CN1065041A - Inner shelving vehicle wheel hanging - Google Patents

Abstract

Automotive wheel of the present invention hangs, and adopts very better way physical construction, makes vehicle body naturally and understandably reach to the inside when automobile turning, also promptly to the center of curvature direction canting of turnings, feels nature and comfortable thereby make to take.In addition, when travelling on bevelled ground, wheel suspension of the present invention also can make vehicle body keep near horizontal state.Because structure simple and reliable, manufacturing and designing of suspension gear of the present invention is very easy, and maintenance is the same convenient with prior art also, so with low cost.

Description

Inner shelving vehicle wheel hanging

The present invention relates to the suspension of automotive wheel, relate to the interior canting independent suspension of the independent suspension of automotive wheel, particularly automotive wheel specifically.

Characteristics of the present invention are, when automobile travels when for example turning as curve, the chassis (this paper indication chassis all is not to be with hanger) that the automobile that the present invention hangs is housed will be towards the center of curvature canting of running route, as bicycle inside canting when turning together with vehicle body.And the automobile that conventional suspension gear is housed is when travelling as curve, and its chassis always towards the opposite direction canting of the center of curvature of running route, also is outside canting together with vehicle body.

In the prior art, the suspension of automobile generally has three types.For having the suspension of (or claiming bridge) of rigidity wheel shaft, left and right sides wheel is bound up rigidly by this rigidity wheel shaft than oldfashioned one class, and the chassis is bearing on the wheel shaft of front and back (Fig. 1) such as steel spring or coil spring then by certain springing.Second class is that four wheels are connected on the chassis by four rocking arms respectively, is furnished with the spring bearing load between rocking arm and the chassis in addition, and wheel then is contained on the rocking arm, does one motion (Fig. 3) with rocking arm.The 3rd class is that four wheels are connected on the chassis by four rocking arms and four pull bars respectively, is furnished with the spring bearing load between rocking arm and the chassis in addition, and rocking arm, this constitutes a quadrangle (Fig. 5) chassis, pull bar and wheel.More than second and third type all be independent suspension, i.e. four wheels independent action respectively.

But, more than the suspension of these prior aries, all can not make automobile inside canting when turning.Because always making chassis and the outside canting of vehicle body (Fig. 2,4 and 6) cause to take, action of centrifugal force, these suspensions feel comfortable inadequately.

For example shown in Figure 6 is the third independent suspension when turning, the outside state of canting, and the simplification mechanism of its outside canting is such: when automobile turning, acted on a centnifugal force F on center of gravity _Cf, at the then corresponding centripetal force F of balance with it that produced of left and right sides wheel with ground contact portion _F1And F _F2Because the effect of these three power has just produced a moment M on revolver ₁Act on pull bar E ₁B ₁On have one with centnifugal force power F in the same way ₃, act on rocking arm G ₁A ₁On have one with centripetal force power F in the same way ₅, this F ₃And F ₅The chassis is produced a heeling moment M _C1; In like manner, on the wheel of the right side, produced a moment M ₂Act on pull bar E ₂B ₂On have one with centnifugal force power F in the same way ₄, act on rocking arm G ₂A ₂On have one with centripetal force power F in the same way ₆, this F ₄And F ₆The chassis is produced heeling moment M _C2Like this, at F ₃, F ₄, F ₅And F ₆The effect under body produced a total heeling moment M _c, M _c=M _C1+ M _C2Thereby vehicle body is to the centnifugal force direction, and just direction tilts laterally.

In like manner as can be seen, in the prior art first kind and second class to be suspended on when turning also be bevelled (Fig. 2,4) laterally.

For many years, take uncomfortable problem, occurred many inventions and patent really for solving this outside canting, for example, USP4,589,678; USP4,484,767-A; USP4,487,429, or the like.But in order to reach the purpose of inside canting, some complicated structures, for example hydraulic pressure or electric device have all been adopted in these inventions unlimitedly.Because the complexity of structure has been brought manufacturing, used and has keeped in repair the difficulty of aspects and the raising of cost, so, have not yet to see relevant automobile vendor and adopt and place in operation.

The objective of the invention is to, adopt very better way physical construction,, when turning, make vehicle body naturally and understandably reach to the inside, feel comfortable thereby make to take unlike any suspension complexity of prior art.

Brief description of drawings:

Fig. 1, the structural plan that first kind prior art hangs;

Fig. 2, the turn condition figure that first kind prior art hangs;

Fig. 3, the structural plan that the second class prior art hangs;

Fig. 4, the turn condition figure that the second class prior art hangs;

Fig. 5, the structural plan that the 3rd class prior art hangs;

Fig. 6, the turn condition figure that the 3rd class prior art hangs;

Fig. 7, the structural plan that inventing type hangs;

Fig. 8, the turn condition figure that inventing type hangs;

Fig. 9, the special case of inventing type suspended structure;

Figure 10, the turn condition figure of suspended structure special case of the present invention;

Figure 11 A, the B embodiment of the invention 1;

Figure 12, the embodiment of the invention 2.

