CN204674327U - Cluster spring compensates suspension gear - Google Patents
Cluster spring compensates suspension gear Download PDFInfo
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- CN204674327U CN204674327U CN201520262359.6U CN201520262359U CN204674327U CN 204674327 U CN204674327 U CN 204674327U CN 201520262359 U CN201520262359 U CN 201520262359U CN 204674327 U CN204674327 U CN 204674327U
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Abstract
Cluster spring on vehicle compensates a suspension gear, and it comprises free spring, compensator spring, compensator spring pre-tightening apparatus, vibration isolation block, light damping shock absorber, guiding mechanism, described free spring, compensator spring, light damping shock absorber; This light damping shock absorber is arranged between vehicle frame and guiding mechanism, and described compensator spring is connected with vehicle frame or guiding mechanism, is provided with compensator spring pre-tightening apparatus in compensator spring upper end, and guiding mechanism is used for connecting wheel and vehicle body; Concrete feature be vehicle suspension gear on elastic element be made up of free spring and compensator spring, the load hung has between a compensating basin near the natural bow stroke hung, hang the load that bears in this compensating basin in change time, its stroke does not change or changes very little, when the load hung exceedes between compensating basin, the stroke hung just can change, and adopts the vehicle of this design, can improve the handling of vehicle and traveling comfort simultaneously.
Description
Technical field
The utility model relates to the suspension gear of vehicle, and by free spring, compensator spring, pre-tightening apparatus, vibration isolation block, light damping shock absorber, guiding mechanism forms.The utility model is designed with load compensation function near the natural bow stroke of vehicle, effectively can reduce the change of suspension device for vehicle N/R stroke, improves the traveling comfort of vehicle and handling.
Background technology
General vehicle, in normal driving process, all can be subject to the impact coming from road surface or track, if these impacts directly pass to car body or vehicle body by wheel and suspension gear, can damage car body and parts, and destroy the traveling comfort of occupant.Therefore general vehicle is all provided with elastomeric suspension to slow down the impact coming from wheel, but the elasticity of suspension itself can cause again the vibration of car body or vehicle body, because the change of impact or motion state of automobile can cause the change of hanging load, and cause the pitching of car body and the change of roll vibration and wheel attitude, thus cause the stability of vehicle and handling decline.
As everyone knows, the vehicle of current technical design, its suspension gear is made up of elastic element, guiding mechanism, shock absorber and Panhard rod.Elastic element is mainly used to bear and transmits vertical load, relaxes the impact to vehicle body because Uneven road causes.The most important thing is spring in elastic element, kind comprises steel spring, coil spring, torsion bar spring, hydro-pneumatic spring, air spring and rubber spring etc.Shock absorber is used for the vibration caused due to elastic system that decays, and the type of shock absorber has cylinder type damper, resistance adjustable shock absorber, inflatable vibration damper.Guiding mechanism is used for transmitting the force and moment between wheel and vehicle body, and keep wheel to beat by the relative vehicle body of certain movement track, usual guiding mechanism forms by controlling swing arm type rod member simultaneously.Kind has single lever-type or multi link formula.When steel spring is as elastic element, separately can not establish guiding mechanism, itself is double to play the guiding role.On some car and passenger vehicle, for preventing vehicle body from excessive lateral inclination occurring turning to etc. in situation, in suspension, add Panhard rod, object improves lateral stiffness, make automobile have understeer characteristics, improve manipulation stability and the riding comfort of automobile.
With the elastic element of the suspension of current technical design and damping element, there are two main performance requirements: driving comfort and manipulation stability.The vertical shake of the suspension major effect vehicle of common vehicle.Traditional suspension is nonadjustable, and in driving, the distortion of spring is depended in the change of bodywork height.Therefore be just naturally present in a kind of phenomenon, when vehicle zero load and load time, the ground Clearance of vehicle body is different.Especially some cars adopt soft coil spring, and the deformation stroke of load rear spring can be larger, and when causing automobile unloaded and load, the ground Clearance differs and has tens millimeters, and the crossing ability of automobile is affected.Simultaneously vehicle when different motoring conditions to being hung with different requirements.Generally need when travelling any suspension soft in the hope of comfort, need again any suspension hard in the hope of stability when sharply turning and braking, these two main performance requirements also exist conflict and contradiction.The passive suspension generally used, because have fixing suspension stiffness and damping coefficient, can not meet the requirement of travelling comfort and manipulation stability simultaneously.
