CN109466263A - Double transverse arm independent front suspensions of equation motorcycle race and its control method of Line stiffness - Google Patents
Double transverse arm independent front suspensions of equation motorcycle race and its control method of Line stiffness Download PDFInfo
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- CN109466263A CN109466263A CN201811434237.5A CN201811434237A CN109466263A CN 109466263 A CN109466263 A CN 109466263A CN 201811434237 A CN201811434237 A CN 201811434237A CN 109466263 A CN109466263 A CN 109466263A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/32—Resilient suspensions characterised by arrangement, location or kind of springs having springs of different kinds
- B60G11/48—Resilient suspensions characterised by arrangement, location or kind of springs having springs of different kinds not including leaf springs
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram
- B60G3/20—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram all arms being rigid
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2300/00—Indexing codes relating to the type of vehicle
- B60G2300/27—Racing vehicles, e.g. F1
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/20—Stationary vehicle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
- B60G2800/22—Braking, stopping
Abstract
The invention discloses a kind of double transverse arm independent front suspensions of equation motorcycle race and its control methods of Line stiffness, including the anti-roll bar (1) being arranged on vehicle frame (25), the both ends of anti-roll bar (1) are connected by stock (3) with link block (4), front overhang push rod (20) are connected on link block (4), front overhang push rod (20) is connected with front column (19), front column (19) and front overhang wheel side (21), which cooperate, to be connected, and the connection of two independent front suspensions is realized with this.Three spring links (5) are set among two link blocks (4), third spring (6) with shock-absorbing spring (7) is set in the middle part of three spring links (5), and third spring (6) is fixed on vehicle frame (25).Present invention design has the interlocking frame of third spring to realize suspension Line stiffness and the relatively independent adjustment of roll stiffness, and when taking turns jump, vehicle body is more steady, can improve vehicle to control stability.
Description
Technical field
The present invention relates to the double transverse arm independent front suspensions and its line of a kind of double cross arm independent suspension, especially equation motorcycle race
The control method of rigidity.
Background technique
The speed of equation motorcycle race traveling is continuously improved with the development of vehicle manufacturing technology, the traveling behaviour of equation motorcycle race
Handing stability and driving safety are increasingly valued by people, while people require also in day the comfort of driving now
Benefit is promoted, and rigid axle suspension commercial vehicle has been unable to meet ride performance and control stability etc. requirement.
Double cross arm independent suspension is widely used to equation motorcycle race due to its preferable control stability and comfort
On, and there is also a small amount of interconnection double cross arm independent suspensions in the market, but two independences for interconnecting double cross arm independent suspension are outstanding
Frame passes through rigid connection, it is more difficult to realize the relatively independent adjustment of suspension Line stiffness and roll stiffness, and manipulated when taking turns and jumping
Stability is poor, affects to the comfortableness and security for driving equation motorcycle race.
Summary of the invention
The object of the present invention is to provide a kind of double transverse arm independent front suspensions of equation motorcycle race and its controls of Line stiffness
Method.The present invention can effectively improve the Line stiffness of front suspension when jump is taken turns in racing car in the same direction, to improve the operation stabilization of vehicle
Property.
Technical solution of the present invention: double transverse arm independent front suspensions of equation motorcycle race, including it is symmetricly set on vehicle frame front
The independent suspension assembly of two sides, the independent suspension assembly include the link block connecting with front overhang push rod, are connected on link block
There is independent spring, the other end of independent spring is connected with the preceding armed lever of vehicle frame；It is characterized by: the link block of two sides is respectively articulated with
There is a short axle, three spring links are hinged between two short axles, the middle part of three spring links is equipped with third spring, third spring
End be hinged with triangle lifting lug, triangle lifting lug is fixed on the preceding armed lever of vehicle frame；The third spring includes being arranged three
Piston base in the middle part of spring link, the front of piston base are equipped with piston front bar, and the end of piston front bar is equipped with rotary table, described
Piston base is equipped with first and limits platform edge, and rotary table is equipped with the second limitation platform edge, and the first limitation platform limits platform edge along with second
Between be equipped with shock-absorbing spring；A stock is respectively articulated in the middle part of the link block of two sides, the end of two stocks is hinged with one
Connecting plate is organized, anti-roll bar is equipped between two groups of connecting plates, anti-roll bar is equipped with anti-roll bar lifting lug, and anti-roll bar lifting lug is solid
It is scheduled on vehicle frame.