Consult accompanying drawing 7, suspended structure of the present invention is described.

WXYZ represents the chassis of automobile;

C ₁D ₁And C ₂D ₂Represent spring respectively;

C ₁X and C ₂Y represents spring C respectively ₁D ₁And C ₂D ₂Bearing;

I ₁J ₁And I ₂J ₂Represent left and right wheels respectively;

E ₁G ₁K ₁And E ₂G ₂K ₂The supporting mass of representing supporting wheel respectively;

A ₁D ₁G ₁And A ₂D ₂G ₂Represent left and right sides rocking arm respectively, their an end G ₁And G ₂Respectively with supporting mass E ₁G ₁K ₁And E ₂G ₂K ₂Be hinged, and other end A ₁And A ₂Then be hinged with the chassis;

B ₁E ₁And B ₂E ₂Represent left and right sides pull bar respectively, their an end E ₁And E ₂Respectively with supporting mass E ₁G ₁K ₁And E ₂G ₂K ₂Be hinged, and other end B ₁And B ₂Then be hinged with the chassis.

Supporting mass E ₁G ₁K ₁And E ₂G ₂K ₂Structure belong to prior art, if this wheel drives, then supporting mass includes constant-speed universal joint and axle drive shaft links.

Supporting mass E ₁G ₁K ₁And E ₂G ₂K ₂Be rigid body, E wherein ₁G ₁With G ₁K ₁, and E ₂G ₂With G ₂K ₂It is the one that rigidly fixes.

By seeing supporting mass E among the figure ₁G ₁K ₁And E ₂G ₂K ₂, rocking arm A ₁D ₁G ₁And A ₂D ₂G ₂, the relevant side of chassis WXYZ, and pull bar B ₁E ₁And B ₂E ₂Also can be simplified to two quadrangle: A respectively ₁B ₁E ₁G ₁And A ₂B ₂E ₂G ₂But the characteristics of suspended structure of the present invention are: left rocking arm A ₁D ₁G ₁(be simplified to straight line A ₁G ₁) be and left lever B ₁E ₁Be arranged to criss-cross; Right rocking arm A ₂D ₂G ₂(be simplified to straight line A ₂G ₂) be and right pull bar B ₂E ₂Be arranged to criss-cross.That is to say the hinge-point A on rocking arm and chassis ₁And A ₂Lay respectively at pull bar and chassis hinge-point B ₁And B ₂The top.In other words, pull bar and chassis hinge-point B ₁And B ₂Lay respectively at rocking arm and chassis hinge-point A ₁And A ₂The below.

Should be noted that pull bar B ₁E ₁And B ₂E ₂With rocking arm A ₁G ₁And A ₂G ₂Function exchange.If spring C ₁D ₁And C ₂D ₂Lower fulcrum D ₁And D ₂Act on B respectively ₁E ₁And B ₂E ₂On the bar, B then ₁E ₁And B ₂E ₂Become rocking arm, and bar A ₁G ₁And A ₂G ₂Then become pull bar.But characteristics at this moment of the present utility model remain: rocking arm intersects with pull bar.

Another point should be noted that the hinge-point G of rocking arm and supporting mass and the hinge-point E of pull bar and supporting mass can be separately positioned on two sides up and down of wheel shaft y, also can be arranged on simultaneously wheel shaft y above or below, but be good with the top that is arranged on wheel shaft y simultaneously.

Fig. 8 represents to be equipped with the vehicle that the present invention hangs, centnifugal force F when turning _CfEffect under, the inwardly state and the stressing conditions of canting.

Can see by Fig. 8, when automobile turning, on center of gravity O, act on a centnifugal force F _Cf, on the wheel of the left and right sides equally also at its corresponding generation centripetal force F of balance with it with ground contact portion _F1And F _F2Under the effect of these three power, moment M of same generation on revolver ₁, moment M of same generation on the wheel of the right side ₂, simultaneously, act on left lever B ₁E ₁On also have one with centnifugal force power F in the same way ₃, act on left rocking arm A ₁G ₁On also have one with centripetal force power F in the same way ₅But, at this moment owing to architectural feature of the present invention be, pull bar BE and chassis hinge-point B, be positioned at the below of the hinge-point A on rocking arm AG and chassis, that is to say with prior art in this upper-lower position of 2 just in time intercourse, in other words, pull bar of the present utility model and rocking arm are arranged to criss-cross, so F ₃And F ₅To the heeling moment M that the chassis produced _C1Just in time with of the prior art opposite.In like manner, act on right pull bar B ₂E ₂On also have one with centnifugal force power F in the same way ₄; Act on right rocking arm A ₂G ₂On also have one with centripetal force power F in the same way ₆These two power F ₄And F ₆Heeling moment M to the chassis generation _C2Also just in time with of the prior art opposite.Like this, at F ₃, F ₄, F ₅And F ₆Effect under, the chassis is connected vehicle body has just produced a total heeling moment M _c=M _C1+ M _C2, its direction is just opposite with prior art, thereby makes vehicle body (connect chassis) towards the direction opposite with centnifugal force, also promptly naturally and understandably produces canting towards the direction one of centripetal force towards interior side direction.