In order to solve the contradiction between travelling comfort and manipulation stability, create electronically-controlled suspension technology, the control form of current known electronically-controlled suspension mainly contains two kinds, by the form of fluid control and the form that controlled by air pressure.The fluid control form of electronically-controlled suspension is relatively advanced form, and Active Suspensions just belongs to this class form, and it adopts a kind of active mode to suppress road surface to the impulsive force of vehicle body and body inclination power.The air pressure control form of electronically-controlled suspension is also called self adaptation and hangs, and it deals with the change on road surface by adjustment within the specific limits.No matter be that Active Suspensions or self adaptation hang, they have electronic control component (ECU), have ECU just must have sensor.Sensor is parts important on electronically-controlled suspension, once malfunctioning whole suspension work will mal.All these make the complex structure of existing electronically-controlled suspension system unavoidably, the defects such as technical requirements is high, cost intensive, and power consumption is large, limit this High Performance and are suspended on widespread use on vehicle.
The known patent the most close with the utility model is " use is combined with the spring of flexible backbone to improve the Vehicle wheel suspensions of stiffness curve " (CN97181615.8), the Vehicle wheel suspensions that this utility model relates to uses a coil spring keep with one and be connected flexible backbone, a part of spring is compressed at normal traveling-position, make it to remain on compressive state, to obtain two kinds of different stiffness curves, its point of transition is positioned near normal traveling-position; During compression, whole coil spring is compressed, and when loosening, only has the uncompressed part of spring to be relaxed, and therefore, suspending apparatus is asymmetric, and rigidity when loosening is greater than rigidity during compression.On the one hand, each skeleton comprises two connecting elements, all or part of the matching of an a connecting element and coil spring spring coil, another connecting element or match with all or part of of another spring coil of spring, or match with the housing of shock absorber, on the other hand, each skeleton comprises a longitudinal elements, the deformable when compressing of this longitudinal elements, indeformable when loosening, be connected with two connecting elements, at least two spring coils of skeleton restriction and compression coil spring.But this utility model is only limitted to the rigidity changing spring among a small circle, the rideability of vehicle still can be improved when not needing Panhard rod, but it is limited to add the change of device to its rigidity at same spring, do not relate to the damping content reducing shock absorber simultaneously, fundamentally can not improve manipulation and the comfort property of suspension gear.
Utility model content
Main purpose of the present utility model is to provide a kind of cluster spring and compensates suspension gear, when normal vehicle operation and in safe range in acceleration and deceleration or turning process, this suspension make vehicle to inclination, pitching, yaw, beat and the control of bodywork height all very effective, make to come from overbalance that the impact on ground or car body the produce actv. that can be draped to absorb, keep wheel to the adhesive ability on ground to greatest extent, to give full play to the driving brake action of wheel, the stability of vehicle when running at high speed and turn is improved greatly.In addition when the load carrying ability of vehicle changes, vehicle can keep certain bodywork height all the time, so the geometric relationship hung also can be guaranteed constant, thus the parastate making car body and road surface or orbit plane remain required, meet or exceed the effective utilization of active suspension general at present.
The realization of above-mentioned purpose is by realizing the elastic element of suspension i.e. the combination of spring and load compensation.The stroke hung when we are to balance static in the horizontal plane during vehicle load is natural bow, hangs born load for unloaded lotus G when being still in plane time unloaded with vehicle
0, hang born load during to be still in plane during vehicle load for G, the stroke during maximum compression of suspension is dynamic deflection.By the unitized design of different spring, make it near the natural bow hung, in the load certain limit that suspension is born during change, the stroke hung does not change or changes very little, the load range that the stroke hung does not change is called (sets minimum as A between compensating basin, be B to the maximum, A < G
0< G < B), the load of suspension is in compensating basin during interior change, and the stroke of suspension is constant or change is very little, and when the load of suspension exceedes between compensating basin, the stroke of suspension just can change.
The elastic element of suspension described in the utility model is combined by free spring and compensator spring, when the suspension travel of vehicle is longer than natural bow, elastic anchorage force is provided by free spring, when vehicle suspension travel quiet scratch change between dynamic deflection time, elastic anchorage force or compensator spring is jointly provided to provide elastic anchorage force separately by compensator spring and free spring, the main feature of this technology is exactly the restriction that the range of compensator spring is subject to preload piece, only in the natural bow hung to dynamic deflection operated within range.
Above method of designing can make the elastic element of suspension possess desirable stiffness characteristics for the vehicle that some load variations are less: near the natural bow hung, possess load automatic compensation function, on the one hand, when changing in the scope of hanging load between compensating basin, although there is the change increasing or reduce in the load hung, the compensator spring hung is under the effect of pre-tightening apparatus, length is constant, on the other hand, when hanging load exceedes the scope between this compensating basin, when being namely less than A, free its length change, compensator spring length is constant, when being greater than B, free spring and compensator spring length change simultaneously.That is the stroke hung in zero load to not changing during load or changing very little; At this moment because the predetermincd tension of compensator spring makes the elastic element of suspension be provided with the function of load auto-compensation when this trip, near the natural bow hung, the rigidity of the elastic element of whole suspension becomes very large, considerably beyond the rigidity of spring itself, vehicle is had good handling, suspension travel is when leaving natural bow simultaneously, free spring and compensator spring will recover original rigidity, still can there is corresponding change along with the change of load in the stroke hung, keep the driving comfort of vehicle.
