CN202080083U - Vehicular suspension device - Google Patents
Vehicular suspension device Download PDFInfo
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- CN202080083U CN202080083U CN2011200509047U CN201120050904U CN202080083U CN 202080083 U CN202080083 U CN 202080083U CN 2011200509047 U CN2011200509047 U CN 2011200509047U CN 201120050904 U CN201120050904 U CN 201120050904U CN 202080083 U CN202080083 U CN 202080083U
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Abstract
The utility model provides a vehicular suspension device, which aims at further reducing the shaking of a steering wheel when the input from a road to wheels changes. The vehicular suspension device is structurally characterized in that the inward-inclination offset delta k of a steering knuckle pin, the dip angle theta k of the steering knuckle pin, the backward-inclination offset delta c of the knuckle pin, and the rear inclination angle theta c of the knuckle pin meet the relation that delta c multiplied tan(theta k) plus delta k multiplied tan (theta c) is no more than alpha (which is of a value close to 0 set corresponding to a suspension structure).
Description
Technical field
The utility model relates to a kind of suspension device for rolling stock that car body is hung.
Background technology
In suspension device for rolling stock, improve in hope under the situation of straight ahead of vehicle, chaufeur to follow the trail of the objective fare intention and and its cooresponding handling maneuver response and vehicle movement between relation, become important key element.
Specifically, importantly have following 2 points simultaneously, that is, with respect to the steering operation of chaufeur and vehicle reacts delicately, and bearing circle does not rock with respect to disturb input outward from ground-surface.
The characteristic of this draft hitch, be related to from the cooresponding moment variations around the steering yoke bolt axle of the input of wheel side.
In patent documentation 1, disclose the connecting rod structure of following stabiliser, that is, can utilize stabiliser that the direction that moment acted on of steering direction is changed.
By this structure, in the technology of patent documentation 1 record, when turning beginning (when handling maneuver begins), the moment of the increase side that rotates with respect to suspension improves the handling maneuver sensation.In addition, when turning is stablized (when keeping motionless), the moment of the minimizing side that rotates with respect to suspension becomes understeering tendency of car, makes vehicle stabilization.
Patent documentation 1: TOHKEMY 2006-082790 communique
The utility model content
But, in the technology that patent documentation 1 is put down in writing, when turning to, make wheel to the toeing-in directional steering, realize the raising of vehicle run stability.
Therefore, because pavement roughness etc. and under the situation about changing,, bearing circle is produced rock around the moment variations of steering yoke bolt axle from the input of wheel side.
As noted above, in the prior art, from the road surface when the input of wheel changes, be difficult to reduce fully rocking of bearing circle.
Problem of the present utility model is, from the road surface when the input of wheel changes, further reduce rocking of bearing circle.
In order to solve above-mentioned problem, the related suspension device for rolling stock of the utility model constitutes, and steering yoke bolt introversion offset delta k, pivot stud angle θ k, wheel caster offset delta c, kingpin caster angle θ c satisfy the relation of following formula.
δ ctan (θ k)+δ ktan (θ c)≤α (wherein, α for suspension structure set accordingly 0 near value)
The effect of utility model
According to the utility model and since from the road surface when the input of wheel changes, can suppress the moment around the steering yoke bolt axle, so can further reduce rocking of bearing circle.
Description of drawings
Fig. 1 is the summary construction diagram with automobile 1A of the related draft hitch of the 1st embodiment 1.
Fig. 2 is the figure of the structure example of expression draft hitch 1.
Fig. 3 is the figure that explanation is used to define the parameter of steering yoke bolt axle.
Fig. 4 is the distortion angle β of tyre contact patch of the expression wheel that is in turn condition and the figure that transverse force Fy reaches back the relation between the positive moment of torsion Mz.
Fig. 5 is the transverse force Fy of expression wheel and returns the figure of positive moment of torsion Mz in the situation of wheel center generation.
Fig. 6 is the transverse force Fy and time positive moment of torsion Mz of expression wheel center position and the figure that centers on the relation between the moment Mk of steering yoke bolt axle.
Fig. 7 is the above-below direction load of expression wheel and the figure that centers on the relation between the moment of steering yoke bolt axle.
Fig. 8 is the figure of the example of the suspension arm in the expression draft hitch 1.
Fig. 9 is expression wheel caster offset delta c and the figure that centers on the relation between the moment variations amount of steering yoke bolt axle.
Figure 10 is expression steering yoke bolt introversion offset delta k and the figure that centers on the relation between the moment variations amount of steering yoke bolt axle.
Figure 11 is the figure of the deflection angle of expression wheel and the relation between flare changes over the ground.
Figure 12 is the figure of the concrete structure example of expression draft hitch 1.
Figure 13 is the figure of an example that expression is provided with the state of suspension arm.
Figure 14 is the figure that expression suspension structure shown in Figure 13 is positioned at the state of the wheel side of turning.
Figure 15 is the figure of other examples that expression is provided with the state of suspension arm.
Figure 16 is the figure that expression suspension structure shown in Figure 15 is positioned at the state of the wheel side of turning.
Figure 17 is expression with the right of formula (2) as x axle, the figure of straight line of equation representative with the left side during as the y axle.
Figure 18 be expression to utilize the installation site on steering swivel 14 be the suspension arm of 1 point, steering yoke bolt introversion offset delta k is the figure of zero state.
