermediate piece 100a becomes a friction piece with guiding element 90a with intermediate piece 100b wedging as its friction member 40a; In the time of traction friction mechanism F1a thereby axial engagement, also with guiding element 90a swelling at once on the interior edge face of differential carrier 72.And fully symmetrically, intermediate piece 100b becomes a friction piece with guiding element 90b with intermediate piece 100a wedging as its friction member 40b too.That is; Intermediate piece 100a becomes a rotor with guiding element 90a simultaneously with 100b with the 90b wedging, and by the axial sealing process of differential carrier 72, sets up the closed conflict of stable axial force and connect; Axial engagement power T corresponding to institute's transmitting torque is provided, or claims force-closed power T.

Obviously, the operating mode of differential mechanism D1 shown in Fig. 4 B, also corresponding to the anti-line sliding travelling state that drags motor of vehicle, difference only is to have changed the direction of transmission of torque.Directly get into the line sliding state and work as vehicle; When perhaps changing the reverse direction actuation travelling state over to; Intermediate piece 100a and 100b among Fig. 4 B; Will be synchronously relatively guiding element 90a and 90b turn over the angle of circumference Δ, be transformed to guide surface 94d and 104d and guide surface 94b and 104b to mesh respectively/wedging, two rotation guide mechanism Ga and Gb get into the synchronous drive state once more.Because in all straight-line travellings, differential mechanism D1 has upwards symmetrical fully engagement/wedging and driving relationship of week, so the related work process need not repeat specification.

And drive when going when Vehicular turn, perhaps there are the needs that differential rotates in two output shafts 74 of its differential mechanism D1, and when having external diameter difference or running into situation such as concavo-convex ground such as the driving wheel with this coupling, differential mechanism D1 will get into differential rotation operating mode.Referring to Fig. 2,4,5, because of about complete symmetry, so, produce with the relative left end output shaft of right-hand member output shaft 74b 74a that to transfer toward gesture soon be that example describes and gets final product.In addition, suppose 0＜λ≤ξ especially, that is to say, but the space wedge mechanism is in the jointing state of friction self-locking, its guiding element 90 can not drive the friction member that intermediate piece 100 supports it to axial and trackslip, only if overload.

During the wheeled vehicle normal direction of rotation, the frictional force of ground effects on all driving wheel peripheries forms the torque M that turns to that forces Vehicular turn ₀, this turns to torque M ₀When forcing Vehicular turn, also through with one group of driving wheel of differential mechanism D1 two output shafts 74 coupling, through output shaft 74a and 74b, drive the interior frictional resistance moment M that two differential 80a and 80b overcome differential mechanism D1 _fAnd differential rotates.Equally, if this group of driving wheel external diameter does not wait or runs into concavo-convex ground, under the non-slip normal state,, also will drive differential mechanism D1 and overcome frictional resistance moment M in it from the friction torque on ground _fAnd differential rotates.

Therefore, with reference to Fig. 2,4,5, turn to torque M ₀On the periphery of the driving wheel that a pair of and differential mechanism D1 two output shafts 74 are coupled, be assigned additional torque, to order about the driving wheel quick rotation that driving wheel is relative and output shaft 74a is coupled that is coupled with output shaft 74b.That is, append under the torque on the driving wheel periphery at this, with the direct-coupled intermediate piece 100b of output shaft 74b will overcome itself and intermediate piece 100a, with the Topland 96b of guiding element 90b, and and guide surface 94c between the summation M of frictional resistance moment _f, change soon by relative intermediate piece 100a of arrow Sb direction and the guiding element 90b among Fig. 4 B, just do to remove the rotation of the leading role of rotating guide mechanism Gb.So normal pressure between guide surface 104c and the 94c and the rotation leading role of rotating guide mechanism Gb will disengage disappearing in a flash and simultaneously of trend each other along with two guide surfaces produce.Nature, traction friction mechanism F1 and space wedge mechanism based on the moving axially of the Gb of this mechanism/tension force will separate or separate wedge immediately.Yet; Because the existence all the time of motivational drive torque, therefore, have between guide surface 94c and the 104c above-mentioned disengage trend each other when; Planetary pinion 50 must drive differential 80b adaptively; That is guiding element 90b catch up with intermediate piece 100b immediately transfer toward gesture soon, thereby cause guide surface 94c and 104c fit tightly once more/wedging/engagement to be to continue transmitting driving torque, separate and do not have the substance of any moment.Next, under the effect of above-mentioned additional torque, intermediate piece 100b changes another relative guiding element 90b soon, to attempt to remove wedging/meshing relation of guide surface 94c and 104c.Promptly; Differential rotates among the threshold state formula circulation be in one " separate the wedging of wedge → again → separate again wedge " all the time continuously, and so moves in circles, and finishes to turn to go up to vehicle; Disappear with the additional torque of the driving wheel of output shaft 74a and 74b coupling, or because of less than M _fAnd be not enough to remove till the wedging/meshing relation between guide surface 94c and the 104c.

Understand easily; Constantly follow intermediate piece 100b and relatively in the fast process of changeing of intermediate piece 100a at guiding element 90b; Differential action through planetary pinion 50; Guiding element 90a will have the trend of relative intermediate piece 100a slow-speed, the trend that driven intermediate piece 100a has slow-speed immediately to follow because of the effect of loading.That is to say; Also got between guiding element 90a and the intermediate piece 100a between a guide surface 94a and the 104a in the circulation of " separate the wedging of wedge → again → separate again wedge ", just this circulation is the circulation that intermediate piece 100a constantly follows the relative intermediate piece 100b of guiding element 90a slow-speed trend.This shows, the essence that differential mechanism D1 differential rotates, one all the time in the process of attempting to remove space wedging relation or meshing relation, simultaneously again all the time not in the process of trying hard to keep this wedging or meshing relation exactly.The differential engagement process all fours of planetary pinion and differential gear in this and the common cylinder planetary pinion open type differential mechanism is the same in fact with the differential principle of worm gear and worm screw in the high friction of the turbo type differential mechanism.Therebetween, the cyclic process of " separate the wedging of wedge → again → separate again wedge " is seamless fully, natural and continuous, has no gap and pause among following in sb's footsteps, and has only kinematic active and driven difference in synchronously.And the source of the direct power that this differential rotates; Just remove the torque of wedging/meshing relation and promptly separate the wedge torque; Crucially come from the driving wheel that is coupled with its two output shafts 74, have that driving wheel that transfers toward gesture soon, the for example above-mentioned driving wheel that is coupled with output shaft 74b.