In double transverse arm independent front suspensions of equation motorcycle race above-mentioned, the independent suspension assembly includes being fixed on front overhang
Take turns the front column on side, the top of front column is equipped with upper separation lifting lug, is connected with triangle in front overhang through ball pin on upper separation lifting lug
Block, two base angles of corner block are managed after being respectively equipped with front overhang Top Crossbeam front tube and front overhang Top Crossbeam in front overhang, before front overhang Top Crossbeam
The end of pipe is connected through ball pin with vehicle frame, and the end of pipe is connected through ball pin with vehicle frame after front overhang Top Crossbeam；The front column
Lower part is equipped with lower separation lifting lug, is connected with corner block under front overhang through ball pin on lower separation lifting lug, two bottoms of corner block under front overhang
Angle is managed after being respectively equipped with front overhang lower cross arm front tube and front overhang lower cross arm, and the end of front overhang lower cross arm front tube is through ball pin and vehicle frame phase
Even, the end of pipe is connected through ball pin with vehicle frame after front overhang lower cross arm；Front overhang push rod is additionally provided under the front overhang on corner block to hang
Ear, front overhang push rod lifting lug are hinged with front overhang push rod.
In double transverse arm independent front suspensions of equation motorcycle race above-mentioned, the connecting plate is equipped with multiple through-holes, described
The end of stock is equipped with the adjusting bolt matched with through-hole.
In double transverse arm independent front suspensions of equation motorcycle race above-mentioned, three spring links are equipped with loss of weight through-hole.
In double transverse arm independent front suspensions of equation motorcycle race above-mentioned, a kind of control method of front suspension Line stiffness is provided,
I.e. by the offset frequency of the inclination gain and suspension of the stiffness change vehicle body of control third spring, in the inclination gain of vehicle body and suspension
It is biased minimum when calculate the Line stiffness of front suspension, optimal front suspension Line stiffness is obtained with this.
The control method of the Line stiffness of double transverse arm independent front suspensions of equation motorcycle race above-mentioned, it is characterised in that: described
The calculation formula of front suspension Line stiffness are as follows:
Wherein KFrFor front suspension Line stiffness, KFFor front overhang Line stiffness, MRrTransmission ratio when taking turns jump in the same direction for third spring, MR
For front overhang unilateral transmission ratio, KWFlFor front overhang revolver Line stiffness, KWFrFor front overhang right wheel Line stiffness, MfsmFor the spring charge material of front suspension
Amount, KfsFor third spring rate；
The KWFCalculation formula are as follows:
Wherein KWFFor the Line stiffness of front overhang unilateral side wheel, KTFor the rigidity of tire, KRFMultiply for front overhang (containing tire) unilateral side suitable
Rigidity；
The KRFCalculation formula are as follows:
KRF=4 π2fF 2msmrf (3)
Wherein KRFMultiply suitable rigidity, f for front overhang (containing tire) unilateral sideFFor the offset frequency of front suspension, msmrfFor front suspension right-hand wheel
The spring carried mass of tire；
It can be obtained by formula (1), (2) and (3):
Wherein fWFor the front overhang intrinsic frequency for not considering equipped with third spring and tire stiffness influence, mfsmFor front suspension
Spring carried mass.
