CN202703154U - Multi-connecting rod rectilinear translation type suspension using ball spline pair - Google Patents

Abstract

The utility model relates to a multi-connecting rod rectilinear translation type suspension using ball spline pairs. The suspension comprises a spring absorber system, a wheel, an vehicle body and a steering knuckle, as well as an upper-side first suspension branch chain, an upper-side second suspension branch chain, a lower-side first suspension branch chain and a lower-side second suspension branch chain, wherein the spring absorber system is in hinged connection with the steering knuckle and the vehicle body respectively, the steering knuckle cooperates with the wheel through a wheel hub unit, and two ends of the four suspension branch chains are hinged to the steering knuckle and the vehicle body respectively. The beneficial effects of the utility model are that positional parameters such as a wheel camber angle, a kingpin inclination angle and caster angle, a toe-in (toe-out), a left and right wheel span and a front and back wheel base can always remain unchanged when the wheel is bounced up and down, thereby effectively reducing abrasion of tires and effectively raising operation stability, running smoothness and riding comfortableness of an automobile; and the suspension branch chains are simple in structure, and the ball spline pairs are replaceable after being worn, thereby increasing service life of the suspension branch chains.

Description

Adopt many link linears parallel-moving type suspension of ball spline pair

Technical field

The utility model relates to automobile suspension system, especially a kind of many link linears parallel-moving type suspension that adopts the ball spline pair.

Background technology

Suspension be guarantee to have between wheel or vehicle bridge and the automobile bearing system (vehicle frame or self-supporting body) the elasticity contact and can transmitted load, mitigation impact, damped vibration and the vehicles general name of the relative assembly such as vehicle body position in the process of moving.General suspension mainly is comprised of elastic element, shock attenuation unit and guiding mechanism three parts.In some cases, a certain parts held concurrently two kinds or three kinds of effects are such as the steel spring effect of elastic element and guiding mechanism of having held concurrently.Wherein the function of guiding mechanism is to guarantee force and moment reliable delivery all between wheel and vehicle body or the vehicle frame, and determines that wheel is with respect to the placement property of vehicle body or vehicle frame.Path of motion when guiding mechanism has determined wheel bounce and the situation of change of wheel alignment parameter, and the position at roll center and trim center before and after the automobile have affected road-holding property and the anti-trim ability of car load to a great extent.

According to the characteristics of guiding mechanism, automotive suspension mainly can be divided into dependent suspension and independent suspension two large classes.The characteristic feature of dependent suspension is to be connected by a buttress bracing struts or non-disconnected vehicle bridge between the left and right wheels, when monolateral wheel bounce, directly has influence on the opposite side wheel.The independent suspension left and right wheels links to each other with vehicle body or vehicle frame separately " independence " or consists of broken bridge of car.In addition, also have the semi-independent suspension of a kind of characteristics between dependent suspension and independent suspension.The dependent suspension shortcoming is obvious, such as left and right wheels beat interact, non-suspended mass is larger etc., can not satisfy the requirement of current vehicle running smoothness and road-holding property aspect, so independent suspension has obtained very large development.

The constructional feature of independent suspension is that the wheel of both sides connects with vehicle body or vehicle frame by resilient suspension individually, and vehicle bridge is made breakaway-element.Therefore, independent suspension has following advantage: one, in the certain deformation range of suspension spring, the both sides wheel can self-movement, and be independent of each other, when travelling, can reduce rough road like this vibration of vehicle frame and vehicle body, and help to eliminate the bad phenomenon of the continuous beat of wheel flutter, and promoted automobile straight line driveability, guaranteed good road-holding property.Two, reduced the automobile nonspring carried mass.In the dependent suspension situation, whole vehicle bridge and wheel all belong to the nonspring carried mass part.In the independent suspension situation, for drive axle, because main reduction gear, diff and shell thereof all are fixed on the vehicle frame, have become spring carried mass; For steeraxle, it only has steering yoke bolt and steering swivel, and the unjointed beam at middle part no longer exists.So when adopting independent suspension, nonspring carried mass comprises all or part of quality of a part of part in wheel mass and the suspension system, nonspring carried mass is much smaller during obviously than the usefulness dependent suspension.Nonspring carried mass is less when road conditions is identical with the speed of a motor vehicle, and then the suffered impact load of suspension is less, so adopt independent suspension can improve the ground connection performance of vehicle running smoothness and tire.When three, adopting broken bridge of car, the position of engine assembly just can reduce and reach descends centre of gravity of vehicle, has improved Riding Stability of Automobile.Give simultaneously wheel larger up-and-down movement space, thereby can design suspension rate less, the body vibrations frequency is reduced, to improve riding comfort.Four, be easy to realize that drive wheel turns to.Above advantage is widely used on the modern automobile independent suspension, and particularly the wheel flutter of car has all generally adopted independent suspension, and in order to improve driving safety, the rear overhang of increasing luxury car has also adopted independent suspension.