Figure 19 be expression to utilize the installation site on steering swivel 14 be the suspension arm of 2 points, steering yoke bolt introversion offset delta k is the figure of zero state.
Figure 20 is the figure of other structure example of the related draft hitch 1 of expression the 1st embodiment.
Figure 21 is the figure of other structure example of the related draft hitch 1 of expression the 1st embodiment.
Figure 22 is the figure of expression distortion angle and the relation between the power of wheel effect.
The specific embodiment
Below, with reference to accompanying drawing, the embodiment of having used automobile of the present utility model is described.
(the 1st embodiment)
(integral structure)
Fig. 1 is the summary construction diagram with automobile 1A of the related draft hitch 1 of the 1st embodiment of the present utility model.
In addition, Fig. 2 is the figure of the structure example of expression draft hitch 1, and Fig. 2 (a) is the concrete structure example of front suspension, and Fig. 2 (b) is arranged on the scheme drawing of the state on the automobile 1A.In Fig. 1 and Fig. 2, automobile 1A has: draft hitch 1; Steering hardware 2; And wheel 3FL, 3FR, 3RL, 3RR.
Car body installing component 11 is parts that suspension arm 12,13 is installed on the car body, can support suspension arm 12,13 to the car body above-below direction with freely swinging.
Suspension arm the 12, the 13rd, for example the suspension arm of A font utilizes car body installing component 11 and car body to link.In addition, in the present embodiment, suspension arm 12 is a upper arm, and suspension arm 13 is a underarm.
The two ends of steering swivel 14 can be supported by suspension arm 12,13 with rotating freely.With the line that the strong point up and down of steering swivel 14 links, constituting imaginary S. A. is the steering yoke bolt axle.In addition, steering swivel 14 has wheel hub 16, and it can keep wheel with rotating freely.In addition, steering swivel 14 has spindle arm, and it transmits the handling maneuver input from steering hardware 2 via not shown intermediate rod.And steering swivel 14 is accepted handling maneuver input from steering hardware 2 by making spindle arm, thereby is that swing at the center with the strong point of suspension arm 12,13.
Shock absorber 15 is shock attenuation units such as oil snubber, and the upper end is fixed on the car body, and the lower end is fixed on the underarm.In addition, draft hitch 1 has spring (not shown) side by side with shock absorber 15.
Wheel hub 16 is arranged on the holding member of the wheel on the steering swivel 14, is that the center can keep wheel with rotating freely with the S. A..
Bearing circle 21 and Steering gear 22 link, and it is to center on rotatablely moving of the axle of Steering gear 22 that the handling maneuver of chaufeur is operated transmission.
(around the structure of steering yoke bolt axle)
(condition of wheel caster side-play amount)
Fig. 3 is the figure that explanation is used to define the parameter of steering yoke bolt axle, and Fig. 3 (a) is the figure (lateral plan) that observes wheel from the vehicle side, and Fig. 3 (b) is the figure (front elevation) that observes wheel from vehicle front.
In Fig. 3, the steering yoke bolt axle of wheel is determined by following parameter, that is: the leaning angle of the steering yoke bolt axle of in lateral plan, observing (hereinafter referred to as " kingpin caster angle ") θ c, fore-and-aft direction side-play amount (hereinafter referred to as " wheel caster side-play amount ") the δ c at the wheel center height R place of the steering yoke bolt axle of in lateral plan, observing, the leaning angle of the steering yoke bolt axle of in front elevation, observing (hereinafter referred to as " pivot stud angle ") θ k, and the left and right directions side-play amount at the wheel center height R place of the steering yoke bolt axle of in front elevation, observing (hereinafter referred to as " steering yoke bolt introversion side-play amount ") δ k.
Fig. 4 is the distortion angle β of tyre contact patch of the expression wheel that is in turn condition and the figure that transverse force Fy reaches back the relation between the positive moment of torsion Mz.
In Fig. 4, if the working direction of wheel (velocity vector towards) and wheel towards producing skew, make wheel have distortion angle β, then on wheel, produce transverse force Fy.Because this transverse force Fy puts forth effort at the rear side of comparing with the tyre patch center of wheel, so, produce the positive moment of torsion Mz that returns that makes direction that distortion angle β reduces with respect to the ground connection center.
Fig. 5 is the transverse force Fy of expression wheel and the figure that returns the situation that positive moment of torsion Mz produces at wheel center, is the figure that illustrates in order to compare with situation shown in Figure 4.
Have the transverse force Fy that produces under the situation of distortion angle β at wheel, as shown in Figure 4, its acting point is compared with the center of tyre contact patch and is positioned at the rear.Therefore, around the ground connection center, generation as noted above makes the positive moment of torsion Mz that returns of direction that distortion angle β reduces.Relative therewith, as shown in Figure 5, produce the transverse force Fy of wheel and return under the situation of positive moment of torsion Mz at wheel center, above-mentioned transverse force Fy and return the skew that positive moment of torsion Mz can not produce fore-and-aft direction, but as being detected to the power of same position (wheel center) effect.
Fig. 6 is the transverse force Fy and time positive moment of torsion Mz of expression wheel center position and the figure that centers on the relation between the moment Mk of steering yoke bolt axle, Fig. 6 (a) expression wheel caster offset delta c is positive situation, Fig. 6 (b) expression wheel caster offset delta c is zero situation, and Fig. 6 (c) expression wheel caster offset delta c is negative situation.In addition, overlooking the state of observing wheel shown in each figure shown in Figure 6, will have the situation of steering yoke bolt axle at vehicle front with respect to wheel center, is positive situation as wheel caster offset delta c.