Compared with prior art, two link blocks of the invention are separately connected a stock, and setting is anti-between two stocks
Roll bar connects front overhang push rod on link block, and front overhang push rod is connected with front column, front column and front overhang wheel side mutual cooperation company
It connects, the connection of two independent front suspensions is realized with this.Three spring links are set among two link blocks, in the middle part of three spring links
Third spring with shock-absorbing spring is set, and third spring is fixed on vehicle frame, on the one hand this interconnection architecture makes front suspension exist
Third spring in the movement of jump is taken turns in two sides in the same direction can occur to compress or stretch, so that the Line stiffness of front suspension is effectively improved, it is another
Aspect is little on the influence of two sides suspension in the jump of front suspension reversing wheel or roll motion, to improve the control stability of vehicle.
In addition, can also show that vehicle braking can be adjusted flexibly by changing the rigidity of third spring in the present invention by simulation analysis
The effect nodded, and other vehicle body state changes is kept to be basically unchanged, the influence to inclination is unobvious, while having little influence on wheel
The stress of tire.
Connecting plate of the invention is equipped with multiple through-holes, and the end of the stock is equipped with the adjusting spiral shell matched with through-hole
Bolt facilitates the position for adjusting link block, to realize the angular adjustment of third spring.
Three spring links of the invention are equipped with loss of weight through-hole, can reduce the own wt of three spring links, to vehicle body weight
Certain booster action is played in the requirement of amount.
Detailed description of the invention
Fig. 1 is structural schematic diagram of the invention；
Fig. 2 is the mounting structure schematic diagram for interconnecting double transverse arm independent front suspensions；
Fig. 3 is the partial enlargement structural representation of third spring；
Fig. 4 is the partial enlargement structural representation of independent suspension assembly；
Fig. 5 is relation schematic diagram of the wheel jump in the same direction to amount of spring compression；
Fig. 6 is that reversing wheel is jumped and spring-compressed displacement diagram；
Fig. 7 is that reversing wheel jumps third spring displacement slight change curve synoptic diagram；
Fig. 8 is that step turns to lower influence schematic diagram of the third spring rate to angle of heel of emulation；
Fig. 9 is the Braking nose dive angle change schematic diagram of third spring different-stiffness；
Figure 10 is to brake vehicle body under third spring different-stiffness to nod angle contrast's schematic diagram；
Figure 11 is the variation schematic diagram of vehicle roll angle in Fish-Hook emulation under third spring different-stiffness.
Appended drawing reference: the anti-roll bar of 1-, 2- connecting plate, 3- stock, 4- link block, tri- spring link of 5-, 6- third spring,
7- third spring, 8- piston base, 9- piston front bar, 10- triangle lifting lug, 11- short axle, 12- independent spring, 13- loss of weight through-hole,
14- through-hole, 15- adjusts bolt, manages after 16- front overhang Top Crossbeam, corner block in 17- front overhang, 18- front overhang Top Crossbeam front tube, before 19-
Column, 20- front overhang push rod, 21- front overhang wheel side, corner block under 22- front overhang, 23- front overhang lower cross arm front tube, 24- front overhang lower cross arm
After manage, 25- vehicle frame, 26- rotary table, 27- first limit platform edge, 28- second limit platform edge, the anti-roll bar lifting lug of 29-, 30- forearm
Bar separates lifting lug on 32-, lifting lug, 34- front overhang push rod lifting lug is separated under 33-.
Specific embodiment
Below with reference to embodiment, the invention will be further described, but is not intended as the foundation limited the present invention.