At present, most widely used independent suspension mainly contains on automobile: double cross arm independent suspension, MacPherson strut and multi-connecting-rod separated suspension.The outstanding advantages of double cross arm independent suspension is flexible design, but wheel alignment parameter and wheelspan change greatly when adopting the automotive wheel of this suspension to beat, and have reduced automobile straight line driveability, cause road-holding property relatively poor, simultaneously the tire serious wear.The advantage of McPherson strut is simple in structure, save the space, and the positional parameters such as its wheelspan, toe-in and outward camber change little in the wheel bounce process, alleviated wear on tyres, also so that automobile has preferably road-holding property, but its designability is relatively poor, and there is friction force between the piston rod of shock absorber and the orienting sleeve, so that the increase of the dynamic stiffness of suspension, the elastic behavior variation, especially this impact is more remarkable when little displacement.The advantage of multi-connecting-rod separated suspension mainly is that wheel alignment parameter changes very little in the time of can guaranteeing wheel bounce, but its design flexibility is poor, and is very responsive to the bar linkage structure parameter, and the processing and manufacturing accuracy requirement is high, the equipment adjustment difficulty is mainly used in medium-to-high grade car at present.

Although conventional independent suspension can both satisfy the suspension design requirement on function at present, when wheel bounce, wheel alignment parameter all can change.In actual applications, the larger variation meeting of wheel alignment parameter has a negative impact to vehicle handling stability or other aspect performances, can cause automobile straight line driveability to descend such as the variation of wheelspan, also cause simultaneously rolling resistance to increase and on the impact of steering swivel system; The variation of camber angle can cause the inordinate wear of tire.

Can not change be a Focal point and difficult point in the independent suspension structure innovative design to the positional parameter of wheel in the time of how can guaranteeing wheel bounce.Universal group and Tsing-Hua University once united three kinds of linear guiding mechanisms that can be used in automotive suspension of proposition, referring to [1. Zhao Jingshan mountain, Wang Jianyi. spatial multi-connecting bar forktruck lift guide mechanism [P]. Chinese patent: 200910085582.7,2009-11-4.], [2. support holt, Zhao Jingshan, Zhang Jie, Liu is to. a kind of many link linear guide independent suspensions [P] with 3-RRR flexible compensation mechanism. Chinese patent: CN201110215816.2,2012-02-22.], [3. outstanding person, Zhao Jingshan, the money holt, Wang Jianyi. a kind of elastic multi-link linear guide independent suspension [P]. Chinese patent: CN201110218599.2,2012-02-22.].The suspension side chain is the RPR kinematic link in the above-mentioned patent [1], have preferably each to rigidity, but the RPR kinematic link is not suitable for use in the suspension guide mechanism owing to existing moving sets to cause mobile vice division chief cliding friction larger; [2] the suspension side chain is the RRR kinematic link in, and it is along relatively poor perpendicular to the directional stiffness on the determined plane of RRR kinematic link, and hinge movement is secondary a lot; [3] side chain of suspension is elastic multi-link in, and rigidity is relatively poor longitudinally along wheel for its guiding mechanism, and the guiding mechanism bob is during to end position, and elastic rod may produce motion and suddenly change; And elasticity, intensity and toughness for the pilot bar composite material have very high requirement.Therefore the practicality of above-mentioned 3 kinds of suspension pilot bars is not strong, needs to continue to be improved.