General vehicle possesses four or more suspension gear, when the wheel that a suspension gear connects is subject to the impact coming from ground or track, this hangs the load be subject to and can exceed between the compensating basin of suspended load, the stroke hung can change, the load that this suspension gear acts on vehicle body also can change, and the junction of other suspension gear is transmitted to by vehicle body, now other suspension gears work between the compensating basin near natural bow, if suffered load variations is less than the load range between compensating basin, then the load of this change is compensated, the stroke of affected suspension does not change or changes very little, thus make whole vehicle body can keep motionless, if exceed the load range between compensating basin, the stroke of suspension gear can change, but because there is load compensation interval, the stroke of suspension gear can produce one and gets back to the trend of natural bow stroke and very quick return near natural bow, make the handling of vehicle also can return to optimum regime very soon.
Adopt the suspension of this design just to possess two effects simultaneously, first be good geometry deformation ability, because such elastic parts has less rigidity in its main stroke, although centre has very little section stiffness very large, within the parameter area that the traveling comfort that this scope can be made to be reduced to vehicle by design allows.When impact exceedes this scope, the distortion required for elastic element generation of suspension will be made, and this change of being out of shape the elastic anchorage force caused can be absorbed by other suspension being in high rigidity mode of operation, it is made to reduce to very little to the impact that car body produces.Next is that the elastic element hung has the trend automatically operated between high stiffness region, under the impact of this trend, the suspension most of the time is operated in high rigidity state, now because the effect of high rigidity, the inclination of car body, pitching and load change etc. all effectively can be absorbed by the suspension of high rigidity, even do not need horizontal and vertical stabilizer rod, also good balance can be kept, under common driving condition, vehicle there will not be obvious cornering roll, and brake is nodded and accelerated phenomenon of swinging back.These are that in current Suspension Technique, five-star technology is also difficult to realize, rely on the effect of compensator spring in elastic element to achieve comparatively ideal characteristic because hang simultaneously, decrease the vibration of car body, weaken the effect that in suspension, shock absorber keeps for body gesture, light damping shock absorber can be adopted, can effectively reduce costs, the cost for the structure reduction suspension that simplify shock absorber in suspension has the effect of crux.
The utility model is achieved in that
A kind of cluster spring compensates suspension gear, it is characterized in that, it includes free spring, compensator spring, compensator spring pre-tightening apparatus (2), light damping shock absorber (7) and guiding mechanism (5); Described free spring, compensator spring, light damping shock absorber are arranged between vehicle frame (1) and guiding mechanism (5), described compensator spring is connected with vehicle frame (1) or guiding mechanism (5), compensator spring pre-tightening apparatus (2) is installed in compensator spring one end, guiding mechanism (5) is used for connecting wheel and vehicle body, for free spring (6), compensator spring (3) and light damping shock absorber (7) provide location and installation.
Wherein, described free spring (6) upper end is connected with vehicle frame (1), lower end is connected with guiding mechanism (5), and described light damping shock absorber (7) upper end is connected with vehicle frame (1), lower end is connected with guiding mechanism (5); Described compensator spring (3) upper end is connected with vehicle frame (1) or lower end is fixedly connected with guiding mechanism (5), and at coupling end, compensator spring pre-tightening apparatus (2) being installed, this compensator spring (3) lower end or upper end are provided with vibration isolation block; This light damping shock absorber (7), free spring (6) and compensator spring (3) are formed and are installed in parallel between vehicle frame (1) and guiding mechanism (5).
Wherein, described free spring (6) lower end is connected with guiding mechanism (5), upper end is connected with light damping shock absorber (7) lower end, is connected with guide cylinder (11) in light damping shock absorber (7) outer wall lower end; Described compensator spring (3) lower end is connected with light damping shock absorber (7) upper end, this compensator spring (3) upper end is connected with vehicle frame (1), and at coupling end, compensator spring pre-tightening apparatus (2) being installed, this compensator spring (3), light damping shock absorber (7), free spring (6) are connected in turn to be formed between vehicle frame (1) and guiding mechanism (5) and are installed in series.In this installation form, also installation can be inverted.Described free spring (6) upper end is connected with vehicle frame (1), lower end is connected with light damping shock absorber (7) upper end, is connected with guide cylinder (11) in light damping shock absorber (7) outer wall upper end; Described compensator spring (3) upper end is connected with light damping shock absorber lower end, this compensator spring (3) lower end is connected with guiding mechanism (5), and at coupling end, compensator spring pre-tightening apparatus (2) being installed, this free spring (6), light damping shock absorber (7), compensator spring (3) are connected in turn to be formed between vehicle frame (1) and guiding mechanism (5) and are installed in series.