Embodiment 1: double transverse arm independent front suspensions of equation motorcycle race constitute as shown in Figs 1-4, including are symmetricly set on vehicle
The independent suspension assembly of 25 front part sides of frame, the independent suspension assembly include the link block 4 connecting with front overhang push rod 20, even
It connects and is connected with independent spring 12 on block 4, the other end of independent spring 12 is connected with the preceding armed lever 30 of vehicle frame 25.The link block of two sides
4 have been respectively articulated with a short axle 11, and three spring links 5 are hinged between two short axles 11, and three spring links 5 are logical equipped with loss of weight
Hole 13, can reduce the own wt of three spring links 5, and certain booster action is played in the requirement to car body weight.Three springs connect
The middle part of bar 5 is equipped with third spring 6, and the end of third spring 6 is hinged with triangle lifting lug 10, and triangle lifting lug 10 is fixed on vehicle frame 25
Preceding armed lever 30 on.The third spring 6 includes the piston base 8 that three spring links, 5 middle part is arranged in, piston base 8
Front is equipped with piston front bar 9, and the end of piston front bar 9 is equipped with rotary table 26, and the piston base 8 is equipped with the first limitation platform edge
27, rotary table 26 is equipped with the second limitation platform and limits platform between 28 equipped with shock-absorbing spring along 27 and second along 28, first limitation platforms
7.The middle part of two sides link block 4 has been respectively articulated with a stock 3, and the end of two stocks 3 is hinged with one group of connecting plate 2, and two
Anti- roll bar 1 is equipped between group connecting plate 2, anti-roll bar 1 is equipped with anti-roll bar lifting lug 29, and anti-roll bar lifting lug 29 passes through weldering
The mode connect is fixed on vehicle frame 25.The connecting plate 2 is equipped with multiple through-holes 14, and the end of the stock 3 is equipped with and leads to
The adjusting bolt 15 that hole 14 matches facilitates the position for adjusting link block 4, to realize the angular adjustment of third spring 7.
As shown in attached drawing 2 and attached drawing 4, the independent suspension assembly includes the front column being fixed on front overhang wheel side 21
19, the top of front column 19 is equipped with upper separation lifting lug 32, is connected with corner block 17 in front overhang through ball pin on upper separation lifting lug 32, preceding
Two base angles of outstanding upper corner block 17 are respectively equipped with pipe 16 after front overhang Top Crossbeam front tube 18 and front overhang Top Crossbeam, before front overhang Top Crossbeam
The end of pipe 18 is connected through ball pin with vehicle frame 25, and the end of pipe 16 is connected through ball pin with vehicle frame 25 after front overhang Top Crossbeam.Described
The lower part of front column 19 is equipped with lower separation lifting lug 33, is connected with corner block 22 under front overhang, front overhang through ball pin on lower separation lifting lug 33
Two base angles of lower corner block 22 are respectively equipped with pipe 24 after front overhang lower cross arm front tube 23 and front overhang lower cross arm, front overhang lower cross arm front tube
23 end is connected through ball pin with vehicle frame 25, and the end of pipe 24 is connected through ball pin with vehicle frame 25 after front overhang lower cross arm.Before described
It hangs and is additionally provided with front overhang push rod lifting lug 34 on corner block 22, front overhang push rod lifting lug 34 is hinged with front overhang push rod 20.
Using double transverse arm independent front suspensions of equation motorcycle race, the control of front suspension Line stiffness is carried out.Double transverse arms independently hang
The rigidity of third spring is to influence the principal element of suspension Line stiffness and roll angular rigidity in frame, and value size also determines vehicle
The offset frequency of the inclination gain and suspension of body.Stiffness change vehicle body by controlling third spring rolls the inclined of gain and suspension
Frequently, the Line stiffness that front suspension is calculated in the biased minimum for rolling gain and suspension of vehicle body, obtains optimal front suspension with this
Line stiffness.The determination of the front suspension Line stiffness multiplies suitable rigidity, the Line stiffness of front overhang unilateral side wheel and preceding including front overhang unilateral side
The determination of suspension roll angular rigidity, the calculation formula of the front suspension Line stiffness are as follows:
Wherein KFrFor front suspension Line stiffness, KFFor front overhang Line stiffness, MRrTransmission ratio when taking turns jump in the same direction for third spring, MR
For front overhang unilateral transmission ratio, KWFlFor front overhang revolver Line stiffness, KWFrFor front overhang right wheel Line stiffness, MfsmFor the spring charge material of front suspension
Amount, KfsFor third spring rate；
The KWFCalculation formula are as follows:
Wherein KWFFor the Line stiffness of front overhang unilateral side wheel, KTFor the rigidity of tire, KRFMultiply for front overhang (containing tire) unilateral side suitable
Rigidity；
The KRFAre as follows:
KRF=4 π2fF 2msmrf(N/m) (3)
Wherein KRFMultiply suitable rigidity, f for front overhang (containing tire) unilateral sideFFor the offset frequency of front suspension, fFValue generally 2.4~
Within the scope of 3.0Hz, racing car possible value under some specific operations is relatively higher, msmrfFor the spring charge material of tire on the right side of front suspension
Amount；
It can be obtained by formula (1), (2) and (3):
Wherein fWFor the front overhang intrinsic frequency for not considering equipped with third spring and tire stiffness influence, which relatively considers tire
The suspension offset frequency value of rigidity is relatively bigger than normal, mfsmFor the spring carried mass of front suspension.