The utility model content

The utility model will solve the shortcoming of above-mentioned prior art, a kind of many link linears parallel-moving type suspension that can be used for the employing ball spline pair of Motor Vehicle Independent Suspension System is provided, camber angle, Kingpin inclination angle and casterangle, left and right wheels distance, toeing-in (posterior cord) and the wheel base of realizing wheel can remain constant in wheel bob process, thereby improve road-holding property, the riding comfort of automobile and the traveling comfort of taking, and can effectively reduce the wearing and tearing of tire.Simultaneously, under the prerequisite with stronger exploitativeness, it is large respectively to rigidity to guarantee that this suspension fork mechanism has, and reduces as far as possible the stand under load distortion.

The utility model solves the technical scheme that its technical matters adopts: many link linears parallel-moving type suspension of this employing ball spline pair, comprise jounce bumper system, wheel, vehicle body and steering swivel, and upside article one suspension side chain, upside second suspension side chain and downside article one suspension side chain, downside second suspension side chain, described jounce bumper system is hinged with steering swivel and vehicle body respectively, steering swivel cooperates with wheel by hub, and the two ends of four suspension side chains are hinged with steering swivel and vehicle body respectively.

As preferably, upside article one suspension side chain, upside second suspension side chain, downside article one suspension side chain and downside second suspension side chain comprise dust boot, short connecting rod, set pin, buffer gasket, castellated shaft, oil-hole screw, flat key, hub splines, back-up ring, bolt and long connecting rod all with the structure of ball spline pair.Wherein, short connecting rod and castellated shaft adopt transition fit, and by the set pin captive joint, castellated shaft and hub splines cooperate, the spline back-up ring is connected with castellated shaft by bolt, and hub splines is provided with flat key and adopts transition fit with long connecting rod, also is provided with dust boot on the suspension side chain.

As preferably, the vertical plane at 2 suspension side chain places that upside is a group is non-coplanar, and the vertical plane at 2 suspension side chain places that downside is a group is also non-coplanar, the intersection conllinear on above-mentioned these two groups of vertical planes or parallel.

As preferably, the vertical plane at upside article one suspension side chain and downside article one suspension side chain place is coplanar, and the vertical plane at upside second suspension side chain and downside second suspension side chain place is coplanar, and the angle on two vertical planes is 90 °.

As preferably, steering swivel is provided with upside the first journal stirrup, upside the second journal stirrup, downside the first journal stirrup and downside the second journal stirrup, and steering swivel also is provided with jounce bumper connecting bore one, jounce bumper connecting bore two, brake caliper connecting bore one and brake caliper connecting bore two.

The effect that utility model is useful is: the positional parameters such as camber angle, Kingpin inclination angle and casterangle, toeing-in (posterior cord), left and right wheels distance and wheel base that can realize wheel can remain constant in wheel bob process, thereby effectively reduce the wearing and tearing of tire, and can effectively improve road-holding property, the riding comfort of automobile and the traveling comfort of taking; The suspension branched structure is simple, and can change after the secondary wearing and tearing of ball spline, has improved the work life of suspension side chain.

Description of drawings

Fig. 1 is structural representation of the present utility model.

Fig. 2 is suspension branched structure scheme drawing.

Fig. 3 is the structural representation of steering swivel.

Fig. 4 is the birds-eye view of this suspension system.

Fig. 5 be this suspension system along the x axle to view.