Under special circumstances, if the A point overlaps with the B point, just then hang the special case that becomes shown in Fig. 9 (9-1).Be easy to find out that at this moment supporting mass, rocking arm and pull bar three have formed English truss, it is a rigidity, and in fact, because the rigid construction of English truss, they just can further be reduced to firm bar A ₁D ₁G ₁And A ₂D ₂G ₂(Fig. 9-2).Two combine into one to that is to say pull bar and rocking arm.

Figure 10 has represented special case shown in Figure 9 state and stressing conditions when turning.Can draw through calculating, work as A ₁J ₁The same A of extended line ₂J ₂The joining O of extended line above center of gravity O the time, the heeling moment M that is produced _cMake the inside canting of automobile; Otherwise, when O is below center of gravity O, M _cMake the outside canting of auto body.By analysis, suspension of the prior art three types, the overwhelming majority belongs to this situation in back, so its heeling moment always makes the outside canting of vehicle body.

About suspension gear of the present invention, the derivation of equation and numerical calculation that it produces the mechanical analysis of introversion side naturally please see the annex of this specification sheets for details, do not repeat them here.

Suspension of the present invention, except making vehicle when turning the inside canting, on bevelled ground, vehicle body is kept near horizontal state, because, on the bevelled road surface, gravitational vector can be decomposed into two vectors, one-component is perpendicular to the bevelled road surface, and another component then is parallel to the bevelled road surface, the centnifugal force that produces when this latter just is equivalent to turn.So because the top mechanical mechanism of having analyzed, suspension of the present invention will produce a heeling moment, make vehicle body towards the opposite direction canting of centnifugal force, just make vehicle body towards the canting of bevelled reversing sense, thereby make the position of vehicle body maintenance near level.

The advantage that the present invention hangs just is that structure is very simple, unlike any prior art complexity; When turning, can make vehicle body inwardly canting naturally; Can also be on the bevelled road surface, vehicle body is kept near horizontal state, thereby take the sensation nature and comfortable.In addition, the special case of the utility model suspension is implemented even can reequip easily on the existing automobile of major part.

In a word, the inventor that the present invention hangs is by creationary intellectual work, found the structural arrangement that general rule of the present invention hangs, i.e. rocking arm and pull bar arranged crosswise, and the notion of the supporting-point O ' of special case of the present invention suspension, thereby found, if hinge-point A arranges than higher (h ₁Bigger, for this example, h ₁=450) suspension that makes this pattern also can produce very big positive heeling moment as the special case that the present invention hangs, and also, makes the moment of the inside canting of vehicle body.And this improvement is incomparably simple, but can produce significant effect.Therefore, hanging device of the present invention is creative.

According to the design that the invention described above hangs, can enumerate two following embodiment, the concrete enforcement structure of suspension gear of the present invention further is illustrated.

Embodiment 1

As shown in figure 11, y-wheel axis wherein: z-steering shaft axis, wheel 9 can reach the purpose that turns to around the revolution of z axle; The 1-support; The 2-pull bar; The 3-upper bracket of the spring; 4-garden pin; The 5-supporting mass; The last king pin of 6-; 7-universal coupling housing; The 8-bolster; The 9-wheel; King pin under the 10-; 11-garden pin; The 12-spring lower support; The 13-rocking arm; The 14-coil spring; The 15-axle drive shaft; 16-garden pin; 17-chassis (not being with suspension); 18-garden pin; The 19-bearing; The 20-joint bolt; The 21-axle drive shaft.

Pin-and-hole E and G are arranged on the supporting mass 5.It does rotating the connection by the garden pin 4 and 11 that is inserted among pin-and-hole E and the G with pull bar 2 and rocking arm 13.

By garden pin 16, the other end B of pull bar 2 does rotating the connection with support 1.

By garden pin 18, the other end A of rocking arm does rotating the connection with bearing 19.

Support 1 and bearing 19 all pass through joint bolt (for example 20) and chassis 17 Joints.

One spring bearing 3 and 12 are respectively arranged on the end of support 1 and the rocking arm 13.Between these two bearings 3 and 12, a coil spring 14 is housed.

Since with the break-in line of centers of the joining constant-speed universal joint of change speed gear box not with swivel pin 18 conllinear of rocking arm 13 on bearing 19, therefore when hanging action, the inevitable variation to some extent of the length of axle drive shaft 15.For this reason, axle drive shaft 15 must be made Collapsible structure slip or that have the rolling original paper.

Respectively there is a constant speed universal coupling (not shown) at the two ends of axle drive shaft 15.The constant-speed universal joint of one end and the change speed gear box shaft in the chassis link, and the universal coupling of the other end then is contained in the constant-speed universal joint housing 7, and link with axle drive shaft 21.

Bolster 8 and constant-speed universal joint housing 7 Joints, 9 of wheels are contained on the bolster 8 by antifriction-bearing box.