The both ends of anti-roll bar of the invention are connected by stock with link block, and front overhang push rod, front overhang are connected on link block
Push rod is connected with front column, and front column and front overhang wheel side cooperate and connect, and the connection of two independent front suspensions is realized with this.Two
Three spring links are set among a link block, the third spring with third spring, third spring are set in the middle part of three spring links
Be fixed on vehicle frame, this interconnection architecture make front suspension third spring in the movement that jump is taken turns in the same direction in two sides can occur compression or
It stretches, and in the jump of front suspension reversing wheel or roll motion, it is little on the influence of two sides suspension, to improve vehicle to operation stabilization
Property.And the Braking nose dive angle of the more big then vehicle body of the rigidity of third spring is smaller in braking process, so suitably reducing the
The rigidity of three springs can effectively inhibit Braking nose dive, increase stability when vehicle body starting.
The present inventor has also carried out simulation analysis to the double transverse arm independent front suspensions of interconnection, to verify reliability of the invention.
Embodiment 2: the simulation analysis of wheel hop
The simulation parameter of double cross arm independent suspension is set as wheelspan 1550mm, spring carried mass 1212kg, height of center of mass
300mm, tire static diameter 228.6mm, tire stiffness 140N/mm, tire quality 3.5kg, the effective travel for taking turns jump are
50mm, the length of spring cushion are 200mm, and the length of third spring is 270mm, and it is as shown in Figure 5 to jump simulation result for wheel in the same direction.
It is respectively that the independent spring of double transverse arm independent front suspensions and the change in displacement of third spring compare in Fig. 5.It is independent
Spring and third spring its variable quantity when wheel in the same direction is jumped are almost equal, i.e., third spring can be with by rationally designing mechanical structure
Keep the transmission ratio of its transmission ratio and independent spring almost equal.Show that third spring can play increase Line stiffness when wheel in the same direction is jumped
Effect, and the distance that compression will be kept under similar situations such as rolling, i.e., inclination do not generated or only minor impact.
The emulation that reversing wheel is jumped is as shown in Figure 6.Double transverse arm independent front suspensions provide main toss about and go all out, elastic displacement
Variation is symmetric.Third spring also has the variation in displacement, and its variation is mutual in the center about wheel skip displacement
Symmetrically, the Influence of Displacement of rod piece, length value are maintained at 251mm when third spring is not rolled under the load of itself car weight
Near, the change curve of amplification as shown in fig. 7, but its variable quantity it is long compared to the original of third spring negligible.
Embodiment 3: the simulation analysis that step turns to
The rigidity (125lbs/in and 250lbs/in) different to third spring carries out step respectively and turns to emulation, emulation knot
Fruit curve is as shown in Figure 8.
Fig. 8 shows that step essentially coincides the change curve of vehicle roll angle after turning under third spring different-stiffness, table
Bright i.e. third spring is nearly free from influence to vehicle roll.