Description of reference numerals: jounce bumper system 1, wheel 2, vehicle body 3, steering swivel 4, upside article one suspension side chain 5a, upside second suspension side chain 5b, downside article one suspension side chain 6a, downside second suspension side chain 6b, dust boot 7, weak point connects 8, set pin 9, buffering spacer 10, castellated shaft 11, oil-hole screw 12, flat key 13, hub splines 14, back-up ring 15, bolt 16, long connecting rod 17, jounce bumper connecting bore one 18a, jounce bumper connecting bore two 18b, brake caliper connecting bore one 19a, brake caliper connecting bore two 19b, hub anchor shaft 20, upside the first journal stirrup 21a, upside the second journal stirrup 21b, downside the first journal stirrup 22a, downside the second journal stirrup 22b.

The specific embodiment

The utility model is described in further detail below in conjunction with accompanying drawing:

Embodiment: such as Fig. 1, this many link linears parallel-moving type suspension comprises wheel 2, vehicle body 3, jounce bumper system 1 and steering swivel 4.Described steering swivel 4 connects with wheel 2 by hub, and jounce bumper system 1 is hinged with steering swivel 4 and vehicle body 3 respectively.This system also comprises four suspension side chains, is respectively upside article one suspension side chain 5a, upside second suspension side chain 5b, and downside article one suspension side chain 6a, downside second suspension side chain 6b, their two ends are hinged with steering swivel 4 and vehicle body 3 respectively.

Suspension side chain shown in Figure 2 includes dust boot 7, short connecting rod 8, set pin 9, buffer gasket 10, castellated shaft 11, oil-hole screw 12, flat key 13, hub splines 14, back-up ring 15, bolt 16 and long connecting rod 17.Described short connecting rod 8 and castellated shaft 11 adopt transition fit, and connect by set pin 9, are convenient to dismounting.Described castellated shaft 11 and hub splines 14 cooperate, so that the suspension side chain only has flexible vertically degree of freedom, and the ball spline pair is gauge member.Described colored back-up ring 15 is connected with castellated shaft 11 by bolt 16, and its effect is to prevent from that castellated shaft is drawn out of to cause hub splines 14 inner balls to drop.Described hub splines 14 adopts transition fit with long connecting rod 17, and flat key 13 can transmit than high pulling torque.Described dust boot 7 is installed on the suspension side chain, effect be prevent dust, waterproof and corrosion prevention.

Article four, the suspension side chain is crossed constraint so that suspension system only has one degree of freedom, and wherein the vertical plane at four suspension side chain places is non-coplanar, and intersection conllinear or parallel.For stability of configuration and the raising load-carrying capacity that improves suspension fork mechanism, the vertical plane at upside article one suspension side chain 5a and downside article one suspension side chain 6a place is coplanar, the vertical plane at upside second suspension side chain 5b and downside second suspension side chain 6b place is coplanar, and the angle on two vertical planes is 90 °, as shown in Figure 4.

As shown in Figure 3, steering swivel 4 is provided with upside the first journal stirrup 21a, upside the second journal stirrup 21b, downside the first journal stirrup 22a and downside the second journal stirrup 22b, and steering swivel 4 also is provided with jounce bumper connecting bore one 18a, jounce bumper connecting bore two 18b, brake caliper connecting bore one 19a and brake caliper connecting bore two 19b.Wherein, be equipped with suspension side chain connecting bore on four journal stirrups, the intersection on determined two the vertical planes of suspension side chain connecting bore axis of two journal stirrups of upside, with the intersection on determined two the vertical planes of suspension side chain connecting bore axis of two journal stirrups of downside, both overlap or are parallel.

It is that mechanism characteristics by this suspension fork mechanism determines that many link linears parallel-moving type suspension provided by the utility model only has the degree of freedom that moves along the z axle, next just analyzes the theory of mechanisms motion characteristics of this suspension fork mechanism.