21 of axle drive shafts pass hollow bolster 8, and link with wheel 9 at its end, rotate with drive wheels.

Last king pin 6 and following king pin 10 also are to be fixed on the housing 7 of constant-speed universal joint.

Like this, supporting mass is by its pin-and-hole supporting king pin 6 and 10, thereby wheel 9 can turn round with respect to supporting mass 5 around the axis z of king pin 6 and 10.This revolution is that the action by the steering hardware that is contained in down king pin 10 ends realizes, thereby makes wheel steering, and whole vehicle is turned.

Embodiment 2

Figure 12 shows the specific embodiment of suspension gear extraordinary circumstances of the present invention (the A point overlaps with the B point).All all identical among the part title in addition of labels and the embodiment 1 among the figure.The yet detailed preamble of its effect and operating principle does not repeat them here.As can be seen from Figure, present embodiment has saved pull bar 2, and rocking arm 13 is then made one with supporting mass 5, need not be hinged with garden pin 11.The key that this special case is implemented has been shown in Fig. 9-2, and promptly O must be above center of gravity O.

It should be understood that; the present invention here show and the form described just as the more superior example of the present invention; each parts can be taked in the various changes aspect shape, size and the arrangement and not depart from design essence of the present invention and the protection domain that appended claims proposed.

Inner shelving vehicle wheel hanging

Annex

In this annex, adopt the method for mechanical analysis to come detailed proof suspension of the present invention, can make the automobile inwardly canting naturally and understandably when turning that has this suspension, in analysis, adopt 11 accompanying drawings:

Figure 13 regards to the antagonistic force F of left and right wheels with asking during the vehicle straight _R1And F _R2

Figure 14, Ackermann steer angle regard to the antagonistic force F of left and right wheels with asking _R1And F _R2

Figure 15 asks spring load F in the special case ₁And F ₂(vehicle straight)

Figure 16 asks the heeling moment on chassis when vehicle begins to turn in the special case

Figure 17 asks spring load F in the general rule ₁And F ₂(vehicle straight)

Figure 18 asks the heeling moment on chassis when vehicle begins to turn in the general rule

Figure 19, the code name that each relevant size is adopted during analysis

Figure 20, the enforcement size of the prior art of second type

Figure 21, the enforcement size that general rule of the present invention hangs

Figure 22, the enforcement size that special case of the present invention hangs

Figure 23, the enforcement size of the prior art of the 3rd type

Wheel antagonistic force F when asking the vehicle straight earlier _R1And F _R2, (Figure 13)

F _r1＝F _r2＝ (W)/2 （1）

Ask Ackermann steer angle wheel antagonistic force F again _R1And F _R2And friction force Ff ₁And Ff ₂(Figure 14) (according to the mechanics general rule, the symbol negate clockwise of moment is for just, and clockwise direction is for negative).

∑M _J1＝0

F _r2·1 ₄- W· (1 ₄)/2 - F _cf·h = 0 (2)

Separate F _R2

F _r2= (w1 ₄+ 2F _cf·h)/(21 ₄) (3)

∑ Y=0 is arranged again

F _r1+F _r2-W＝0

F _r1＝W-F _r2（4）

From (3)

F _r1= w - (w1 ₄+ 2F _cf·h)/(21 ₄)

= (w1 ₄- 2F _cf·h)/(21 ₄) （5）

∑ X=0 is arranged again

F _f1+F _f2-F _cf＝0 （6）

And friction force is directly proportional with antagonistic force

(F _f1)/(F _r1) = (F _f2)/(F _r2) （7）

F _f1= F _f2· (F _r1)/(F _r2) （8）

Substitution (6)

F _f2· (F _r1)/(F _r2) + F _f2- F _cf= 0 （9）

Separate Ff ₂

F _f2= F _cf· (F _r2)/(F _r1+ F _r2) （10）

From (3), (5), (10)

F _f2= F _cf· (w1 ₄+ 2F _cf·h)/(2w1 ₄) （11）

In generation, gone back to (6)

F _f1= F _cf· (w1 ₄+ 2F _cf·h)/(2w1 ₄) - F _cf= 0 （12）

Separate F _F1

F _f1= F _cf· (w1 ₄- 2F _cf·h)/(2w1 ₄) （13）

During above straight and the ground when turning regards to the antagonistic force F of wheel _R1And F _R2Value, and the frictional ground force Ff when turning ₁And Ff ₂Value all is the same.

Carry out the mechanical analysis that special case of the present invention hangs now

At first determine spring C ₁D ₁With C ₂D ₂Stressed F when the vehicle straight ₁, F ₂

Contrast Figure 15-3 and Figure 19

a ₂= (1 ₂- 13)/2 （14）

b ₂= (1 ₄- 1 ₃)/2 （15）

Again from Figure 15-3

∑M _A2＝0

F _r2.b ₂-F ₂.a ₂（16）

Separate F ₂,

F ₂= F _r2· (b ₂)/(a ₂) （17）

From (1), (14), (15)

Because left-right symmetric during the vehicle straight, so

F ₁= F ₂= (W(1 ₄- 1 ₃))/(2(1 ₂- 1 ₃)) （19）

The situation of (turn, but vehicle body not canting as yet) is investigated a left side earlier and is hung (Figure 16-2) when investigating vehicle again and beginning to turn.Be noted that vehicle body not canting as yet at this moment, spring length does not change as yet, therefore, and spring stress F ₁, F ₂Remain size shown in the formula (19).