In Fig. 6,, wheel caster offset delta c as moment arm, is transformed to around the moment Mk of steering yoke bolt axle for transverse force Fy to the wheel center position effect.On the other hand, to the positive moment of torsion Mz that returns of wheel center effect, Direct Transform is the moment Mk around the steering yoke bolt axle.At this moment, according to the front and back position of wheel center and steering yoke bolt axle relation, can with around the moment of steering yoke bolt axle shown in Fig. 6 (a)～(c), be categorized as following 3 kinds of situations.
(1) wheel caster offset delta c is positive situation
Shown in Fig. 6 (a), at wheel caster offset delta c for just, promptly, in lateral plan, observe, the steering yoke bolt axle is compared under the situation that is positioned at the place ahead with wheel center, by transverse force Fy cause around the moment of steering yoke bolt axle, and be equidirectional by returning the moment that positive moment of torsion Mz causes around the steering yoke bolt axle, promote wheel revolutions separately respectively around the steering yoke bolt axle.
(2) wheel caster offset delta c is zero situation
Shown in Fig. 6 (b), at wheel caster offset delta c is zero, promptly, in lateral plan, observe, under the steering yoke bolt axle situation consistent with wheel center position, do not produce the moment that causes by transverse force Fy, only produce by returning the moment that positive moment of torsion Mz causes around the steering yoke bolt axle around the steering yoke bolt axle.In the case, produce the wheel revolutions that centers on the steering yoke bolt axle by returning positive moment of torsion Mz.
(3) wheel caster offset delta c is negative situation
Shown in Fig. 6 (c), at wheel caster offset delta c is negative, promptly, in lateral plan, observe, the steering yoke bolt axle is compared under the situation that is positioned at the rear with wheel center, the moment around the steering yoke bolt axle by transverse force Fy causes becomes opposite sense with the moment around the steering yoke bolt axle that is caused by time positive moment of torsion Mz, cancels each other out.
In the utility model, utilize the character in the above-mentioned situation (3).That is, in that wheel is produced under the situation of variation of distortion angle β, for wheel, when transverse force Fy changes, the variation that also produces back positive moment of torsion Mz.The transverse force Fy of wheel reaches back positive moment of torsion Mz, and all the time with the shape and the size of pavement roughness, perhaps the size of moving velocity and transverse acceleration etc. changes accordingly.
Therefore, even because above-mentioned factor changes the distortion angle β of wheel, also make and do not change around the moment Mk of steering yoke bolt axle, therefore, variation by reaching back positive moment of torsion Mz with transverse force Fy accordingly, make wheel caster offset delta c, and utilize back value that the ratio Mz/Fy between positive moment of torsion Mz and the transverse force Fy obtains about equally, thereby can prevent unnecessary the rocking of bearing circle 21 with respect to wheel center.
(condition of steering yoke bolt introversion side-play amount)
Fig. 7 is the above-below direction load of expression wheel and the figure that centers on the relation between the moment of steering yoke bolt axle.In addition, Fig. 7 (a) illustrates kingpin caster angle composition (corresponding with the 2nd of formula (1)), and Fig. 7 (b) illustrates pivot stud angle composition (corresponding with the 1st of formula (1)).
The moment Mk around the steering yoke bolt axle by exerting oneself on the wheel to cause can be decomposed into kingpin caster angle composition and pivot stud angle composition.In addition, in Fig. 7, the steering yoke bolt axle is positioned at the situation of body inner side, k is positive situation as steering yoke bolt introversion offset delta.
As shown in Figure 7, the kingpin caster angle component list is shown in pivot stud angle θ k and under zero the state, is positioned at the moment around steering yoke bolt with steering yoke bolt introversion offset delta k out-of-position position.Usually, because the steering yoke bolt axle at the wheel center height place in front elevation, observed, compare with wheel center and to be positioned at body inner side, thus steering yoke bolt introversion offset delta k only get on the occasion of.Therefore, big if steering yoke bolt introversion offset delta k becomes, then the moment around the steering yoke bolt axle also becomes big.
On the other hand, to be shown in kingpin caster angle be under zero the state, to be positioned at the moment around steering yoke bolt with wheel caster offset delta c out-of-position position to the pivot stud angle component list.The steering yoke bolt axle at the wheel center height place of observing in lateral plan is compared with wheel center and to be configured in car body the place ahead or all can in the rear.At this moment, for pivot stud angle composition to the power of the above-below direction of wheel input, at wheel caster offset delta c for just being that the steering yoke bolt axle at wheel center height place is compared under the situation that is positioned at the place ahead with wheel center, and comparing with wheel center under the situation that is positioned at the rear, around the moment of steering yoke bolt axle towards difference.
In the utility model, the above-mentioned moment that utilization is different along with the difference of the position of the steering yoke bolt axle at wheel center height place around the steering yoke bolt axle.That is, make steering yoke bolt introversion offset delta k get on the occasion of the time the kingpin caster angle composition, offset with the pivot stud angle composition of wheel caster offset delta c when negative.If adopt this structure, even then change, also can suppress moment variations around the steering yoke bolt axle to the power of the above-below direction of wheel input, prevent unnecessary the rocking of bearing circle 21.