The corresponding system of axes oxyz of model, take upside article one suspension side chain 5a and vehicle body junction revolute pair axis as the x axle, y axle along continuous straight runs is positioned at the vertical plane at suspension side chain place, and corresponding z axle is along vertical, as shown in Figure 4 and Figure 5.If suspension side chain A ₁B ₁Length be l ₁, the angle that suspension props up chain axis and plane oxy is According to [Zhao Jingshan, Feng Zhijing, Chu Fulei. robot mechanism Degree of Freedom Analysis theoretical [M]. Beijing: Science Press, 2009.] analysis theories of the mechanism freedom that proposes, can write out suspension side chain A ₁B ₁Kinematic screw be:

${\$}_{A_1{B}_1}=\left[\begin{array}{ccc}{\$}_{A_1}& {\$}_{P_1}& {\$}_{B_1}\end{array}\right]---\left(1\right)$

Wherein, ${\$}_{A_1}={\left[\begin{array}{cccccc}1& 0& 0& 0& 0& 0\end{array}\right]}^T$

Suspension side chain A ₁B ₁End conswtraint

Can be obtained by the reciprocity screw theory, namely

$ ^TE$ ^r=0（2）

Wherein $ is kinematic screw system, $E=\left[\begin{array}{cc}0& I_3\\ {\mathrm{<figure-callout\; id="3"\; label="I"\; filenames="HDA0000157232600000011.png"\; state="\{\{state\}\}">I</figure-callout>}}_3& 0\end{array}\right],$ ${\mathrm{<figure-callout\; id="3"\; label="I"\; filenames="HDA0000157232600000011.png"\; state="\{\{state\}\}">I</figure-callout>}}_3=\left[\begin{array}{ccc}1& 0& 0\\ 0& 1& 0\\ 0& 0& 1\end{array}\right],$ $ ^rAntispin system for $.

Obvious matrix

The condition of contraction is:

If l ₁Be zero, then this moment revolute pair A ₁With B ₁Overlap revolute pair A in the reality ₁And B ₁Do not overlap, so suspension side chain A ₁B ₁End conswtraint

Can be obtained by the reciprocity screw theory.Can be obtained by (2) formula

For:

${\$}_{A_1{B}_1}^r={\left[\begin{array}{cccccc}1& 0& 0& 0& 0& 0\\ 0& 0& 0& 0& 1& 0\\ 0& 0& 0& 0& 0& 1\end{array}\right]}^T---\left(3\right)$

Another suspension side chain A that can write out equally, ₂B ₂The constraint spiral be:

${\$}_{A_2{B}_2}^r={\left[\begin{array}{cccccc}0& 1& 0& 0& 0& 0\\ 0& 0& 0& 1& 0& 0\\ 0& 0& 0& 0& 0& 1\end{array}\right]}^T---\left(4\right)$

Therefore, steering swivel 4 suffered being constrained to:

${\$}_4^r=\left[\begin{array}{cc}{\$}_{A_1{B}_1}^r& {\$}_{A_2{B}_2}^r\end{array}\right]---\left(5\right)$

(5) formula substitution (2) formula can be obtained the free motion that steering swivel 4 has is:

$ ₄=[0?0?0?0?0?1] ^T（6）

Formula (6) shows that steering swivel 4 has one along the free motion of z direction of principal axis translation, thereby the steering swivel 4 of this spacing multi-connecting-rod linear guiding suspension fork mechanism can be done the motion of translation of single degree of freedom boning out.In like manner, can only have along the free motion of z direction of principal axis translation in the hope of steering swivel under four suspension side chain constraints.Therefore, this spacing multi-connecting-rod linear guiding suspension fork mechanism can make the parameters such as camber angle, Kingpin inclination angle and casterangle, wheelspan and wheelbase of the wheel that links with steering swivel 4 remain unchanged in the wheel bounce process.So just the wearing and tearing of tire be can reduce to greatest extent, and then road-holding property, riding comfort and the travelling comfort of automobile improved.Owing to adopted the gauge member ball spline secondary, the suspension branched structure is simple simultaneously, and processing technology is simple; Article four, the suspension side chain is crossed the load-carrying capacity that constraint has strengthened suspension fork mechanism.