∑X＝0

F ₅-F _f1＝0 （20）

F ₅= F _f1= F _cf· (w1 ₄- 2F _cf·h)/(2w1 ₄) （21）

∑Y＝0

F ₉+F _r1-F ₁＝0 （22）

From (5), (19)

F ₉= (W1 ₄(1 ₄- 1 ₂) + 2F _cf·h(1 ₂- 1 ₃))/(21 ₄(1 ₂- 1 ₃)) （23）

In like manner, hang (Figure 16-3) for the right side

∑X＝0

F ₆-F _f2＝0 （24）

F ₆= F _f2= F _cf· (w1 ₄+ 2F _cf·h)/(2w1 ₄) （25）

∑Y＝0 F ₁₀+F _r2-F ₂＝0 （26）

From (3), (19)

F ₁₀= (W1 ₄(1 ₄- 1 ₂) - 2F _cf·h(1 ₂- 1 ₃))/(21 ₄(1 ₂- 1 ₃)) （27）

Investigate chassis (Figure 16-1)

Contrast Figure 16 and Figure 19

e ₁= e ₂= (1 ₂)/2 （28）

f ₁= f ₂= (1 ₃)/2 （29）

g＝h-h ₁（30）

Ask power F ₁, F ₂, F ₅, F ₆, F ₉With the square M of F for center of gravity O _o

∑M ₀＝F ₂.e ₂-F ₁.e ₁-（F ₅+F ₆）.g+F ₉.f ₁-F ₁₀.f ₂（31）

∑M ₀＝F _cf·( (h·1 ₃)/(1 ₄) - (h - h ₁)) （32）

= F _cf·(h ₁- h· (1 ₄- 1 ₃)/(1 ₄) ) （33）

Introduce a notion (Figure 22), i.e. wheel I now ₁J ₁And I ₂J ₂Earth point J ₁, J ₂With rocking arm K ₁A ₁And K ₂A ₂Fulcrum A on the chassis ₁, A ₂Line J ₁A ₁And J ₂A ₂The intersection point O ' of extended line, and be referred to as supporting-point.Supporting-point O ' height overhead is h ', next determines the value of h '.

From Figure 19, Figure 22

Or h '=h ₁(1 ₄)/(1 _4-1 ₃) (35)

(34) substitution (33),

ΣM _O=F _cf·(h ^′· (1 ₄-1 ₃)/(1 ₄) -h· (1 ₄-1 ₃)/(1 ₄) )

=F _cf· (1 ₄-1 ₃)/(1 ₄) ·(h′-h) （36）

From (33) as can be seen, if the height h of center of gravity O remains unchanged, the hinge-point A of rocking arm on the chassis ₁, A ₂Height h ₁Big more, hang heeling moment ∑ M for the chassis ₀Big more, and if

h ₁＞h· (1 ₄-1 ₃)/(1 ₄) （37）

, ∑ M then _OFor on the occasion of, even the inside canting of vehicle.

Otherwise, if h ₁More little, then hang heeling moment ∑ M for the chassis _OAlso more little, and if

h ₁＜h· (1 ₄-1 ₃)/(1 ₄) （38）

, ∑ M then _OBe negative value, even the outside canting of vehicle.

Under special circumstances, the heeling moment that hangs for the chassis is zero, at this moment, and from (36)

h′-h＝0 （39）

That is

h′＝h （40）

Be that center of gravity O and supporting-point O ' are contour

If

h′＞h （41）

Then supporting-point O ' is higher than center of gravity O,

h′-h＞0 （42）

Heeling moment is being for just at that time, the inside canting of vehicle

If

h′＜h （43）

Then supporting-point O ' is lower than center of gravity O

h′-h＜0 （44）

Heeling moment is for bearing the outside canting of vehicle at that time.

It more than is the mechanical analysis of hanging for special case of the present invention

Below carry out mechanical analysis for general run of thins suspension of the present invention.