(comprehensive condition)
Fig. 8 is the figure of the example of the suspension arm 12,13 in the expression draft hitch 1.In addition, Fig. 8 (a) illustrates roughly that the installation site of suspension arm on steering swivel 14 of A font is the situation of 1 point, and Fig. 8 (b) illustrates the situation that the installation site of suspension arm on steering swivel 14 of A font roughly is divided into 2 points.
According to The above results, in the draft hitch 1 of present embodiment, with any illustrated suspension arm among Fig. 8 (a) or Fig. 8 (b), as upper arm and underarm and be configured in steering swivel 14 about.And, the position of the steering yoke bolt axle at the wheel center height place that will in lateral plan, observe, compare with wheel center and to be configured in the rear, and be configured so that steering yoke bolt introversion offset delta k, pivot stud angle θ k, wheel caster offset delta c, kingpin caster angle θ c satisfy the relation of following formula (1).
δc·tan(θk)+δk·tan(θc)≤0 (1)
Wherein,
By adopting this structure, can from the road surface when the input of wheel changes, further reduce rocking of bearing circle 21.
Even wheel caster offset delta c comprises roughly about 20% error with respect to the value that the ratio Mz/Fy that utilizes back between positive moment of torsion Mz and the transverse force Fy obtains, also can play its effect here.
Fig. 9 is expression wheel caster offset delta c and the figure that centers on the relation between the moment variations amount of steering yoke bolt axle.
In Fig. 9, illustrate with the situation of wheel caster offset delta c=0mm and compare, wheel caster offset delta c is substantially equal to back under the situation of the ratio Mz/Fy between positive moment of torsion Mz and the transverse force Fy, and make this value change permissible range α 1 promptly under ± 20% the situation, reduce effect around the variable quantity of the moment of steering yoke bolt axle.As can be known under any situation shown in Figure 9, if as and the cooresponding permissible range α 1 of wheel caster offset delta c, in ± 20%, then play at least minimizing effect with respect to Mz/Fy more than or equal to 30%.
In addition, the value of this α 1 can be corresponding with suspension structure and be set.
In addition, though steering yoke bolt introversion offset delta k with respect to above-mentioned formula (1) as equation and definite value comprises roughly about 20% error, also can play its effect.
Figure 10 is expression steering yoke bolt introversion offset delta k and the figure that centers on the relation between the moment variations amount of steering yoke bolt axle.
In Figure 10, illustrate with the situation of steering yoke bolt introversion offset delta k=60mm and compare, be substantially equal to formula (1) and under the situation of definite value as equation, and make this value change permissible range α 2 promptly under ± 20% the situation, reduce effect around the variation of the moment of steering yoke bolt axle.As can be known under any situation shown in Figure 10,, then play at least minimizing effect more than or equal to 48% if be ± 20% with the cooresponding permissible range α 2 of the situation that with formula (1) is equation.
In addition, the value of this α 2 can be corresponding with suspension structure and be set.
Here, the pacing factor in the formula (1) is the situation of the left side=0, in the case, utilizes independent wheel suspension structure, can offset the load variations to the wheel input all the time.
Relative therewith, in the zone by on the left side＜0, make the suspension structure of left and right wheels interact with each other, offset outer effect of disturbing thereby have.
That is, on the rut road, repair the road, the road surface of fluctuating etc. is arranged, may be subjected to from the road surface for different outer the disturbing of left and right wheels.
At this moment, in the zone of on the left side＜0, have from about the effect that also is cancelled of the outer influence of disturbing of other wheels input.
(deflection angle-favorable camber characteristics) over the ground
Below, the favorable camber characteristics of deflection angle under the situation of setting steering yoke bolt axle as noted above-over the ground is described.
Figure 11 is the figure of the deflection angle of expression wheel and the relation between flare changes over the ground.In addition, in Figure 11 (a), be illustrated in pivot stud angle respectively and be 6 when spending, kingpin caster angle is made as the characteristic under the situations of 3 degree, 6 degree, 9 degree.In addition, in Figure 11 (b), be illustrated in kingpin caster angle respectively and be under the situations of 6 degree, pivot stud angle is made as the characteristic under the situations of 3 degree, 6 degree, 9 degree.
Shown in Figure 11 (a), if under the state of identical pivot stud angle, kingpin caster angle is increased, then can increase foreign steamer to the car body inward camber, wheel to the positive flare of car body in can increasing.
That is, interior wheel, foreign steamer all can make the tire lateral force of inside and outside wheel increase towards producing the flare horizontal thrust in turning.
In addition, shown in Figure 11 (b),, pivot stud angle is reduced, then can make foreign steamer the car body inward camber is increased if under the state of identical kingpin caster angle.On the other hand, if pivot stud angle is increased, wheel increases the positive flare of car body in then can making.
That is, interior wheel, foreign steamer all can make the tire lateral force of inside and outside wheel increase towards producing the flare horizontal thrust in turning.
As noted above, by kingpin caster angle θ c and the pivot stud angle θ k that selects tire lateral force is further increased, thereby the bearing circle 21 opposite with intention that can suppress to be caused by pavement roughness etc. rocks, simultaneously during according to intention direction of operating dish 21, can improve the responsibility of vehicle at chaufeur.
(effect)
Below, illustration.
Figure 12 is the figure of the concrete structure example of the related draft hitch 1 of expression present embodiment.