Be not difficult to learn by above-mentioned explanation, when with the driving wheel of output shaft 74b coupling on additional torque, be not enough to overcome frictional resistance moment M in suffered total of intermediate piece 100b _fThe time, guide surface 94c and 104c just can not have the trend that disengages each other, and intermediate piece 100b can not arrive the transition point of separating wedge, and intermediate piece 100a and guiding element 90b change soon relatively, and differential rotates and also just can't realize certainly.Have only two kinds of possibilities and this situation occurs, the one, there is not the differential demand, additional torque equals zero, and the 2nd, the driving wheel that should change relatively soon is in the ground of trackslipping of low coefficient of friction, does not have enough additional torques to act on differential mechanism D1 through this driving wheel.That is to say, even associated drive wheel is on the ground of trackslipping of low coefficient of friction, also will can't differential and can not skid because of differential mechanism D1.Further; Trackslip by driving wheel and must cause the differential mechanism differential to rotate this general knowledge to be not difficult to expect; Even if the driving torque more than needed on the intermediate piece 100b is greater than zero; Even if with the driving wheel of its coupling and the adhesion on ground/torque deficiency or wretched insufficiency, no matter whether turn, this driving wheel all will can not realize that differential rotates and finally can't trackslip because of differential mechanism D1.This driving wheel because skid in the trend possibly not provide differential to rotate to differential mechanism D1 and necessaryly separate the wedge torque, otherwise it can not be in the trend of skidding.Therefore, differential mechanism D1 naturally and understandably possesses has absolute or relative preventing to drive the ability that driving wheel trackslips.

For example, when the driving wheel that is coupled through output shaft 74b and intermediate piece 100b is unsettled, when perhaps traction/the torque of this driving wheel acquisition can be ignored, the whole of driving torque that are assigned on the intermediate piece 100b will be converted into driving torque more than needed at once.And in response to the variation of torque, differential mechanism D1 with synchronous self-adapting change the anti-skidding operating mode that prevents that driving wheel from trackslipping over to.In this operating mode, intermediate piece 100b can have three kinds of working conditions in this specification aforementioned definitions.That is, as lift angle λ≤ζ _Min(work as ζ _MinGreater than zero) time owing to receive driving torque effect from guiding element 90b, like the arrow Sb indication among Fig. 4 B, intermediate piece 100b will be relatively as the intermediate piece 100a of the friction member 40b of its axial support member, unconditionally transfixion.That is, friction mechanism F1 or two output member direct friction self-lockings are just drawn in the traction friction pair self-locking between two members.At this moment, although the relative intermediate piece 100b of guiding element 90b has the trend of trackslipping and climbing, limit receiving differential carrier 72 rigidity on axially, two members can only unitary rotation.That is, guiding element 90b drives intermediate piece 100a and rotates, thereby will have more than needed the whole of driving torque by the traction friction mechanism F1 of friction self-locking, is passed to the output shaft 74a and this side drive wheel of intermediate piece 100a and coupling with it.Among Fig. 5 with half cycle to dashed line form marked the bang path of respective torque stream.So differential mechanism D1 has infinitely-great locking coefficient and skid resistance.Simultaneously, guiding element 90a and 90b, and then two output shaft 74a of coupling with it and 74b and associated drive wheel will have no sluggishly perhaps seamlessly to do as a whole and rotate, restraining the trend that driving wheel trackslips, and the powered vehicle zero slip advance.

And work as ζ _Min＜λ≤ξ _MinThe time; Friction self-locking by guiding friction pair between guide surface 94c and the 104c; Guiding element 90b still can directly drive intermediate piece 100a through intermediate piece 100b and rotate synchronously; With the whole of driving torque that will have more than needed, pass to the output shaft 74a and this side drive wheel of intermediate piece 100a and coupling with it, differential mechanism D1 still has infinitely-great locking coefficient and suppresses the ability that driving wheel trackslips.Have only when the driving wheel with intermediate piece 100a coupling to be stuck when not changeing, traction friction mechanism F1 just can skid because of overload, and therefore differential mechanism D1 just can not possess infinitely-great locking coefficient.But this kind situation is obviously without any need for locking coefficient, because this situation has not been to prevent the driving wheel problem in the technological category of trackslipping.

Last a kind of situation is to work as ξ _MinDuring＜λ＜ξ; Though intermediate piece 100b has the trend that circumferential wedge shape space that part 90b and intermediate piece 100a surrounded slides and extrudes that is directed to all the time; But the axial stiffness by Topland 96b and tooth bottom surface 108b is conflicted, and still can keep the meshing relation of non-self-locking between guide surface 94c and the 104c.So; Guiding element 90b still can be through the traction friction mechanism F1 in trackslipping; Part with its driving torque more than needed; Synchronously pass to output shaft 74a and this side drive wheel of intermediate piece 100a and coupling with it, make differential mechanism D1 have restriction and drive ability that driving wheel trackslips and limited locking coefficient.

And in case obtain enough traction/torques with the driving wheel of intermediate piece 100b coupling; Intermediate piece 100b will obtain the wedge ability of separating that differential rotates immediately; The friction self-locking of itself and intermediate piece 100a does not have again transmission of torque more than needed to intermediate piece 100a same naturally EOS.Obviously, this terminal procedure is complete self adaption and shock-free natural process.

So far, differential mechanism D1 prevents that the working procedure of trackslipping is clear completely.Though what more than be directed against is the explanation of extreme case, understand easily, under non-extreme case; The driving torque more than needed on the intermediate piece 100b just, when the driving torque that planet gear 50 obtains, intermediate piece 100b will have preceding two kinds in above-mentioned three kinds of working conditions less than intermediate piece 100b; And working procedure is identical; Only pairing lift angle interval becomes and is λ≤ζ (when ζ＞0) and ζ＜λ≤ξ, wherein, and ζ＞ζ _Min, ξ＞ξ _MinIn these two kinds of situation, what traction friction mechanism F1 all can be with the driving torque of having more than needed is whole, absolutely is transferred to the driving wheel that is coupled with intermediate piece 100a, and differential mechanism D1 all can reach desirable skidproof effect.So its working procedure need not repeat specification in this.