Spring stress F when at first, determining the vehicle straight ₁, F ₂,

From Figure 17-3, investigate wheel I ₂J ₂

∑X＝0

F ₄.Cosβ＝0，F ₄＝0 （45）

∑Y＝0

F _r2-F ₈-F ₄.Sinβ＝0 （46）

From (1), (46)

F ₈＝ (W)/2 （47）

Investigate rocking arm A ₂D ₂G ₂

∑M _A2＝0

F ₈.b ₂-F ₂.a ₂＝0 （48）

From (47), (15), (14)

(w)/2 · (1 ₄-1 ₃)/2 -F ₂· (1 ₂-1 ₃)/2 =0

F ₂= (W)/2 · (1 ₄-1 ₃)/(1 ₂-1 ₃) （49）

Since the vehicle straight, left-right symmetric, so

F ₁=F ₂= (W(1 ₄-1 ₃))/(2(1 ₂-1 ₃)) （50）

The length of (vehicle body is not canting as yet) spring changes as yet when investigating vehicle again and beginning to turn, so spring stress is still constant, promptly remains

F ₁=F ₂= (W(1 ₄-1 ₃))/(2(1 _2-1 ₃)) （51）

From Figure 18-2, investigate left wheel

∑M _G1＝0

F ₃.Cosα.（h ₄-h ₃）+F ₃.Sinα.d ₁-F _f1.h ₃＝0 （52）

Separate F ₃, from (13)

F ₃= (F _Cfh ₃(w1 ₄-2F _cf·h))/(2w1 ₄（(h ₄-h ₃)cosα+d ₁sinα)) （53）

From (13), (53)

∑X＝0

F ₅-F ₃Cos-F _f1＝0

F ₅= (F _cf(w1 ₄-2F _cf·h)(h ₄cosα+d ₁sinα))/(2w1 ₄(h ₄-h ₃)cosα+d ₁sinα)) （54）

From (5), (53)

∑Y＝0，F _r1+F ₃Sinα-F ₇＝0

F7= (W1 ₄-2F _cf·h)/(21 ₄) (1

+ (F _cfh ₃sinα)/(W((h ₄-h ₃)cosα+d ₁sinα)) ) （55）

Investigate left rocking arm G ₁D ₁A ₁(Figure 18-2)

∑Y＝0

F ₇+F ₉-F ₁＝0 （56）

From (55), (51)

F ₉= (W(1 ₄-1 ₃₎)/(2(1 ₂-1 ₃)) - (W1 ₄-2F _cf·h)/(21 ₄) （1

+ (F _cfh ₃sinα)/(w((h ₄-h ₃)cosα+d ₁sinα)) ） （57）

In like manner, hang for the right side, from Figure 18-3

∑M _G2＝0

F ₄Cosβ.（h ₄-h ₃）+F ₄Sinβ.d ₂-F _f2.h ₃＝0

From (11) (58)

F4= (F _cfh ₃(w1 ₄+2F _cfh))/(2w1 ₄((h ₄-h ₃)cosβ+d ₂sinβ)) ) （59）

∑X＝0

F ₆-F ₄Cosβ-F _f2＝0 （60）

From (11), (59)

F ₆= (F _cf(w1 ₄+2F _cfh)(h ₄cosβ+d ₂sinβ))/(2w1 ₄((h ₄-h ₃)cosβ+d ₂sinβ)) （61）

∑Y＝0

F _r2-F ₈-F ₄Sinβ＝0 （62）

From (3), (59)

F ₈= (W1 ₄+2F _cfh)/(21 ₄) (1-

(F _cfh ₃sinβ)/(w((h ₄-h ₃)cosβ+d ₂sinβ)) )（63）

For right rocking arm A ₂D ₂G ₂

∑Y＝0

F ₈+F ₁₀-F ₂＝0 （64）

From (51), (63)

F ₁₀= (W(1 ₄-1 ₃))/(2(1 ₂-1 ₃)) - (W1 ₄+2F _cfh)/(21 ₄) (1-

(F _cfh ₃sinβ)/(w((h ₄-h ₃)cosβ+d ₂sinβ)) ） （65）

From Figure 18-1, hang about can obtaining and act on all power F for the chassis ₁, F ₂, F ₃, F ₄, F ₅, F ₆, F ₉And F ₁₀The heeling moment M that is produced _O

∑M _O＝F ₂.e ₂-F ₁.e ₁+F ₃Cosα.i+F ₄Cosβ.i+F ₃Sinα.f ₁+F ₄Sinβ.f ₂-（F ₅+F ₆）.g+F ₉.f ₁-F ₁₀.f ₂（66）

Contrast Figure 18 and Figure 19 have

e ₁=e ₂= (1 ₃)/2 （67）

f ₁=f ₂= (1 ₃)/2 （68）

g＝h-h ₁（69）

i＝h-h ₂（70）

d ₁=d ₂= (1 ₄-1 ₁)/2 （71）

From (50), (53), (59), (54), (61), (57), (65), (67), (68), (69), (70), (71), (72)

Because of (66) more complicated, its segmentation is simplified

F ₃coaα·1+F ₄cosβ·1

=F ₃icosα+F ₄icosα= (F ₃+F ₄)icosα

= (F _cfh ₃icosα)/((h ₄-h ₃)cosα+d ₁sinα) (74)