Below, at the suspension structure of structure example shown in Figure 12, effect of the present utility model is described.
Figure 12 illustrates following structure example, that is, utilize A font roughly and the installation site on steering swivel 14 to be divided into the suspension arm (with reference to Fig. 8 (b)) of 2 points, can rotate freely and swingingly support the strong point up and down of steering swivel 14.In the case, the steering yoke bolt axle is by straight line 14a definition, and this straight line 14a is that the connecting rod that will make upper arm prolongs respectively and the intersection point that obtains and the connecting rod that makes underarm prolong respectively and the intersection point that obtains links.
Figure 13 is illustrated in the suspension structure shown in Figure 12, the state of suspension arm is set to, the angle A1 that the connecting rod X of car body front side is become with extended line L to car body the place ahead is roughly 90 °, the connecting rod Y of car body rear side be 60 ° figure roughly to the angle that extended line L became in car body the place ahead.In addition, in Figure 13, the foreign steamer side when turning to is shown.
Under the situation of example shown in Figure 13, the steering swivel installation site x of the connecting rod X of car body front side is accompanied by turning to of wheel and moves on circular arc L1.In addition, the steering swivel installation site y of the connecting rod Y of car body rear side is accompanied by turning to of wheel and moves on circular arc L2.Its result prolongs connecting rod X, Y respectively and the intersection point P that obtains, moves to position P2 from position P1.
At this moment, wheel center and steering yoke bolt axle are changed to X2 from X1 by the distance of the vehicle fore-and-aft direction between the point, left and right vehicle wheel direction distance changes to Y2 from Y1, make the steering yoke bolt axle observed from wheel center pass through some P to the car body rear and outside car body side shifting.
In addition, Figure 14 is the figure that expression suspension structure shown in Figure 13 is positioned at the state of the wheel side of turning.
Under the situation of example shown in Figure 14, the steering swivel installation site x of the connecting rod X of car body front side is accompanied by turning to of wheel and moves on circular arc L1.In addition, the steering swivel installation site y of the connecting rod Y of car body rear side is accompanied by turning to of wheel and moves on circular arc L2.Its result prolongs connecting rod X, Y respectively and the intersection point P that obtains, moves to P2 from P1.
At this moment, wheel center and steering yoke bolt axle are changed to X2 from X1 by the distance of the vehicle fore-and-aft direction between the point, left and right vehicle wheel direction distance changes to Y2 from Y1, make the steering yoke bolt axle observed from wheel center pass through some P to car body the place ahead and outside car body side shifting.
In the present embodiment, the position of the steering yoke bolt axle at the wheel center height place that will in lateral plan, observe, compare with wheel center and to be configured in the rear, and be constructed such that steering yoke bolt introversion offset delta k, pivot stud angle θ k, wheel caster offset delta c, kingpin caster angle θ c satisfy the relation of formula (1).
Therefore, under above-mentioned Figure 13, any situation shown in Figure 14, by turning under the situation of the power of wheel effect left and right vehicle wheel direction, condition according to the wheel caster side-play amount, by transverse force Fy cause around the moment of steering yoke bolt axle, become opposite sense with the moment that causes by time positive moment of torsion Mz, cancel each other out around the steering yoke bolt axle.
In addition, according to the condition of steering yoke bolt introversion side-play amount,, kingpin caster angle composition and pivot stud angle composition are offset for the power of the vehicle above-below direction of importing to wheel.
Therefore, even change, also can suppress moment variations around the steering yoke bolt axle to the power of the above-below direction of wheel input.
Therefore, the draft hitch 1 related according to present embodiment is even under the situation that the power to the left and right directions of wheel input and above-below direction changes, also can further reduce rocking of bearing circle 21.
In addition, in the present embodiment, steering swivel 14 is corresponding with steering swivel, and suspension arm 12,13 is corresponding with support component.In addition, as the permissible range of formula (1) and the α 2 that illustrates is corresponding with α in claims.
(effect of the 1st embodiment)
(1) steering yoke bolt introversion offset delta k, pivot stud angle θ k, wheel caster offset delta c, kingpin caster angle θ c satisfy the relation of following formula.
δ ctan (θ k)+δ ktan (θ c)≤α (wherein, α for corresponding with suspension structure set 0 near value)
Therefore, from the road surface when the input of wheel changes, owing to can suppress moment around the steering yoke bolt axle, so can further reduce rocking of bearing circle.
(2) steering yoke bolt introversion offset delta k, pivot stud angle θ k, wheel caster offset delta c, kingpin caster angle θ c satisfy the relation of following formula.
δc·tan(θk)+δk·tan(θc)＝0
Thus, can utilize independent wheel suspension structure, offset load variations all the time to the wheel input.
(application examples 1)
In the structure example of the illustrated Figure 12 of the 1st embodiment, can be as the suspension arm of draft hitch 1 be set shown in following.
Figure 15 is illustrated in the suspension structure shown in Figure 12, the state of suspension arm is set to, the angle A1 that makes the connecting rod X of car body front side be become with extended line L to car body the place ahead is roughly 120 °, and the angle that the connecting rod Y of car body rear side is become with extended line L to car body the place ahead is roughly 90 °.In addition, in Figure 15, the foreign steamer side when turning to is shown.