Wherein, described free spring (6) center lower end is connected with guiding mechanism (5), upper end, both sides is connected with vehicle frame (1), described compensator spring (3) upper end is connected with vehicle frame (1), this compensator spring (3) lower end is provided with vibration isolation block (4), and this vibration isolation block (4) and free spring (6) centering are arranged.
Wherein, when free spring (6) and compensator spring (3) are installed in parallel, the load that time unloaded with vehicle, suspension is born is for G
0, hanging born load during load factor is G, the predetermincd tension F > G-G of the compensator spring (3) that composition hangs
0, when free spring (6) is near the natural bow value of vehicle, to the elastic anchorage force f < G that vehicle provides
0.In order to increase the handling of vehicle, when designing, the predetermincd tension F>=1.1 (G-G of the spiral compensation spring that composition hangs
0), when the free spring of spiral is near the natural bow value of vehicle, to elastic anchorage force f≤0.9G that vehicle provides
0.If need handling very strong vehicle, very large multiple can be designed, such as racing car, can F>=2 (G-G
0), f≤0.5G
0
Wherein, when free spring (6) and compensator spring (3) are installed in series, the load that time unloaded with vehicle, suspension is born is for G
0hanging born load during load is G, the predetermincd tension F > G of the compensator spring (3) that composition hangs, when free spring (6) is near the natural bow value of vehicle, meets f < G to the elastic anchorage force that vehicle provides
0.
Wherein, the predetermincd tension F > 1.1 (G-G of the compensator spring (3) of composition suspension
0), when free spring (6) is near the natural bow value of vehicle, to the elastic anchorage force f < 0.9G that vehicle provides
0.This suspension is generally used on the very long vehicle of the suspension travel such as motor bike, is applied to racing car relatively less, can certainly go design according to the multiple of parallel connection.
Certainly in order to improve the traveling comfort of vehicle, also range size between compensating basin can be adjusted at any time according to the size of load and operating needs, specifically can carry out dynamic conditioning to realize to the predetermincd tension of compensator spring by control apparatus, common control apparatus has electronics automatically to regulate or the mode of manual regulation.
Wherein, the predetermincd tension F > 1.1G of the compensator spring (3) that composition hangs, when free spring (6) is near the natural bow value of vehicle, to the elastic anchorage force f < 0.9G that vehicle provides
0.
Wherein, the damping coefficient of described light damping shock absorber is less than 0.25 in extension stroke, and compression stroke is less than 0.15.Because the balance of vehicle body keeps with compensator spring, the vibration of vehicle body simultaneously alleviates, so adopt the less shock absorber of damping coefficient just can keep the rideability of vehicle.
The utility model beneficial effect is: by hanging combination and the compensating action of elastic element, achieve the performance requriements exceeding active suspension, be suitable for most highway and guideway vehicle, the passenger vehicle very little for load variations is especially applicable, not only reduce manufacturing cost, also improve handling and traveling comfort.
Accompanying drawing explanation
Fig. 1 is that suspension in the utility model embodiment 1 cluster spring when being in range compensates and hangs schematic diagram, and the load now hung is less than between compensating basin, and free spring is in elongation state, and compensator spring does not have load.
Fig. 2 is that suspension in the utility model embodiment 1 cluster spring when being in natural bow compensates and hangs schematic diagram, the load now hung is in compensation interval range, a part of load shared by free spring, compensator spring is shared a part of load but is less than predetermincd tension, now hangs balance quiescence when being in load.
Fig. 3 is that suspension in the utility model embodiment 1 cluster spring when being in dynamic deflection compensates and hangs schematic diagram, the load now hung is greater than between compensating basin, and free spring continues to be compressed, and the load that compensator spring is shared is greater than predetermincd tension, continue to be compressed, now hang and be in larger compressive state.
Fig. 4 is that suspension in the utility model embodiment 2 air spring when being in range compensates and hangs schematic diagram, and the load now hung is less than between compensating basin, and free spring is that steel spring is in relaxation state, and compensator spring is that air spring does not have load.
Fig. 5 is that suspension in the utility model embodiment 2 gas spring when being in natural bow compensates and hangs schematic diagram, the load now hung is in compensation interval range, free spring is that steel spring shares a part of load, compensator spring is that gas spring is shared a part of load but do not compressed, and now hangs balance quiescence when being in load.