F ₃sinα·f ₁+F ₄sinβ·f ₂

=F ₃f ₁sinα+F ₄f ₁sinα= (F ₃+F ₄)f ₁sinα

= (F _cfh ₃f ₁sinα)/((h ₄-h ₃)cosα+d ₁sinα) （75）

From (74), (75) F ₃Coa α 1+F ₄Cos β 1+F ₃Sin α f ₁+ F ₄Sin β f ₂

= (F _cfh ₃(icosα+f ₁sinα))/((h4-h ₃)cosα+d ₁sinα) （76）

(F ₅+F ₆)·g

= (F _cfg(h ₄cosα+d ₁sinα))/((h ₄-h ₃)cosα+d ₁sinα) （77）

F ₉f ₁-F ₁₀f ₂

=F ₉f ₁-F ₁₀f ₁=(F ₉-F ₁₀)· f ₁

= (2F _cfh·f ₁)/(1 ₄) - (F _cfgh ₃f ₁sinα))/((h ₄-h ₃)cosα+d ₁sinα) （78）

(73), (76), (77), in (78) generation, gone back to (66), is reduced to

+ 1/((h ₄-h ₃)(1 ₁-1 ₃)+(1 ₄-1 ₁)(h ₄-h ₂)) ·

·(h ₃(h-h ₂)(1 ₁-1 ₃)

-(h-h ₁)(h ₄(1 ₁-1 ₃)

+(1 ₄-1 ₁)(h ₄-h ₂))) （79）

More than be the mechanics General Analytical formula of the heeling moment that hangs of the present invention, hang, also can use above expression formula for the prior art of the third type, contrast Figure 19 and Figure 23, order:

l ₁＝l ₄（80）

h ₂＝h ₄（81）

h ₁＝h ₃（82）

(80), (81), (82) substitution (79), then (79) become

（83）

Below only coefficient is learned expression formula, and the notion of no numerical value (amount) in order to say something eloquently, is implemented more given numerical value at this to each contrast, and they are;

The present invention is generally hung Figure 21 formula (79)

Special case of the present invention is hung Figure 22 formula (33)

The second type prior art is hung Figure 20 formula (33)

The 3rd type prior art is hung Figure 23 formula (83)

In this analysis, get W=2000, F _Cf=500, the high h=550 of center of gravity

The present invention is generally hung contrast Figure 21, Figure 19, formula (79)

F _cf＝500 （84）

h＝550 （85）

L ₁＝1354 （86）

L ₃＝818 （87）

L ₄＝1524 （88）

h ₁＝450 （89）

h ₂＝409 （90）

h ₃＝450 （91）

h ₄＝574 （92）

Special case of the present invention is hung contrast Figure 22, Figure 19, formula (33)

F _cf＝500 （93）

h＝550 （94）

h ₁＝450 （95）

L ₄＝1524 （96）

L ₃＝818 （97）

The second type prior art is hung contrast Figure 20, Figure 19, formula (33)

F _cf＝500 （98）

h＝550 （99）

h ₁＝250 （100）

L ₄＝1524 （101）

L ₃＝818 （102）

The 3rd type prior art is hung contrast Figure 23, Figure 19, formula (83)

F _cf＝500 （103）

h＝550 （104）

L ₃＝818 （105）

L ₄＝1524 （106）

Each relevant formula of above each data substitution is got

The present invention is generally hung

Substitution formula (79)

∑ M _O=+150000 inside cantings (107)

Special case of the present invention is hung

∑M _O=F _cf(h ₁-h· (1 ₄-1 ₃)/(1 ₄) )

=+97500 inside cantings are hung (108) to the second type prior art

∑M _O=F _cf(h ₁-h· (1 ₄-1 ₃)/(1 ₄) )

=-2500 outside cantings are hung (109) to the 3rd type prior art

∑M _O=F _cf·h· (1 ₃-1 ₄)/(1 ₄)

=-127300 outside cantings (110)

Contrast

The present invention generally hangs

Inwardly canting of heeling moment=+ 150000

Special case of the present invention hangs

Inwardly canting of heeling moment=+ 97500

The second type prior art hangs

Outwards canting of heeling moment=-2500

The 3rd type prior art hangs

Outwards canting of heeling moment=-127300

Below 6 should be noted

1. even prior art hangs and adopts higher articulated point of rocker arm A, make h '＞h, heeling moment still will be very little, be not enough to produce significant canting, because from (37), even

h ₁＞h· (1 ₄-1 ₃)/(1 ₄)

Thereby, make the inside canting of vehicle, but this only is qualitative leap, rather than quantum leap, the heeling moment that also needs the enough sizes of foot affair just can make vehicle produce significant canting.Hanging for special case of the present invention, heeling moment is+the 97500(general rule is 150000, also wants big) need overcome spring C with it ₁D ₁And C ₂D ₂Drag, for spring C ₁D ₁And C ₂D ₂It is a pair of couple.Known two springs open shelves are L ₂=1218, so this couple is 80, again from formula (51), spring is fully loaded stressedly to be

F ₁=F ₂= (W(1 ₄-1 ₃))/(2(1 ₂-1 ₃))

= (2000(1524-818))/(2(1218-818))

=1765 (W=2000)

Couple 80 is compared with spring fully loaded stressed 1765, accounts for 0.045 this increment load of 4 percent five, produces 4 percent five additional deformation can make spring, makes the significant canting of vehicle body.Prior art hangs again, and the hinge-point A of the rocking arm of prior art suspension is lower usually, i.e. h ₁Smaller, the general mid point that does not exceed wheel, if the wheel diameter of picking up the car is 600, promptly radius is 300, promptly as getting h ₁Be 300, then heeling moment will for