More than explanation is to the foundation job description with differential mechanism D1 of 0＜λ≤ξ characteristic of the present invention.Clear, except the sliding operating mode (ξ of extreme limit _MinOutside＜the λ＜ξ), the engagement of rotating guide mechanism G all has the essential attributes of wedging.Therefore; Its differential rotates to depend on separates the wedge torque; This separates the additional torque that the wedge torque is derived from relevant couple drive wheel, and can not depend on the driving torque (this driving torque only provides wedging power for the space wedge mechanism, can only be used to keep the wedging state uniquely) of 50 pairs differential 80 of planetary pinion; And therefore had infinitely-great locking coefficient, and best the preventing ability of trackslipping.

In addition, know that when ξ＜λ＜90 were spent, according to differential mechanism D1 of the present invention, no matter be in any state and any direction, it rotated the guiding tooth 92 of guide mechanism G and 102 engagement, does not have the essential attributes of wedging by the definition of ξ.Therefore, the differential in this situation rotates will not need to separate earlier wedge, just not need additional torque necessarily greater than interior frictional resistance moment M _f, only rely on the driving torque that obtains from planet gear 50, can directly drive intermediate piece 100 and rotate to realize differential.Nature, therefore differential mechanism D1 will not have infinitely-great locking coefficient, can only limit to trackslip and can not suppress or prevent to trackslip, just as above-mentioned to ξ _MinThe explanation of the sliding operating mode of limit in＜λ＜ξ situation.Rotate guide mechanism G in effect wherein, through friction swirl gear F1 being applied the mode of axial pressure, increase the interior frictional resistance moment M of differential mechanism D1 exactly _f, with the locking coefficient of acquisition needs.Be not difficult thus to reach a conclusion; Except the architectural difference of having explained; The working mechanism essence of cone planetary gear differential mechanism that has friction plate in differential mechanism D1 in this situation and the existing technology is identical, so the application does not do repeat specification to its working procedure.

As stated, differential mechanism D1 axial and circumferential structure is symmetry fully, so; The relative 74b of its output shaft 74a produces the differential working procedure when transferring toward gesture soon, and, the differential working procedure when reverse direction actuation is gone; Prevent the working procedure that driving wheel trackslips under the perhaps various travelling states; All identical or be similar to, so, need not to give the secondary explanation.The situation that need not repeat specification equally also comprises, the differential mechanism D1 working condition in the anti-sliding curve state that drags motor.Because difference only is that institute's torque transmitted is a negative value, and the wedge torque is just separated in the source of the direct power that its differential rotates, and crucially comes from that driving wheel with slow-speed trend in the driving wheel that is coupled with its two output shafts 74.And, the differential mechanism D1 working condition in the neutral gear sliding curve state.Because as previously mentioned, the value of lift angle λ has guaranteed, is in the 90a of guiding element fully freely and the 90b of non-driven state, relatively the interior edge face friction self-locking of differential carrier 72.Therefore, as long as the additional torque on the relevant couple drive wheel is enough, intermediate piece 100a and 100b just can overcome the comprehensive frictional resistance moment from traction friction mechanism F1 and differential carrier 72, drive guiding element 90a and 90b differential respectively and rotate.

Be not difficult to find that the differential mechanism D1 in the present embodiment is a torque induction type no-spin lockup that only is sensitive to differential torque/additional torque by above-mentioned explanation.It is by the direct friction of the traction friction mechanism F1 between two output members; So that space wedge mechanism friction self-locking; Thereby the mode with the direct friction self-locking realizes the interlocking between its output member, finally reaches and redistributes driving torque, and prevent or limit the purpose that driving wheel trackslips.There is not any circulating power therebetween.And whether depend on adaptively in response to wherein driving torque more than needed, greater than zero and when greater than zero its opportunity that whether changes anti-skidding operating mode over to and change over to fully.Both are complete not to exist the delay on any time therebetween synchronously with giving birth to going out, more irrelevant with the rotating speed size, irrelevant with the size and the change frequency of driving torque more than needed.The ability and the promptness of its reallocation torque are higher than all artificial control system.And, as λ≤ξ _MinThe time, differential mechanism D1 has the skid resistance of dealing with all egregious cases, comprises the situation that output shaft 74 fractures or do not have from root, just its inner axial force, wearing and tearing and M _fMaximum relatively.And work as ξ _MinDuring＜λ≤ξ, except extreme case, differential mechanism D1 has and can be rated as best preventing and trackslip and the torque distribution ability, has possessed the speciality that is applicable to all differential positions.And when ξ＜λ＜90 were spent, differential mechanism D1 was specially the broad limited-slip differential of a locking coefficient span, its inner axial force, wearing and tearing and M _fMinimum relatively, be very suitable for drive axle and use.And expansion ground, when λ=0 was spent, differential mechanism D1 did not have torque output, and when λ=90 were spent, differential mechanism D1 was equal to an open type differential mechanism that does not have any anti-slip function.

What should explain in passing is, about two the limiting value ζ and the ξ of lift angle, this specification has provided literal definition clearly, need not through any performing creative labour, and those skilled in the art can define thus and derive its functional relation.And can find that ζ and ξ are drag torque/load torques that is proportional on the interior or outer peripheral surface that acts on intermediate piece 100, just be proportional to the dynamic parameters of the traction/torque of the driving wheel that is coupled with this member.This characteristic helps promoting the skid resistance of common vehicle.As extreme value wherein, ζ _MinAnd ξ _MinIt then is a structural parameter that only depends on friction factor and physical dimension; Its numerical value is big more; The interval of guide surface lift angle λ that can obtain infinitely great locking coefficient is also just big more; The design freedom that locking coefficient is controlled on the interior any number in interval [1, ∞] is just high more, and corresponding inside axial thrust load T will be more little.Simultaneously, also help its interior frictional resistance moment M of reduction _f, to be applied to steering drive axle better.But this dynamic characteristic also has the unfavorable one side of the design freedom of compression lift angle λ.That is,, might when underloading, exceed dynamic ξ according to normal/λ that average load design draws, perhaps when heavy duty less than dynamic ζ, influence the normal differential of differential mechanism D1 or the possibility of anti-skidding self-locking thereby exist.