Fig. 6 is that suspension in the utility model embodiment 2 gas spring when being in dynamic deflection compensates and hangs schematic diagram, and the load now hung is greater than between compensating basin, and steel spring continues to be compressed, and gas spring continues to be compressed, and now hangs and is in larger compressive state.
Fig. 7 is that suspension in the utility model embodiment 3 free spring-compensating when being in range hangs schematic diagram, and free spring and compensator spring are series design.The load now hung is less than between compensating basin, and free spring is in relaxation state, and compensator spring does not have load.
Fig. 8 is that suspension in the utility model embodiment 3 free spring-compensating when being in natural bow hangs schematic diagram, and free spring and compensator spring are series design.The load now hung is in compensation interval range, and free spring is all compressed, and compensator spring bears whole load, but except pretension, does not continue to be compressed, and now hangs balance quiescence when being in load.
Fig. 9 is that suspension in the utility model embodiment 3 free spring-compensating when being in dynamic deflection hangs schematic diagram, and free spring and compensator spring are series design.The load now hung is greater than between compensating basin, and free spring is in most compressed state, and compensator spring continues to be compressed, and now hangs and is in larger compressive state.
Figure 10 is that suspension in the utility model embodiment 4 free spring-compensating when being in range hangs schematic diagram, and free spring and compensator spring are series design.The load now hung is less than between compensating basin, and free spring is in relaxation state, and compensator spring does not have load.
Figure 11 is that suspension in the utility model embodiment 4 free spring-compensating when being in natural bow hangs schematic diagram, and free spring and compensator spring are series design.The load now hung is in compensation interval range, and free spring is all compressed, and compensator spring bears whole load, but except predetermincd tension, does not continue to be compressed, and now hangs balance quiescence when being in load.
Figure 12 is that suspension in the utility model embodiment 4 free spring-compensating when being in dynamic deflection hangs schematic diagram, and free spring and compensator spring are series design.The load now hung is greater than between compensating basin, and free spring is in most compressed state, and compensator spring continues to be compressed, and now hangs and is in larger compressive state.
Detailed description of the invention:
See Fig. 1, Fig. 2, Fig. 3, in embodiment 1, vehicle frame (1) in figure, compensator spring pre-tightening apparatus (2), compensator spring (3), vibration isolation block (4), guiding mechanism (5), free spring (6), light damping shock absorber (7), wheel (8).
Suspension described in the utility model comprises vehicle frame 1, compensator spring pre-tightening apparatus 2, compensator spring 3, vibration isolation block 4, guiding mechanism 5, free spring 6, light damping shock absorber 7, wheel 8.Its elastic element is formed by free spring 6 (free spring 6 is coil springs) and compensator spring 3 (compensator spring 3 is coil springs) parallel combination, when stationary vehicle or when being in state of equilibrium, wheel is born by free spring 6 and compensator spring 3 jointly to hanging the load produced, the load hung (to set between compensating basin minimum value as A between compensating basin, maxim is B, and hanging the load of bearing when vehicle is unloaded is G
0, hanging born load during load factor is G, then A < G
0< G < B, this numerical value is the minimum zone of design, general design all can exceed this scope) time, the length of free spring 6 and compensator spring 3 does not all change, only having vibration isolation block 4 that certain deformation can occur, only there is very little change in the stroke that is hung along with the change of load.
In this suspension, the predetermincd tension F > 1.1 (G-G of the compensator spring that composition hangs
0), the elastic anchorage force f < G that free spring provides vehicle
0.
The load hung is less than 0.9G
0time, the free spring 6 of suspension extends, and bears whole load; Compensator spring 3 length is constant, not share loads.
The load hung is more than 1.1 (G-G
0) time, the free spring 6 of suspension continues to be compressed, and bears a part of load; Compensator spring 3 is compressed, and shares all the other loads.
The main feature of this technology is exactly the restriction that the range of compensator spring 3 is subject to pre-tightening apparatus 2, only in the natural bow hung to dynamic deflection operated within range.
Near the natural bow hung, if the unloaded lotus hung is G
0, hanging born load lotus during load is G, and the predetermincd tension F of the bearing force f that the free spring 6 of suspension provides and compensator spring 3 needs to meet following relation simultaneously:
That is the bearing force that now free spring 6 provides is less than the static weight that suspension is born, bearing of the compensator spring 3 that some load is limited by predetermincd tension, when the load hung meets above-mentioned requirements, when the load hung changes in certain limit near its natural bow value, due to the compensating action of compensator spring 3 predetermincd tension, the length of free spring 6 and compensator spring 3 does not all change, even if the stroke hung changes, also be only that vibration isolation block is compressed occurred deformation, but deformation quantity is very little, it is very little that general effect is exactly the stroke change of hanging, in this load range, the rigidity hung is very high.When the change of the load hung has exceeded this scope, then will there is the change of corresponding stroke in two springs, can meet the driving requirements of vehicle completely.