Under the situation of example shown in Figure 15, the steering swivel installation site x of the connecting rod X of car body front side is accompanied by turning to of wheel and moves on circular arc L1.In addition, the steering swivel installation site y of the connecting rod Y of car body rear side is accompanied by turning to of wheel and moves on circular arc L2.Its result prolongs connecting rod X, Y respectively and the intersection point P that obtains, moves to P2 from P1.
At this moment, wheel center and steering yoke bolt axle are changed to X2 from X1 by the distance of the vehicle fore-and-aft direction between the point, left and right vehicle wheel direction distance changes to Y2 from Y1, and a P that passes through of the steering yoke bolt of observing from wheel center is moved to car body rear and body inner side.
In addition, Figure 16 is the figure that expression suspension structure shown in Figure 15 is positioned at the state of the wheel side of turning.
Under the situation of example shown in Figure 16, the steering swivel installation site x of the connecting rod X of car body front side is accompanied by turning to of wheel and moves on circular arc L1.In addition, the steering swivel installation site y of the connecting rod Y of car body rear side is accompanied by turning to of wheel and moves on circular arc L2.Its result prolongs connecting rod X, Y respectively and the intersection point P that obtains, moves to P2 from P1.
At this moment, wheel center and steering yoke bolt axle are changed to X2 from X1 by the distance of the vehicle fore-and-aft direction between the point, left and right vehicle wheel direction distance is changed to Y2 from Y1, make the steering yoke bolt observed from wheel center pass through some P to car body the place ahead and outside car body side shifting.
In should use-case, with the 1st embodiment in the same manner, the position of the steering yoke bolt axle at the wheel center height place that will in lateral plan, observe, compare with wheel center and to be configured in the rear, and be constructed such that steering yoke bolt introversion offset delta k, pivot stud angle θ k, wheel caster offset delta c, kingpin caster angle θ c satisfy the relation of formula (1).
Therefore, under above-mentioned Figure 15, any situation shown in Figure 16, by turning under the situation of the power of wheel effect left and right vehicle wheel direction, condition according to the wheel caster side-play amount, by transverse force Fy cause around the moment of steering yoke bolt axle, become opposite sense with the moment that causes by time positive moment of torsion Mz, cancel each other out around the steering yoke bolt axle.
In addition, according to the condition of steering yoke bolt introversion side-play amount,, kingpin caster angle composition and pivot stud angle composition are offset for the power of the vehicle above-below direction of importing to wheel.
Therefore, even change, also can suppress moment variations around the steering yoke bolt axle to the power of the above-below direction of wheel input.
Therefore, according to should the related draft hitch 1 of use-case, even under the situation that the power to the left and right directions of wheel input and above-below direction changes, also can further reduce rocking of bearing circle 21.
(application examples 2)
In the 1st embodiment, draft hitch 1 has been described by satisfying the condition of formula (1), thereby from the road surface when the input of wheel changes, further reduce rocking of bearing circle 21.
In should use-case, further study the structure of suspension, in formula (1), set additional conditions.
Below, the additional conditions of explanation in should use-case.
The left side of formula (1) can be rewritten shown in (2).
δc·tan(θk)≤-δk·tan(θc) (2)
If as the x axle, as the y axle, then the equation of formula (2) is represented 1 straight line with the left side with the right of formula (2).
Figure 17 is expression with the right of formula (2) as x axle, the figure of straight line of equation representative with the left side during as the y axle.
In Figure 17, near the zone the initial point is, kingpin caster angle θ c and pivot stud angle θ k are zero, and perhaps wheel caster offset delta c and steering yoke bolt introversion offset delta k are zero zone.
In this zone, there is following characteristics in the characteristic as suspension.
(1) kingpin caster angle θ c and pivot stud angle θ k are zero situation
If carry out the setting of this steering yoke bolt axle, then be changed to zero with the flare that turns to wheel together, can't utilize the increase effect of the tire lateral force when turning.In addition, in the case, can't expect the raising of vehicle response.
(2) wheel caster offset delta c and steering yoke bolt introversion offset delta k are zero situation
If carry out the setting of this steering yoke bolt axle, suspension arm is interfered, perhaps make around the torsional rigid of wheel revolutions axle and reduce.
Figure 18 is that the installation site that is illustrated on the steering swivel 14 is the suspension arm (with reference to Fig. 8 (a)) of 1 point and the figure that steering yoke bolt introversion offset delta k is made as zero state (solid line among the figure).
As shown in figure 18, have under the situation of 1 ball-and-socket type joint,, must make ball-and-socket type joint consistent with wheel center position for steering yoke bolt introversion offset delta k being made as zero at the strong point up and down of the steering swivel 14 that links suspension arm.
In the case, owing to can interfere, be difficult to steering yoke bolt introversion offset delta k is made as zero with the parts such as drg that are configured in inside wheel.
In addition, Figure 19 is that the installation site that is illustrated on the steering swivel 14 is the suspension arm (with reference to Fig. 8 (b)) of 2 points and the figure that steering yoke bolt introversion offset delta k is made as zero state (solid line among the figure).
As shown in figure 19, have under the situation of 2 ball-and-socket type joints, for steering yoke bolt introversion side-play amount being made as zero, and make the interval of between ball-and-socket type joint, guaranteeing further broaden at the strong point up and down of the steering swivel 14 that links suspension arm.
In the case, utilization to the moment in spin of wheel effect, reverses the front-rear linkage of suspension arm when quickening easily to the vehicle above-below direction.