With existing technology can't change its friction self-locking lift angle different be to be all under 0.1 the situation ξ of present embodiment at friction factor _MinNot only be about two times that about 5.7 of existing technology is spent, and have more the lift angle extreme value ζ that several different methods comes to promote on demand correspondence _MinAnd ξ _MinBe beneficial to enlarge the design freedom of no-spin lockup D1, promote its combination property, be beneficial to self-locking mechanism under same self-locking coefficient situation, produce the axial force littler than existing technology to enlarge its application area.Such as; With the angle of the revolution rubbing surface 110 in the axial plane or guide surface 94,104 and axis X, be arranged to be not equal to the cone angle (that is any angle between 0 degree～180 degree) of 90 degree; That kind perhaps as shown in Figure 9 will be drawn friction mechanism F1 and will be arranged to friction plate mechanism more than.For example, when two pairs of friction factor being set respectively equaling 0.1 friction plate, ζ is arranged just _Min=14.04 degree and ξ _Min=32.28 degree.

Be understood that; Under the identical prerequisite of differential carrier, on the one hand, with respect to axis X; The turning radius of the tooth face meshing point of Worm gear mechanism in the high friction of the worm-gear type differential mechanism, the turning radius of comparing planetary pinion 50 and differential 80 awl tooth contact points among the differential mechanism D1 is obviously for little.On the other hand, the spiral helical teeth transmission capacity of Worm gear mechanism obviously is low compared to straight bevel gear.On the one hand, the transmission capacity of the rotation guide mechanism G of face contact type obviously is higher than bevel gear drive mechanism again.Therefore, according to the torque bearing capacity of differential mechanism D1 of the present invention, with the high friction of the worm-gear type that is significantly higher than existing technology differential mechanism.Especially, in the anti-skidding operating mode, because driving torque more than needed is through same Worm gear mechanism stack transmission, so the nominal operation torque of the high friction of worm-gear type differential mechanism will be littler, and be inversely proportional to its locking coefficient.On the contrary; According to the driving torque more than needed among the differential mechanism D1 of the present invention, and without same planetary gears and rotation guide mechanism G, but through traction friction mechanism F1; Just directly transmit between two intermediate pieces 100 at two output members; By after 114 stacks of the spline tooth in latter's endoporus, directly be passed to corresponding output shaft 74 again, its nominal operation torque just equals its anti-skidding bearing capacity.Two compare, and differential mechanism D1 need not to tackle the impact of driving torque more than needed because of relevant engaging mechanism, and has stress height advantage stably, and it is more remarkable more greatly that the relative advantage of its bearing capacity just becomes.

And corresponding to as stated; Suppose that the differential mechanism total load stablizes constant; So, along with the variation or the acute variation of traction/torque, the force-bearing situation of Worm gear mechanism in the high friction of the worm-gear type differential mechanism; The inevitable variation constantly or acute variation, driving torque more than needed dynamically will be aggravated the wearing and tearing of this mechanism; And review the differential mechanism D1 in the same situation, it is constant that its planetary gears and rotation guide mechanism G power transmission situation will be stablized, and acceptance driving torque impact dynamically more than needed, can slow down the traction friction mechanism F1 of pulsed torque shock ends dynamics exactly.So the structural strength of its inner associated mechanisms need not to do any particular design because of friction self-locking, because its traction friction mechanism F1 has set up a driving torque without planetary pinion 50 and directly transmitted/reallocate the path between two output shafts 74.Therefore.Compare through two of force-bearing situation, the structure superiority of foundation differential mechanism D1 of the present invention seems more obvious, and it is not only simpler, and is more reasonable, more reliable, has more directly improved performance and life-span, makes that the torque of output is more steady.And obviously, differential mechanism D1 only has the technology difficulty of common open type differential mechanism, and this is the entry level level that any one open differential factory all possesses.It is thus clear that, not only relative worm-gear type, and all anti-skidding or limited-slip differentials of the prior art relatively, the present invention has the manufacturing of being easy to, the cordwood assembling, and with low cost, highly reliable and long-life advantage.

Also have with corresponding as stated; Traction friction mechanism F1 is because of its mean friction radius; That compares worm gear pair in the existing technology significantly has less slip line speed for little, but also because of its lower pair profile contact, and have surface contact stress far below line contact worm gear higher pair.So, according to differential mechanism D1 of the present invention, not only have the frictional strength and the rate of wear, and therefore need not the high-strength wearable material far below existing technology, and, have more the ability of the not available automatic compensation mechanical wear of the latter.In addition; Rotate that guide mechanism G has face contact lower pair equally and advantage that contact stress is given no cause for anxiety; In addition in the whole Life cycle, the G of this mechanism exists hardly and trackslips relatively and mechanical wear, also more has the ability that the self adaption axial spacing changes because of its screw type guide surface.So differential mechanism D1 is insensitive to above-mentioned mechanical wear, can both stable performance ground proper functioning in the whole operating life.Even if excessive wear needs repairing, also only need to change intermediate piece 100 and get final product, not only with low cost but also convenient and simple.Therefore, aspect Economy and working service, the relative existing technology of the present invention has unrivaled superiority equally.