By rational design, in the hanging load certain limit making vehicle during change, the stroke of suspension is constant or very little change only occurs, and this is the characteristic that needs most of vehicle hanging just.Such as when a wheel is subject to impacting, this hangs and is also impacted simultaneously, the change of its load also can produce a vibratory impulse to car body, this impacts and passes to other suspension by vehicle frame, but because other suspension is operated in compensating basin, if by impacting the change of the load brought in the compensating basin that other hangs, other stroke hung does not change or changes very little, and whole vehicle body still keeps the state of relative equilibrium; If same vehicle is because speed, direction and load-carrying change but when changing in scope between compensating basin, the compensator spring 3 that the change that hanging load occurs also can be draped compensates, the stroke hung still keeps required stabilized conditions, vehicle can keep good road-holding property and stability, does not affect the comfort property of vehicle simultaneously.
See Fig. 4, Fig. 5, Fig. 6, in embodiment 2, compensator spring (3), vibration isolation block (4), free spring (6), wheel (8).
In embodiment 2, what the elastic element of vehicle hanging of the present utility model was same comprises free spring 6 and compensator spring 3, and wherein compensator spring 3 is air spring, and free spring 6 is steel spring.
In the present embodiment, gas compensator spring 3 role is identical with the compensator spring 3 described in embodiment 1, and steel spring role is identical with the free spring 6 described in embodiment 1.There is unlike air spring itself characteristic of preloading spring, do not need to increase pre-tightening apparatus in addition, steel spring can play the effect that guiding connects simultaneously, the structure hung can adopt the design more simplified, very well, the vibration isolation block 4 of increase further can reduce noise to the anti-vibration performance of air spring, and steel spring itself has possessed certain damping of vibrations simultaneously, if during to vibration damping less demanding, the design cancelling shock absorber can be adopted.In this suspension, the predetermincd tension F > 1.1 (G-G of the air spring that composition hangs
0), the elastic anchorage force f < G that free spring provides vehicle
0.
See Fig. 7, Fig. 8, Fig. 9, in embodiment 3, free spring (6), light damping shock absorber (7), guide cylinder (11), compensator spring (3), wheel (8).
In embodiment 3, what the elastic element of vehicle hanging of the present utility model was same comprises free spring 6 and compensator spring 3, and wherein compensator spring 3 is coil spring, and free spring 6 is coil spring.
In the present embodiment, compensator spring 3 role is identical with the compensator spring 3 described in embodiment 1, and free spring 6 role is identical with the free spring 6 described in embodiment 1.Unlike in the present embodiment, compensator spring 3 and free spring 6 are connected in series, light damping shock absorber 7 is connected with the guide cylinder 11 of free spring 6, not only can play spring directional tagging, the stroke of all right restraint of liberty spring 6, the elastic anchorage force making it provide meets f < G
0, design simultaneously makes the predetermincd tension F > G of compensator spring.
Near the natural bow hung, if the unloaded lotus hung is G
0, hanging born load during load is G, and the predetermincd tension F of the bearing force f that the free spring 6 of suspension provides and compensator spring 3 has following relation:
In this suspension, for increasing the handling of vehicle, the predetermincd tension F > 1.1G of the compensator spring 3 of composition suspension usually, the elastic anchorage force f < 0.9G that free spring 6 pairs of vehicles provide
0.
See Figure 10, Figure 11, Figure 12, in embodiment 4, free spring (6), light damping shock absorber (7), guide cylinder (11), compensator spring (3), wheel (8).
In embodiment 4, what the elastic element of vehicle hanging of the present utility model was same comprises free spring 6 and compensator spring 3, and wherein compensator spring 3 is coil spring 3, and free spring 6 is coil spring 6.
In the present embodiment, compensator spring 3 role is identical with the compensator spring 3 described in embodiment 3, and free spring 6 role is identical with the free spring 6 described in embodiment 3.Unlike in the present embodiment, compensator spring 3 under, free spring 6 is upper, light damping shock absorber 7 is connected with the guide cylinder 11 of free spring 6, not only can play spring directional tagging, f < G can also be met by the elastic anchorage force that provides of restraint of liberty spring 6
0, design simultaneously makes the predetermincd tension F > G of compensator spring 3.