∑M _O=F _cf(h ₁-h· (1 ₄-1 ₃)/(1 ₄) )

=500(300-550· (1524-818)/1524 )

=+22500

Its positive really heeling moment, if but moment 22500 effect of being converted on the spring couple then only be

22500/1218 ＝18

Take this couple 18 to compare with spring fully loaded stressed 1765,

Only be

18/1765 ＝0.01

Only account for 1%, this faint couple is not enough to vehicle body and produces the canting that can aware.Thus, this prior art only can make not outwards canting of vehicle body at most.

2. the structure of the structure of the present invention's suspension and the suspension of the second type prior art is very different, and its difference is that the hinge-point A that the second type prior art hangs rocking arm disposes very lowly, i.e. h ₁Very little (h in this example ₁=250) and the utility model special case hangs the hinge-point A of rocking arm and disposes very highly, i.e. h ₁Very big (h in this example ₁=450) this is not only the difference on the size, and is difference in essence, the height h of the hinge that the second type prior art hangs ₁Little, therefore only can make the outside canting of vehicle body (even h ₁Big to producing positive heeling moment, but the amount of this positive heeling moment also is very little, only 22500) and the suspension of the utility model special case owing to articulated point of rocker arm height (h ₁=450), it produces a very big positive heeling moment to vehicle body, and (+97500) make vehicle body produce inside canting, and the heeling moment that this is big and the heeling moment of prior art relatively are the latter

97500/22500 ＝4.3

In other words, special case of the present invention hangs, and the canting effect for vehicle body hangs much bigger than prior art.

For a long time, the second type prior art adopts very little h always ₁Value makes the inside canting problem of vehicle body, fails to solve always.The inventor that the present invention hangs by intellectual work, has found the structural arrangement that general rule of the present invention hangs, the notion of the supporting-point O ' that (rocking arm and pull bar arranged crosswise) and invention special case hang.If thereby found that hinge-point A arranges than higher (h ₁Bigger, for this example, h ₁=450), then the suspension of this pattern also can produce very big positive heeling moment as the special case that the present invention hangs, and makes the inside canting of vehicle body.And this change is incomparable simple, but can produce very obvious improvement.Therefore we say that the present invention has invention.

3. in the derivation in front, once used such description for twice, promptly " turn inside diameter; but vehicle body not canting as yet ", this saying, may not allow easily accepted by peoplely, since promptly " turning " how " not canting as yet ", we can adopt another formulation, promptly " when the vehicle straight; if on the center of gravity of vehicle, apply level power (for example centnifugal force) to the right, in this case; vehicle body will be to that direction canting, and heeling moment is much.

4. in this annex, do not mention the analysis of first type suspension.This be because, first type suspension is that a kind of very oldfashioned hangs, the characteristic of its outside canting is too obvious, never controversial, therefore, just needn't take pen and ink more.

5. this mechanical analysis is not conventional analysis, because analytic target is not to be in completely in the state of equilibrium, it is in the horizontal direction with the balance really of vertical direction, i.e. neither along continuous straight runs motion vertically motion again, therefore can use ∑ X=0, ∑ Y=0.But along hand of rotation, it is unbalanced, therefore can not use ∑ M=0.The M of this ∑ just that will look for here.

6. in formula (79), if directly make h ₁=h ₂, also can obtain formula (33).

Claims (3)

1, a kind of automobile wheel suspensioning device, comprise wheel support body (5), hinged and the rocking arm (13) of the other end and above-mentioned supporting mass (5) hinged (11) in one end and chassis (17), the pull bar (2) of one end and chassis (17) hinged and the other end and above-mentioned supporting mass (5) hinged (4) and have the spring (14) of bearing, it is characterized in that described rocking arm (13) is configured to criss-cross with described pull bar (2).

2, by the described wheel suspension assembly of claim 1, it is further characterized in that, the hinge-point (11) of described rocking arm (13) and supporting mass (5), with the hinge-point (4) of described pull bar (2) with supporting mass (5), can be separately positioned on two sides up and down of wheel axis y, also can be arranged on simultaneously wheel axis y above or below, be good with its top that is arranged on wheel axis y simultaneously.

3, a kind of automobile wheel suspensioning device, comprise wheel support body (5), the rocking arm (13) that one end and chassis (17) hinged (18) and the other end and above-mentioned supporting mass (5) are affixed and have the spring (14) of bearing, it is characterized in that, the hinge-point (18) on described right rocking arm (13) and chassis (17), i.e. (A ₂), with garden and ground contact point (J in the middle of the right wheel ₂) line (J ₂A ₂) extended line and the hinge-point (A on left rocking arm and chassis ₁) with garden in the middle of the left wheel and ground contact point (J ₁) line (J ₁A ₁) the joining O ' of extended line is positioned on the car load design gravity point O.

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