Fig. 2,5 is analyzed the discovery of just being not difficult a little, essential two the space wedge mechanisms of differential mechanism D1.Promptly; Remove wherein any one rotation guide mechanism Ga or Gb; For example intermediate piece 100b and differential 80b/ guiding element 90b directly are merged into a part; Differential mechanism D1 is differential and self-locking normally, and original performance and force-bearing situation will not have the change of any essence, and differential position in the middle of being more suitable for.And further, the Placement of guiding element 90a and differential 80a also can be by the rigidity one, and the friction by traction friction mechanism F1 that change into non-the best links to each other, referring to Fig. 6, especially when 0＜λ≤ξ.In this modification no-spin lockup D2, differential 80a be as friction member 40a, and what left end was used to export torque is guiding element 90, and it links to each other through power transmission friction mechanism F2 direct friction with differential 80b of right-hand member.For guaranteeing the reliability of anti-skidding self-locking; That is assurance intermediate piece 100 is gone into the reliability of wedge; Also best at least one axial notch of tooth 102 tooth bottom surfaces that for example leads; Be provided with the corresponding helical compression spring 150 of conflict, to impel routinely friction fit/wedging of traction friction mechanism F1 to tooth 92 Toplands that lead.The working procedure of differential mechanism D2 is quite analogous to, no longer repeat specification.But be to be noted that guiding element 90 is intermediate pieces of a relative mistake moving part 80b.

Certainly, differential mechanism D2 also can do such modification.That is, will rotate guide mechanism G and be set between differential 80a and the intermediate piece 100, the tooth 102 that just will lead is set on the end face of differential 80a, thereby makes guiding element 90 become friction member 40 because of only having the disk-shaped flange modification.But still normally differential and self-locking skidproof of this modification apparently.And, the limiting angle ζ among itself and the differential mechanism D2, all be one with the irrelevant parameter of confirming of load torque/drag torque, and uncertain non-dynamic parameters.Therefore, with the possibility of lift angle λ not occurring less than ζ.That is to say, differential mechanism D2 and this modification do not exist because of the relative load torque of additional torque less, and in the differential operating mode self-locking maybe (the Torsen differential mechanism promptly has this kind situation).

In addition; Shown in the subsequent implementation example; The present invention does not limit the type or the structure of differential mechanism, and in fact, any differential mechanism of two mobilities all has makes it be able to exist and have the revolving meber of two coaxial lines rotations of fundamental function; No matter this axis is the rotational axis X of differential mechanism, or the rotation axis of planetary pinion 50 etc.Therefore; The present invention can be specially the differential mechanism of all forms, comprises symmetric type and asymmetric formula differential mechanism, and gear type and non-gear differential are (like turbo type, slider cam formula and free wheel type; Some is unnecessary although seem), variable ratio and variable ratio formula differential mechanism etc. not.

In addition, what be necessary to explain is to compare with the high friction of turbo type of the prior art differential mechanism; Although have various structure,, all be the friction self-locking effect of utilizing engagement pair owing to realize that the technological thought of self-locking is the same according to differential mechanism D1 of the present invention; So; The same with existing technology, differential mechanism D1 can realize coupling with any speed changer, transfer case too, can accomplish that nature is compatible with electronicss such as the ABS of other safety control class on the vehicle, TCS, ESP.

Visible by above-mentioned explanation of the present invention, according to the no-spin lockup that includes the space wedge mechanism of the present invention, have very strong versatility and adaptability.It can be applied to the place of nearly all needs, propons for example, and back axle, between the bridge of how coherent general formula ransaxle, middle transfer case etc.How many ransaxles no matter all can realize the complete adaptive full-time full wheel drive of wheeled vehicle easily, and ransaxle are many more, and its superiority is remarkable more greatly more, and superiority of effectiveness is also outstanding more.Greatly simplify the differential antiskid system of wheeled vehicle, when guaranteeing reliable, slip-resistant, also abandoning all these unessential non-mechanical means, significantly promoting the reliability of traction aid and the maneuverability of vehicle, significantly reducing fabricating cost.Therefore, the present invention will help the popular and generalization of the full-time all-wheel powered of wheeled vehicle.

Need to prove; Seeing that the structure and the working mechanism of box of tricks have been the known technology that is widely known by the people; And the structural symmetry that has of differential mechanism or the characteristics of similarity; Those skilled in the art can understand without doubt, cast aside beyond vehicle heading and drive condition different of concrete correspondence, before and after working between the wheel of bridge, between the bridge of front and back/working procedure and mechanism middle and that connect the differential mechanism between the bridge all are identical.So the subsequent section of this specification will no longer repeat it and comprise the working mechanism or the process of trackslipping of preventing, and only the distinguishing characteristics of various structure etc. is done necessary explanation.

Embodiment two: the space wedge mechanism does not transmit the no-spin lockup D3 of driving torque

Referring to Fig. 2; Wherein, As long as two tubular matrix 112 that will form as one respectively with two intermediate pieces 100; Be modified to two differential 80 be merged into a hard parts (can referring to Figure 16 of axial opposed) respectively, to constitute the output member of differential mechanism, just can obtain schematic diagram no-spin lockup D3 shown in Figure 7.

Obviously, separate the wedge torque because intermediate piece 100 no longer can access, therefore, the lift angle λ that rotates guide surface among the guide mechanism G can only value λ＞ξ _MinSimultaneously, owing to almost do not have drag torque, so ξ=ξ _Min, and no longer be a dynamic parameters, this will help the stable of design parameter and skidproof effect.So, in the nominal situation, rotate guide mechanism G and no longer transmit driving torque.Therefore, can know that when differential rotated, the surface friction drag among its traction friction mechanism F1 was less, and almost it doesn't matter with the size of driving torque by the application's related definition.And in case get into the operating mode of trackslipping; Be intended to the major part of fast differential 80 of changeing with the driving torque of will having more than needed adaptively at once; Be used to drive corresponding rotation guide mechanism G revolution, with the axial pressure of increase traction friction mechanism F1, and through the F1 of this mechanism; This part driving torque more than needed is delivered to does not have the driving wheel of trend one side that skids, thereby effectively limits trackslipping of respective drive wheel.This scheme is compared differential mechanism D1 and is more suitable in steering drive axle, can obtain good manoeuvring performance.

As stated, an elastic element such as stage clip that acts on intermediate piece 100 should be set best, for example by helical compression spring 150 shown in Figure 6, to guarantee the reliability of differential mechanism D3 work.