Concrete structure is, free spring 6 upper end is connected with vehicle frame 1, lower end is connected with light damping shock absorber 7 upper end, is connected with guide cylinder 11 in light damping shock absorber 7 outer wall upper end; Described compensator spring 3 upper end is connected with light damping shock absorber 7 lower end, this compensator spring 3 lower end is connected with guiding mechanism 5, and at coupling end, compensator spring pre-tightening apparatus 2 being installed, this free spring 6, light damping shock absorber 7, compensator spring 3 are connected in turn to be formed between vehicle frame 1 and guiding mechanism 5 and are installed in series.
Sum up and as above illustrate and embodiment, vehicle hanging method of designing described in the utility model and structure are different from former suspension device for vehicle, this suspension gear relies on the combination of hanging two or more elastic element and compensation to achieve the mutual auto-compensation characteristic of the multiple suspension of vehicle, for the road-holding property of satisfied suspension and traveling comfort require to provide new method of designing.
The casehistory that above embodiment is just carried out for principle of design of the present utility model, actual design and structure may have more change, and the scope such as between compensating basin may not only demand fulfillment A < G
0< G < B, also has B-A to exceed (G-G
0) more than 50% design, even may more than 1 times for special vehicle, also the size of detection load dynamic adjustments can be carried out by setting device to the size of B-A value in addition, can meet higher traveling comfort requires in a word, this patent passes through the design between compensating basin, the impact on vehicle body that one single suspension produces can be compensated by other suspension and be revised, finally can keep and reduce the vibration of vehicle body, road-holding property and traveling comfort can be improved simultaneously.This design and device all by realizing the pretension of compensator spring, for the design of automatic compensation function realizing hanging by spring pre-tightening and structure, all in this scope of patent protection.
Adopt the suspension of this design to have good geometry deformation ability on the one hand, possess the ability absorbed from road shocks, effectively reduce or avoid the vibration of vehicle body; On the other hand when being suspended on natural bow, automatic compensation function is possessed to the load hung, make vehicle when speed, direction and load-carrying change, effectively can reduce or avoid suspension travel excessive variation, actv. solves the contradiction of vehicle driving comfort and manipulation stability, has the result of use being equivalent to or exceeding electronically controlled Active Suspensions on general vehicle.
The above know-why being preferred embodiment of the present utility model and using; for a person skilled in the art; when not deviating from spirit and scope of the present utility model; any based on apparent changes such as the equivalent transformation on technical solutions of the utility model basis, simple replacements, all belong within the utility model protection domain.
Claims (10)
1. cluster spring compensates a suspension gear, it is characterized in that, it includes free spring, compensator spring, compensator spring pre-tightening apparatus (2), light damping shock absorber (7) and guiding mechanism (5); Described free spring, compensator spring, light damping shock absorber are arranged between vehicle frame (1) and guiding mechanism (5), described compensator spring is connected with vehicle frame (1) or guiding mechanism (5), compensator spring pre-tightening apparatus (2) is installed in compensator spring one end, guiding mechanism (5) is used for connecting wheel and vehicle body, for free spring (6), compensator spring (3) and light damping shock absorber (7) provide location and installation.
2. cluster spring as claimed in claim 1 compensates suspension gear, it is characterized in that, described free spring (6) upper end is connected with vehicle frame (1), lower end is connected with guiding mechanism (5), and described light damping shock absorber (7) upper end is connected with vehicle frame (1), lower end is connected with guiding mechanism (5); Described compensator spring (3) upper end is connected with vehicle frame (1) or lower end is fixedly connected with guiding mechanism (5), and at coupling end, compensator spring pre-tightening apparatus (2) being installed, this compensator spring (3) lower end or upper end are provided with vibration isolation block; This light damping shock absorber (7), free spring (6) and compensator spring (3) are formed and are installed in parallel between vehicle frame (1) and guiding mechanism (5).
3. cluster spring as claimed in claim 1 compensates suspension gear, it is characterized in that, described free spring (6) lower end is connected with guiding mechanism (5), upper end is connected with light damping shock absorber (7) lower end, is connected with guide cylinder (11) in light damping shock absorber (7) outer wall lower end; Described compensator spring (3) lower end is connected with light damping shock absorber (7) upper end, this compensator spring (3) upper end is connected with vehicle frame (1), and at coupling end, compensator spring pre-tightening apparatus (2) being installed, this compensator spring (3), light damping shock absorber (7), free spring (6) are connected in turn to be formed between vehicle frame (1) and guiding mechanism (5) and are installed in series.