Embodiment 4: the simulation analysis of braking process
Simulation of Brake experiment is carried out to the vehicle equipped with third spring, since braking deceleration is largely by tyre mould
The influence of type, the tire model that tire selects FSAE official to provide, car weight are the racing car for participating in FSAE race, are set as 275kg (packet
Include driver), third spring rate is removed, parameter is that (two independent spring rigidity are 250lbs/ to default initial values on remaining vehicle
In), emulation experiment compares as shown in Figure 9.
Fig. 9 shows that it is variant to brake the angle initially nodded since car load is unchanged.Compare third to be more clear
Spring rate influences Braking nose dive bring, using the order of Align in ADAMS/CAR post-processing interface by 250lbs/in
Empirical curve starting point be moved to the origin of curve of 125lbs/in.Comparison shows the system of the more big then vehicle body of the rigidity of third spring
Dynamic angle of nodding is smaller.The specific gravity that the rigidity value of third spring accounts for three springs of front suspension is bigger, the stiffness variation of third spring
The variation of suspension Line stiffness is influenced it is also bigger, when being intended to 0 of rigidity of two independent springs of independent suspension under limiting case,
The Line stiffness of front suspension can be provided separately by third spring, but be easy to appear side during inclination if withouyt anti-roll bar
Turn over equal dangerous working conditions.
Change independent spring is 250lbs/in or 300lbs/in (third spring is 125lbs/in), front overhang third bullet
Spring is 125lbs/in or 250lbs/in (independent spring is 250lbs/in), and simulation result is as shown in Figure 10.Vehicle is braked
Simulation process analysis shows, the rigidity for only changing third spring, which can reach, changes all independent spring to inhibiting braking point
The effect of head, and other vehicle body state changes are basically unchanged.
Embodiment 5: the simulation analysis of control stability
Independent suspension independent spring is 125lbs/in or 250lbs/in (front overhang third spring is 125lbs/in), third
Spring is 125lbs/in or 250lbs/in (independent spring is 250lbs/in), carries out Fish-Hook emulation to it.Such as figure
Shown in 11, emulation shows to improve Braking nose dive, changes the rigidity of independent spring and imitates when braking can be improved to the inhibition nodded
Fruit, but body roll can also be produced bigger effect simultaneously, tire force also changes；And only change the rigidity of third spring
The effect for inhibiting to nod is played to Brake Energy, and the influence to inclination is unobvious, while having little influence on the stress of tire.
To sum up, third spring only serves the effect for increasing Line stiffness when wheel in the same direction is jumped, and in reversing wheel jump, inclination and step
The distance that compression will be kept when steering, i.e., do not generate inclination or only minor impact.And in braking process
The Braking nose dive angle of the more big then vehicle body of the rigidity of three springs is smaller, can effectively inhibit Braking nose dive, and the rigidity of third spring
The specific gravity that value accounts for three springs of front suspension is bigger, and the stiffness variation of third spring influences the variation of suspension Line stiffness also bigger.
Claims (5)
1. double transverse arm independent front suspensions of equation motorcycle race, the independent suspension including being symmetricly set on vehicle frame (25) front part sides is total
At the independent suspension assembly includes the link block (4) connecting with front overhang push rod (20), and link block is connected with independence on (4)
Spring (12), the other end of independent spring (12) are connected with the preceding armed lever (30) of vehicle frame (25)；It is characterized by: the connection of two sides
Block (4) has been respectively articulated with a short axle (11), is hinged with three spring links (5) between two short axles (11), three spring links (5)
Middle part be equipped with third spring (6), the end of third spring (6) is hinged with triangle lifting lug (10), and triangle lifting lug (10) is fixed on
On the preceding armed lever (30) of vehicle frame (25)；The third spring (6) includes the piston base being arranged in the middle part of three spring links (5)
(8), the front of piston base (8) is equipped with piston front bar (9), and the end of piston front bar (9) is equipped with rotary table (26), the piston bottom
Seat (8) is equipped with the first limitation platform along (27), and rotary table (26) is equipped with the second limitation platform along (28), the first limitation platform along (27) with
Second limitation platform is equipped with shock-absorbing spring (7) between (28)；A stock (3) has been respectively articulated in the middle part of two sides link block (4),
The end of two stocks (3) is hinged with one group of connecting plate (2), is equipped with anti-roll bar (1) between two groups of connecting plates (2), anti-side
Bar (1) is inclined equipped with anti-roll bar lifting lug (29), and anti-roll bar lifting lug (29) is fixed on vehicle frame (25).