Be not difficult to find through the explanation of present embodiment; Tubular matrix 112 in fact can with any member that rotates among the guide mechanism G; Form as one for perhaps differential 80, to constitute the output member of differential mechanism, simultaneously; Output member, rotating guide mechanism G all can axial asymmetric layout with traction friction mechanism F1 three.For example; Referring to Fig. 7; To rotate guide mechanism Ga transforms between differential 80a and the differential carrier 72; So that intermediate piece 100a and 100b form traction friction mechanism F1a and F1b with differential carrier 72 with differential 80a respectively, and couple directly to intermediate piece 100a with output shaft 74a, be exactly a middle preferably no-spin lockup scheme.

Understand easily,, guaranteeing that differential mechanism D3 also can make following modification under the constant situation of original function referring to Fig. 7.That is, guiding element 90a, 90b are formed on respectively on the both ends of the surface of ring in the cross planet pin 56, so that intermediate piece 100a, 100b form traction friction mechanism F1a, F1b with the interior edge face of differential 80a, 80b respectively.At this moment, two revolving mebers are respectively planet pins 56 and differential 80.

Described in embodiment one; Remove among the differential mechanism D3 any one and rotate for example Gb of guide mechanism; With reference to Fig. 7; And constituting traction friction mechanism F1b by the intermediate piece 100a that keeps and its differential 80b that axially directly faces as friction member 40, any change can not take place in original function and the force-bearing situation of this differential mechanism D3.Further, also can be again with the Placement of guiding element and differential 80a, the friction of being changed into by traction friction mechanism F1a by the rigidity one links to each other, and just can obtain differential mechanism D4 as shown in Figure 8, and its function does not change, and structure is simpler.Wherein, continue the guiding element that chimeric intermediate piece 100a and 100b serve as the other side each other, differential 80a and 80b then serve as the friction member 40 of corresponding intermediate piece 100 respectively.

This shows; The present invention is outside the agent structure with the basic box of tricks shown in the subsequent implementation example; Also can have in the self-locking skidproof structure aspects of key the quantity of rotating guide mechanism G and whether symmetric arrangement, traction friction mechanism F1 quantity and whether symmetric arrangement and tubular matrix 112 and what member rigidity one be between the output member of differential mechanism, carry out the degrees of freedom of various modular design.Compare existing technology practical requirement to a greater degree, simultaneously, also represented its relative merit once more.

Embodiment three: the differential mechanism D5 with the direct friction self-locking in independent space

Present embodiment is still the modification to embodiment one, and purpose is that a traction friction mechanism F1 with many friction disk types of the big turning radius is set for ease, finally to obtain bigger limiting angle ζ _MinAnd ξ _MinFig. 9,10 shows its structural drawing and schematic diagram respectively.

Referring to Fig. 9, compare differential mechanism D1, rotation guide mechanism G among the differential mechanism D5 and traction friction mechanism F1, the footpath upwards no longer is limited by box of tricks.For this reason, guiding element 90 is independent respectively with differential 80, and interconnects through spline pair.Wherein, The tube body that the Xiang Yiduan of guiding element 90a extends; Be supported on rotationally on the ladder interior edge face in the differential carrier 72a endoporus through pad 126; Be formed with external spline teeth 88a on its end outer circumferential face, and with inner hole surface on be formed with complementary inner spline gear 84a differential 80a non-rotatably link to each other.The tube body that the Xiang Yiduan of differential 80b extends; Be supported on rotationally through pad 124 on the interior edge face of differential carrier 72b; Be formed with inner spline gear 84b on its end inner peripheral surface, and with outer circumferential face on be formed with complementary external spline teeth 88b guiding element 90b non-rotatably link to each other.

For friction plate is installed, the inside and outside radially position of the revolution rubbing surface 110a of intermediate piece 100a and 100b and 110b is respectively arranged with the inside and outside flange of annular end face formula.By spline pair, comprise one group of interior friction plate 122 of one at least, non-rotatably be connected on the outer circumferential face of this inward flange, with interior friction plate 122 axial staggered one group of outside friction disc 120, then non-rotatably be connected on the inner peripheral surface of this outward flange.

Obviously, also can obtain the technique effect of present embodiment through other form.Such as, the differential mechanism D6 shown in Figure 11～13 is just simpler.In fact, differential mechanism D6 is exactly according to the improvement of thought of the present invention to the symmetric type spur-gear differential of known technology.It has at least one pair of in axial middle part intermeshing straight tooth column planetary pinion 50a and 50b, axial anodontia section 54a of the two and 54b conflict respectively on the interior edge face of differential carrier 72b and 72a.Referring to Figure 12; Planetary pinion 50a and 50b; Be housed in respectively among the axially extended planet cylinder groove 76a and 76b of differential carrier 72b, and protrude from the wheel toothed portion of latter's notch with utilizing internal diameter, respectively with each self-corresponding differential 80a and 80b engagement that is specially straight toothed spur gear.Wherein, with the same among the differential mechanism D1, differential 80 same with guiding element 90, and have identical rotation guide mechanism G, and draw friction mechanism F1 with the identical many friction disk types of differential mechanism D5.

Here, as long as be provided with the angle of planetary pinion among Figure 11 50 and axis X to such an extent that be not equal to zero, can be modified to asymmetric no-spin lockup again.

In addition, as stated, also can be with intermediate piece 100a and the guiding element 90a of differential mechanism D5 and D6; Directly be merged into a part; To obtain the saving simplified structure that rotates guide mechanism Ga, in the time of simplified structure, any material change can not take place in the two original function and force-bearing situation.Be understood that although be not best, the space wedge mechanism also can be arranged in another axial force enclosing housing outside the differential carrier 72.

The differential mechanism D7 of four: two each other indirect friction self-lockings of output terminal of embodiment

Present embodiment has two planetary pinions 50, an all-in-one-piece differential carrier 72, and the modal differential mechanism/mechanism form of an in-line planet pin 56, is the modification to differential mechanism D1 equally.Wherein, planet pin 56 is through any suitable components, and is fixing such as the relative differential carrier of stop pin 72, perhaps, and through chimeric snap ring in the circular groove of each end of planet pin 56.