4. cluster spring as claimed in claim 1 compensates suspension gear, it is characterized in that, described free spring (6) upper end is connected with vehicle frame (1), lower end is connected with light damping shock absorber (7) upper end, is connected with guide cylinder (11) in light damping shock absorber (7) outer wall upper end; Described compensator spring (3) upper end is connected with light damping shock absorber lower end, this compensator spring (3) lower end is connected with guiding mechanism (5), and at coupling end, compensator spring pre-tightening apparatus (2) being installed, this free spring (6), light damping shock absorber (7), compensator spring (3) are connected in turn to be formed between vehicle frame (1) and guiding mechanism (5) and are installed in series.
5. cluster spring as claimed in claim 1 compensates suspension gear, it is characterized in that, described free spring (6) center lower end is connected with guiding mechanism (5), upper end, both sides is connected with vehicle frame (1), described compensator spring (3) upper end is connected with vehicle frame (1), this compensator spring (3) lower end is provided with vibration isolation block (4), and this vibration isolation block (4) and free spring (6) centering are arranged.
6. cluster spring as claimed in claim 2 compensates suspension gear, it is characterized in that, when free spring (6) and compensator spring (3) are installed in parallel, the load that time unloaded with vehicle, suspension is born is for G
0, hanging born load during load is G, the predetermincd tension F > G-G of the compensator spring (3) that composition hangs
0, when free spring (6) is near the natural bow value of vehicle, to the elastic anchorage force f < G that vehicle provides
0.
7. the cluster spring as described in claim 3 or 4 compensates suspension gear, it is characterized in that, when free spring (6) and compensator spring (3) are installed in series, the load that time unloaded with vehicle, suspension is born is for G
0hanging born load during load is G, the predetermincd tension F > G of the compensator spring (3) that composition hangs, when free spring (6) is near the natural bow value of vehicle, meets f < G to the elastic anchorage force that vehicle provides
0.
8. cluster spring as claimed in claim 6 compensates suspension gear, it is characterized in that, the predetermincd tension F > 1.1 (G-G of the compensator spring (3) that composition hangs
0), when free spring (6) is near the natural bow value of vehicle, to the elastic anchorage force f < 0.9G that vehicle provides
0.
9. cluster spring as claimed in claim 7 compensates suspension gear, it is characterized in that, the predetermincd tension F > 1.1G of the compensator spring (3) that composition hangs, when free spring (6) is near the natural bow value of vehicle, to the elastic anchorage force f < 0.9G that vehicle provides
0.
10. as described in claim 5 or 6, cluster spring compensates suspension gear, and it is characterized in that, the damping coefficient of described light damping shock absorber is less than 0.25 in extension stroke, and compression stroke is less than 0.15.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520262359.6U CN204674327U (en) | 2015-04-27 | 2015-04-27 | Cluster spring compensates suspension gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520262359.6U CN204674327U (en) | 2015-04-27 | 2015-04-27 | Cluster spring compensates suspension gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204674327U true CN204674327U (en) | 2015-09-30 |
Family
ID=54174044
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520262359.6U Withdrawn - After Issue CN204674327U (en) | 2015-04-27 | 2015-04-27 | Cluster spring compensates suspension gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204674327U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104773045A (en) * | 2015-04-27 | 2015-07-15 | 席玉林 | Combined spring compensation suspending device |
| CN112721558A (en) * | 2021-01-22 | 2021-04-30 | 重汽(重庆)轻型汽车有限公司 | Load-carrying self-adaptive suspension stiffness design method and suspension elastic assembly |
| CN113905858A (en) * | 2019-05-27 | 2022-01-07 | 索尼集团公司 | Robot device, control method for robot device, and load compensation device |
-
2015
- 2015-04-27 CN CN201520262359.6U patent/CN204674327U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104773045A (en) * | 2015-04-27 | 2015-07-15 | 席玉林 | Combined spring compensation suspending device |
| WO2016173390A1 (en) * | 2015-04-27 | 2016-11-03 | 席玉林 | Combined spring compensation suspension device |
| CN113905858A (en) * | 2019-05-27 | 2022-01-07 | 索尼集团公司 | Robot device, control method for robot device, and load compensation device |
| CN113905858B (en) * | 2019-05-27 | 2024-04-26 | 索尼集团公司 | Robot device, control method for robot device, and load compensation device |
| CN112721558A (en) * | 2021-01-22 | 2021-04-30 | 重汽(重庆)轻型汽车有限公司 | Load-carrying self-adaptive suspension stiffness design method and suspension elastic assembly |
| CN112721558B (en) * | 2021-01-22 | 2024-01-19 | 重汽(重庆)轻型汽车有限公司 | Load self-adaptive suspension stiffness design method and suspension elastic assembly |
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| C14 | Grant of patent or utility model | ||
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| AV01 | Patent right actively abandoned |
Granted publication date: 20150930 Effective date of abandoning: 20171114 |