Therefore, preferably steering yoke bolt introversion offset delta k is set at 20mm at least, preferred kingpin caster angle θ c is more than or equal to 3 degree.That is, δ ktan (θ c)＞1.05 (the solid line part of Figure 19) is for expecting the zone of higher effect.
(application examples 3)
With respect to the structure example of the Figure 12 that illustrates in the 1st embodiment, can shown in following, constitute draft hitch 1.
Figure 20 is the figure of other structure example of the related draft hitch 1 of expression the 1st embodiment.
In structure example shown in Figure 20, show to constitute and utilize the roughly suspension arm of A font (with reference to Fig. 8 (a)), can rotate freely and swingingly support the example of the strong point up and down of steering swivel 14.In the case, the steering yoke bolt axle is defined by the straight line 14a that the strong point up and down with steering swivel 14 links.
For this suspension structure, also can use the utility model, even under the situation that the power to the wheel input changes, also can further reduce rocking of bearing circle 21.
(application examples 4)
With respect to the structure example of the Figure 12 that illustrates in the 1st embodiment, can shown in following, constitute draft hitch 1.
Figure 21 is the figure of other structure example of the related draft hitch 1 of expression the 1st embodiment.
In structure example shown in Figure 21, show constitute utilize the suspension arm of A font (with reference to Fig. 8 (a)) roughly and roughly A font and the installation site on steering swivel 14 be divided into the suspension arm (with reference to Fig. 8 (b)) of 2 points, can rotate freely and swingingly support the example of the strong point up and down of steering swivel 14.In addition, in Figure 21, show upper arm and be the suspension arm of A font roughly, underarm is for roughly A font and the installation site on steering swivel 14 are divided into the situation of the suspension arm of 2 points.But, also can adopt structure with upper arm and underarm exchange.
Under the situation of structure example shown in Figure 21, the steering yoke bolt axle is by straight line 14a definition, and this straight line 14a is that the strong point of steering swivel 14 upsides and the connecting rod that makes underarm prolong respectively and the intersection point that obtains links.
For this suspension structure, also can use the utility model, even under the situation that the power to the wheel input changes, also can further reduce rocking of bearing circle 21.
(the 2nd embodiment)
Below, the 2nd embodiment of the present utility model is described.
In the present embodiment, with respect to the condition of the draft hitch in the 1st embodiment 1, additional consideration the condition during wheel steering.
Below, the condition of the draft hitch 1 when specifying wheel steering.
The transverse force Fy of tire reaches moment (the returning positive moment of torsion) Mz around vertical axis, according to the load of importing to wheel up and down, distortion angle, camber angle etc., carries out various variations.
Figure 22 is the figure of expression distortion angle and the relation between the power of wheel effect.In addition, Figure 22 (a) is the figure of expression tire lateral force Fy with respect to the variation of distortion angle, and Figure 22 (b) is expression around the moment Mz of the vertical axis figure with respect to the variation of distortion angle.In addition, Figure 22 (c) expression Mz/Fy is with respect to the variation of distortion angle.
Shown in Figure 22 (c), along with distortion angle becomes big, the value of Mz/Fy diminishes gradually.That is, in the suspension structure of the 1st embodiment, if become the neutral condition of wheel, promptly the value of the Mz/Fy the distortion angle and zero near then can further reduce rocking of bearing circle 21 about equally.
On the other hand, in the suspension structure of present embodiment, suspension arm is configured to, with wheel steering accordingly, the wheel caster side-play amount is diminished.
Specifically, on the strong point up and down of steering swivel 14, suspension arm is set with Figure 13, mode shown in Figure 14.
In the case, take turns for the turning foreign steamer or in turning, the steering yoke bolt axle of observing from wheel center passes through point, and the increase that is accompanied by deflection angle is forwards moved, and can reduce the wheel caster side-play amount.
As noted above, in the present embodiment because suspension arm is configured to, with wheel steering accordingly, the wheel caster side-play amount is diminished, so when Vehicular turn, can further reduce rocking of bearing circle.
Since around the moment variations of steering yoke bolt axle via steering rack and Steering gear to the bearing circle transmission, so, can reduce rocking of bearing circle by suppressing moment variations around the steering yoke bolt axle.
(effect of the 2nd embodiment)
(1) when making wheel steering, constitute first strong point of steering yoke bolt axle and constitute in second strong point of steering yoke bolt axle at least one move, make the wheel caster side-play amount become wheel around the ratio between the transverse force of the moment of vertical axis and wheel.
Therefore, big even distortion angle becomes, the ratio around between the transverse force of the moment of vertical axis and wheel of wheel diminishes, and also can make the ratio around between the transverse force of the moment of vertical axis and wheel of wheel caster side-play amount and wheel consistent.
(the 3rd embodiment)
Below, the 3rd embodiment of the present utility model is described.
In the present embodiment, with respect to the condition of the draft hitch in the 1st embodiment 1, additional consideration the condition during wheel steering.
Below, the condition of the draft hitch 1 when specifying wheel steering.
In the draft hitch 1 of present embodiment, suspension arm is configured to, with wheel steering accordingly, kingpin caster angle is increased.
Specifically, the downside (underarm) at steering swivel 14 disposes suspension arm with Figure 13, mode shown in Figure 14, and the upside (upper arm) at steering swivel 14 disposes suspension arm with Figure 15, mode shown in Figure 16.