Shown in Figure 14～15; Differential mechanism D7 compares the maximum difference of differential mechanism D1～D6 and is; Two revolving mebers be specially differential 80 with differential carrier 72, and as the key components of output member, direct friction no longer between intermediate piece 100a and the 100b; But respectively with two interior edge face mutual friction mutually as the differential carrier 72 of main revolving member, to form two traction friction mechanism F1a and F1b respectively.This is equivalent to insert the friction plate that is served as by differential carrier 72 between the revolution rubbing surface 110a and 110b in differential mechanism D1, causes the direct friction between two members to be modified to indirect friction.And the relative velocity when reducing friction and need to transmit the friction torques through differential carrier 72, the traction friction mechanism F1 among two embodiments, the mechanism of rotating guide mechanism G and differential and self-locking do not have the essence difference.Certainly, the axial force that planetary pinion 50 brings has increased the equivalent coefficient of friction that draws friction mechanism F1, can bring ζ _MinAnd ξ _MinUseful increase, with the chance of many friction plates of demaning reduction.Perhaps bring the bigger ζ of acquisition _MinAnd ξ _MinChance.Obviously, relative differential mechanism D1, the simple more and easy to understand of the structure of present embodiment.

Be not difficult to expect; Planet pin among Figure 15 56 and output shaft 74b are arranged to hollow structure; To make things convenient for the output of output shaft 74a and 74b homonymy, directly drive differential carrier 72 revolutions from the left side by a live axle again, differential mechanism D7 is the no-spin lockup that is applicable to through live axle with regard to various type.

It is pointed out that differential mechanism D7 must have two rotation guide mechanism Ga or Gb simultaneously.

Obviously, with reference to embodiment two thought, present embodiment also various type is the differential mechanism D8 shown in Figure 16～17, and a locking coefficient is not equal to infinity equally, is more suitable for the no-spin lockup in steering drive axle but compare differential mechanism D7.Wherein,, transfinite, specially be provided with tubulose force bearing ring 130 among the differential mechanism D8 because the effect of rotating guide mechanism G for avoiding the contact strength of planetary pinion 50 and differential 80 both sides' gear teeth flank of tooth.This ring 130 is through its two penetrability cylindrical holes that hold planet pin 56 that directly upwards are provided with; Be fixed between two planetary pinions 50; Conflict respectively on its end face axial to two guiding element 90a, 90b, to stop the excessive compressing of 90 pairs of planetary pinions 50 of guiding element.

Similar with the situation among the differential mechanism D3, guaranteeing that differential mechanism D8 also can make following modification under the constant situation of original function.That is,, guiding element 90a, 90b are formed on respectively on two interior edge faces of differential carrier 72, so that intermediate piece 100a, 100b form traction friction mechanism F1a, F1b with the exterior edge face of differential 80a, 80b respectively with reference to Figure 17.

Different with differential mechanism D7 is, because the F1 of mechanism is effective all the time, removes any one rotation guide mechanism Ga or Gb among the differential mechanism D8, and differential mechanism D8 is the normally anti-skidding self-locking of differential and bilateral still.Change when only being anti-skidding self-locking, drives the driving torque more than needed of the non-output shaft 74 that trackslips, have along with the difference of this axle position and pass through and without the difference of planetary pinion 50.Therefore gear engagement mechanism needs to improve margin of safety.

Be not difficult to expect, can copy rotation guide mechanism G and traction friction mechanism F1 among Fig. 8 fully, single rotation guide mechanism G is set on the planet axis between two planetary pinions 50 56.Intermediate piece 100 and a planetary pinion 50 constitute traction friction mechanism F1, and guiding element 90 and another planetary pinion 50 rigidity one are perhaps with another traction friction mechanism of its formation.To limit the form in relative rotation of 50 of these two planetary pinions, can reach equally the purpose that makes differential mechanism have the ability that above-mentioned restriction trackslips.

Be understood that, also can be arranged on beyond the differential carrier 72 with traction friction mechanism F1 rotating guide mechanism G, with connect this shell 72 with the output shaft 74 non-rotatable any revolving mebers that link to each other.

Visible by above-mentioned explanation; The differential mechanism of direct friction self-locking and indirect friction self-locking; The quantity of both necessary rotation guide mechanism G and inequality, the former is merely one, and the latter whether will look its driving torque be one or two via rotating the difference that guide mechanism G transmits.

Expansion embodiment

Figure 18 shows the schematic diagram of single cylindrical planetary gear formula no-spin lockup D9.Wherein, the tapering of the input ring gear 58 on differential carrier 72 outer edge surfaces is zero, and its inner hole surface is provided with gear ring 64, and drives planetary pinion 50 rotations with this.Differential 80a, 80b are specially central gear 62 and planetary gear carrier 66 respectively, and guiding element 90 is same with differential 80a.Output shaft 74a, 74b directly are coupled with intermediate piece 100 and differential 80b respectively.Differential 80b and intermediate piece 100 are formed traction friction mechanism F1, and the axial force of space wedge mechanism is closed in differential carrier 72.

Figure 19 has provided the schematic diagram of bicylindrical planetary gear type no-spin lockup D10.Wherein, input ring gear 58 forms as one with differential carrier 72, and differential 80a, 80b are specially planetary gear carrier 66 and central gear 62 respectively, and 90 of guiding elements are same with differential 80b.Just in time opposite with differential mechanism D9, output shaft 74a, 74b directly are coupled with differential 80a and intermediate piece 100 respectively, and back two members are formed single traction friction mechanism F1.And different with above-mentioned all embodiments be that in the present embodiment, the axial force of space wedge mechanism is closed in the planetary gear carrier 66.Certainly, if make differential carrier 72 have two revolution end faces once more, above-mentioned axial force still can be closed in wherein once more.Obviously, differential mechanism D10 is suitable as the middle differential mechanism of wheeled vehicle.

Differential mechanism in the middle of being suitable as equally also has bicylindrical dual planetary gear formula no-spin lockup D11 shown in figure 20, and this differential mechanism D11 also is suitable for the through live axles that join ransaxles more.Generally, the driving torque of differential mechanism D11 is imported into from the one of which end through input shaft 60, and with direct driving central gear 62a, its output torque is then exported respectively with output shaft 74 by the output gear 68 of its other end.Wherein, Differential 80a, 80b are specially central gear 62b and planetary gear carrier 66 respectively; Guiding element 90 is still same with differential 80a; Output gear 68 directly is coupled with differential 80b, and output shaft 74 directly be coupled with intermediate piece 100, and differential 80b draws friction mechanism F1 with intermediate piece 100 compositions.The axial force of space wedge mechanism still is closed in the planetary gear carrier 66.