Because this suspension system only has a degree of freedom that moves along the z axle, so revolute pair B ₁Distance along y direction of principal axis and x axle remains constant in the suspension hopping process, establishes this distance and is L, as shown in Figure 5, then

When supposing that suspension is positioned at the up-downgoing way limit, corresponding angle is respectively

With

Then the stroke of suspension and suspension prop up chain length change amount and are respectively:

Therefore, many link linears parallel-moving type suspension of employing ball spline pair provided by the utility model can according to the suspension system designs requirement of reality, carry out suspension fork mechanism stroke and corresponding other design of Structural Parameters.This suspension fork mechanism is with respect to present other known suspension fork mechanisms, not only can guarantee that wheel alignment parameter does not change in the wheel bounce process, and it is respectively large to rigidity, and structure design is simple, and then has improved road-holding property, riding comfort and the travelling comfort of automobile.

In addition to the implementation, the utility model can also have other embodiments.All employings are equal to the technical scheme of replacement or equivalent transformation formation, all drop on the protection domain of the utility model requirement.

Claims (7)

1. many link linears parallel-moving type suspension that adopts the ball spline pair, comprise jounce bumper system (1), wheel (2), vehicle body (3) and steering swivel (4), and upside article one suspension side chain (5a), upside second suspension side chain (5b) and downside article one suspension side chain (6a), downside second suspension side chain (6b), it is characterized in that: described jounce bumper system (1) is hinged with steering swivel (4) and vehicle body (3) respectively, steering swivel (4) cooperates with wheel (2) by hub, four suspension side chain (5a, 5b and 6a, two ends 6b) are hinged with steering swivel (4) and vehicle body (3) respectively.

2. many link linears parallel-moving type suspension of employing ball spline pair according to claim 1, it is characterized in that: described upside article one suspension side chain (5a), upside second suspension side chain (5b), downside article one suspension side chain (6a) and downside second suspension side chain (6b) comprise dust boot (7) all with the structure of ball spline pair, short connecting rod (8), set pin (9), buffer gasket (10), castellated shaft (11), oil-hole screw (12), flat key (13), hub splines (14), back-up ring (15), bolt (16) and long connecting rod (17).

3. many link linears parallel-moving type suspension of employing ball spline pair according to claim 2, it is characterized in that: described short connecting rod (8) and castellated shaft (11) adopt transition fit, and by set pin (9) captive joint, castellated shaft (11) and hub splines (14) cooperate, spline back-up ring (15) is connected with castellated shaft (11) by bolt (16), hub splines (14) is provided with flat key (13) and adopts transition fit with long connecting rod (17), also is provided with dust boot (7) on the suspension side chain.

4. many link linears parallel-moving type suspension of employing ball spline pair according to claim 1, it is characterized in that: the vertical plane at 2 suspension side chains (5a, 5b) place that upside is a group is non-coplanar, the vertical plane at 2 suspension side chains (6a, 6b) place that downside is a group is also non-coplanar, the intersection conllinear on above-mentioned these two groups of vertical planes or parallel.

5. many link linears parallel-moving type suspension of employing ball spline pair according to claim 1, it is characterized in that: the vertical plane at upside article one suspension side chain (5a) and downside article one suspension side chain (6a) place is coplanar, the vertical plane at upside second suspension side chain (5b) and downside second suspension side chain (6b) place is coplanar, and the angle on two vertical planes is 90 °.

6. many link linears parallel-moving type suspension of employing ball spline pair according to claim 1, it is characterized in that: steering swivel (4) is provided with upside the first journal stirrup (21a), upside the second journal stirrup (21b), downside the first journal stirrup (22a) and downside the second journal stirrup (22b), and steering swivel (4) also is provided with jounce bumper connecting bore one (18a), jounce bumper connecting bore two (18b), brake caliper connecting bore one (19a) and brake caliper connecting bore two (19b).

7. many link linears parallel-moving type suspension of employing ball spline pair according to claim 6, it is characterized in that: be equipped with suspension side chain connecting bore on four journal stirrups (21a, 21b and 22a, 22b), the intersection on determined two the vertical planes of suspension side chain connecting bore axis of two journal stirrups of upside (21a, 21b), with the intersection on determined two the vertical planes of suspension side chain connecting bore axis of two journal stirrups of downside (22a, 22b), both overlap or are parallel.

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