In the case, and turn to accordingly, steering swivel 14 bottoms amount of movement is forwards compared with steering swivel 14 top amount of movements and to be become big, can little by little make kingpin caster angle become big.
As noted above, in the present embodiment, can be with the camber angle over the ground that turns to respect to interior foreign steamer, be set in the turning of vehicle towards, tire lateral force is increased.
That is, the bearing circle opposite with intention that can suppress to be caused by pavement roughness etc. rocks, and during according to intention direction of operating dish, can improve the responsibility of vehicle at chaufeur simultaneously.
(effect of the 3rd embodiment)
(1) deflection angle of wheel is big more, compares when the kingpin caster angle of interior foreign steamer is positioned at center position with wheel to become big more.
Therefore, can be with the camber angle over the ground that turns to respect to interior foreign steamer, be set in the turning of vehicle towards, tire lateral force is increased.
(the 4th embodiment)
Below, the 4th embodiment of the present utility model is described.
In the present embodiment, with respect to the condition of the draft hitch in the 1st embodiment 1, additional consideration the condition during wheel steering.
Below, the condition of the draft hitch 1 when specifying wheel steering.
In the draft hitch 1 of present embodiment, suspension arm is configured to, with wheel steering accordingly, the pivot stud angle of foreign steamer is compared with the pivot stud angle of interior wheel is diminished.
Specifically, the downside (underarm) at steering swivel 14 disposes suspension arm with Figure 15, mode shown in Figure 16, and the upside (upper arm) at steering swivel 14 disposes suspension arm with Figure 13, mode shown in Figure 14.
In the case, and turn to accordingly, steering swivel 14 bottoms are the amount of movement of direction to the left and right, with steering swivel 14 tops to the left and right the amount of movement of direction compare and become big, can pivot stud angle be diminished.
As noted above, in the present embodiment, can be with the camber angle over the ground that turns to respect to interior foreign steamer, be set in the turning of vehicle towards, tire lateral force is increased.
That is, the bearing circle opposite with intention that can suppress to be caused by pavement roughness etc. rocks, and during according to intention direction of operating dish, can improve the responsibility of vehicle at chaufeur simultaneously.
(effect of the 4th embodiment)
(1) deflection angle of wheel is big more, and the kingpin caster angle of foreign steamer is compared more with the kingpin caster angle of interior wheel and diminished.
Therefore, can be with the camber angle over the ground that turns to respect to interior foreign steamer, be set in the turning to of vehicle towards, tire lateral force is increased.
Claims (4)
1. suspension device for rolling stock is characterized in that having:
Steering swivel, it is swung with wheel when turning to; And
Support component, it supports described steering swivel swingably,
The steering yoke bolt axle at the wheel center height place in the front elevation and the distance between the wheel center are that steering yoke bolt axle in steering yoke bolt introversion offset delta k, the front elevation and the plumb bob vertical angulation steering yoke bolt axle that is the wheel center height place in pivot stud angle θ k, the lateral plan and the distance between the wheel center are that steering yoke bolt axle and plumb bob vertical angulation in wheel caster offset delta c, the lateral plan is kingpin caster angle θ c, satisfy the relation of following formula (1)
δc·tan(θk)+δk·tan(θc)≤α (1)
Wherein, α for corresponding with suspension structure set 0 near value.
2. suspension device for rolling stock according to claim 1 is characterized in that,
Described steering yoke bolt introversion offset delta k, described pivot stud angle θ k, described wheel caster offset delta c, described kingpin caster angle θ c satisfy the relation of following formula (2),
δc·tan(θk)+δk·tan(θc)＝0 (2)。
3. suspension device for rolling stock according to claim 1 and 2 is characterized in that,
The deflection angle of wheel is big more, compares when the kingpin caster angle of interior foreign steamer is positioned at center position with deflection angle to become big more.
4. suspension device for rolling stock according to claim 1 and 2 is characterized in that,
The deflection angle of wheel is big more, and the pivot stud angle of foreign steamer is compared more with the pivot stud angle of interior wheel and diminished.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010040670A JP2011173561A (en) | 2010-02-25 | 2010-02-25 | Suspension device for vehicle |
| JP2010-040670 | 2010-02-25 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202080083U true CN202080083U (en) | 2011-12-21 |
Family
ID=44686852
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011200509047U Expired - Fee Related CN202080083U (en) | 2010-02-25 | 2011-02-25 | Vehicular suspension device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2011173561A (en) |
| CN (1) | CN202080083U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102887170A (en) * | 2012-09-25 | 2013-01-23 | 湖南中联重科车桥有限公司 | Steering joint, steering front axle assembly and vehicle |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010018172A (en) * | 2008-07-11 | 2010-01-28 | Bridgestone Corp | Wheel alignment adjusting device |
-
2010
- 2010-02-25 JP JP2010040670A patent/JP2011173561A/en active Pending
-
2011
- 2011-02-25 CN CN2011200509047U patent/CN202080083U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102887170A (en) * | 2012-09-25 | 2013-01-23 | 湖南中联重科车桥有限公司 | Steering joint, steering front axle assembly and vehicle |
| CN102887170B (en) * | 2012-09-25 | 2015-08-19 | 湖南中联重科车桥有限公司 | Steering swivel, steering front shaft assembly and vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011173561A (en) | 2011-09-08 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20111221 Termination date: 20160225 |