Figure 21 has provided the another kind of no-spin lockup D12 that is suitable for through live axle, and it has the basic structure form of single cylindrical planetary gear formula differential mechanism.But different with differential mechanism D9 is, its driving torque is imported into from the one of which end through input shaft 60, and with direct driving planetary gear carrier 66, its output torque is then exported respectively by output gear that is arranged on its two ends 68 and output shaft 74.Wherein, differential 80a, 80b are specially central gear 62 and differential carrier 72 respectively, guiding element 90 and differential 80a rigidity one.Output gear 68 directly be coupled with intermediate piece 100, and output shaft 74 directly is coupled with differential 80b, and differential 80b forms with intermediate piece 100 and draw commentaries on classics friction mechanism F1.Equally, the axial force of space wedge mechanism is closed in the differential carrier 72.

Figure 22 shows a kind of planetary no-spin lockup D13 of circular cone of indifferential device shell, and it is suitable for through live axle equally.Its driving torque is imported into from the one of which end through input shaft 60 equally, and with the planet pin 56 of direct driving as planetary gear carrier 66, its output torque is then exported respectively by output gear that is arranged on its two ends 68 and output shaft 74.Wherein, output gear 68 and intermediate piece 100a coupling, output shaft 74 directly is coupled with intermediate piece 100b.Differential 80 still with guiding element 90 rigidity one. Intermediate piece 100a, 100b and planet pin 56 are formed two traction friction mechanism F1a and F1b respectively.The axial force of space wedge mechanism is closed in the fixed frame 70, and 60 of input shafts are realized axial restraints by its shaft shoulder 128.

Need to prove that above-mentioned expansion embodiment all remains with absolute anti-skidding potentiality.Certainly, also can be with reference to Fig. 7, the differential mechanism D3 shown in 17, D8, the exceed no-spin lockup of sliding type of modification.That kind is all used the space wedge mechanism that includes only a rotation guide mechanism G with regard to can be simplified structure.

Below only be to the present invention is directed to description and the diagram that its limited embodiment gives; Has particularity to a certain degree; But it should be understood that mentioned embodiment and accompanying drawing all only are used for illustrative purposes, and be not used in restriction the present invention and protection domain thereof; Its various variations, the layout that is equal to, exchanges and change structure or each member all will be considered to not be separated from spirit and the scope that the present invention conceives.

Claims (10)

1. a no-spin lockup that includes the space wedge mechanism comprises: can be around rotating relatively two revolving mebers of same axis; It is characterized in that: between these two said revolving mebers, be provided with rotating at least one the space wedge mechanism of coaxial line.

2. by the described no-spin lockup of claim 1, it is characterized in that: said space wedge mechanism comprises

But around the traction friction mechanism of same axis revolution and axial engagement, it has intermediate piece and the friction member that turns round and be provided with rubbing surface around said axis, between this two member, to transmit friction torque; Said friction member is in the said intermediate piece of two said revolving mebers and another space wedge mechanism;

For said traction friction mechanism provide engaging force and around said axis rotating at least one rotate guide mechanism, it has around said axis revolution and is provided with the guiding element and the said intermediate piece of corresponding guide surface;

The lift angle λ at the mutual conflict position between said guiding element and said intermediate piece both sides' the said guide surface is greater than 0 degree and less than 90 degree.

3. by the described no-spin lockup of claim 2; It is characterized in that: when said guiding element and said friction member can be connected into a friction piece drivingly by said intermediate piece, the lift angle λ at the mutual conflict position between said guiding element and said intermediate piece both sides' the said guide surface was greater than zero and smaller or equal to ξ; Promptly; 0＜λ≤ξ, wherein, ξ is the maximum value that can make the said lift angle λ of the guiding friction pair self-locking that is formed at said conflict position.

4. by the described no-spin lockup of claim 3; It is characterized in that: said lift angle λ is greater than ζ, that is, and and ζ＜λ≤ξ; Wherein, ζ is the minimum value of said lift angle λ that can make the guiding friction pair self-locking at said conflict position, also is the maximum value that makes the said lift angle λ of said intermediate piece and the self-locking of the inconsistent formed traction friction pair of said traction friction mechanism face, and the implication of ξ is the same.

5. by the described no-spin lockup of claim 3, it is characterized in that: when ζ＞0, said lift angle λ is smaller or equal to ζ, that is, 0＜λ≤ζ, wherein, the implication of ζ is the same.

6. by each described free wheel device of claim 1～5; It is characterized in that: the said guide surface of said guiding element and said intermediate piece is the screw type flank of tooth, and it is arranged on said guiding element and the surface that comprises end face, inner peripheral surface and outer circumferential face that said intermediate piece both sides face mutually; In axial plane, the angle between this screw type flank of tooth and the said axis is greater than 0 degree, less than 180 degree.

7. by each described free wheel device of claim 1～5, it is characterized in that: also comprise the elasticity pre-tightening mechanism that has an elastic element at least, it is used for keeping constantly said intermediate piece to be connected with indirect at least friction between the said friction member.

8. by each described free wheel device of claim 1～5, it is characterized in that: at least one in said traction friction mechanism and the said power transmission friction mechanism, its two corresponding rubbing surfaces be the half cone drift angle greater than 0 degree the frusto-conical surface less than 180 degree.

9. by each described free wheel device of claim 1～5; It is characterized in that: said traction friction mechanism is many friction disk types friction mechanism, and it has two groups of axially staggered each at least one friction plates that non-rotatably are connected respectively with said friction member and said intermediate piece.

10. by each described free wheel device of claim 1～5; It is characterized in that: said power transmission friction mechanism is many friction disk types friction mechanism, and it has two groups of axially staggered each at least one friction plates that non-rotatably are connected respectively with said friction member and said guiding element.

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