2. double transverse arm independent front suspensions of equation motorcycle race according to claim 1, it is characterised in that: the independence is outstanding
Frame assembly includes the front column (19) being fixed on front overhang wheel side (21), and the top of front column (19) is equipped with upper separation lifting lug
(32), it is connected with corner block in front overhang (17) on upper separation lifting lug (32) through ball pin, two base angles of corner block (17) in front overhang
(16) are managed after being respectively equipped with front overhang Top Crossbeam front tube (18) and front overhang Top Crossbeam, the end of front overhang Top Crossbeam front tube (18) is through ball pin
It is connected with vehicle frame (25), the end that (16) are managed after front overhang Top Crossbeam is connected through ball pin with vehicle frame (25)；The front column (19)
Lower part be equipped with lower separation lifting lug (33), be connected with corner block under front overhang (22) through ball pin on lower separation lifting lug (33), under front overhang
(24) are managed after being respectively equipped with front overhang lower cross arm front tube (23) and front overhang lower cross arm in two base angles of corner block (22), front overhang lower cross arm
The end of front tube (23) is connected through ball pin with vehicle frame (25), and the end of (24) is managed after front overhang lower cross arm through ball pin and vehicle frame (25) phase
Even；Front overhang push rod lifting lug (34), front overhang push rod lifting lug (34) and front overhang push rod are additionally provided under the front overhang on corner block (22)
(20) it is hinged.
3. double transverse arm independent front suspensions of equation motorcycle race according to claim 1, it is characterised in that: the connecting plate
(2) multiple through-holes (14) are equipped with, the end of the stock (3) is equipped with the adjusting bolt (15) matched with through-hole (14).
4. double transverse arm independent front suspensions of equation motorcycle race according to claim 1, it is characterised in that: three springs
Connecting rod (5) is equipped with loss of weight through-hole (13).
5. the controlling party of the Line stiffness of double transverse arm independent front suspensions of equation motorcycle race according to claim 1-4
Method, it is characterised in that: the front suspension Line stiffness are as follows:
Wherein KFrFor front suspension Line stiffness, KFFor front overhang Line stiffness, MRrTransmission ratio when taking turns jump in the same direction for third spring, MR is front overhang
Unilateral transmission ratio, KWFlFor front overhang revolver Line stiffness, KWFrFor front overhang right wheel Line stiffness, MfsmFor the spring carried mass of front suspension, KfsFor
Third spring rate；
The KWFAre as follows:
Wherein KWFFor the Line stiffness of front overhang unilateral side wheel, KTFor the rigidity of tire, KRFMultiply suitable rigidity for front overhang (containing tire) unilateral side；
The KRFAre as follows:
KRF=4 π2fF 2msmrf (3)
Wherein KRFMultiply suitable rigidity, f for front overhang (containing tire) unilateral sideFFor the offset frequency of front suspension, msmrfFor the spring of tire on the right side of front suspension
Mounted mass；
It can be obtained by formula (1), (2) and (3):
Wherein fWFor the front overhang intrinsic frequency for not considering equipped with third spring and tire stiffness influence, mfsmFor the spring charge material of front suspension
Amount.
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| CN111516447A (en) * | 2020-05-07 | 2020-08-11 | 广东工业大学 | Shock absorber suspension of formula car and formula car |
| CN111923675A (en) * | 2020-09-10 | 2020-11-13 | 吉林大学 | Front independent suspension system of ultra-flat robot |
| CN112046227A (en) * | 2020-08-24 | 2020-12-08 | 湖北文理学院 | Formula suspension and cycle racing |
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2018
- 2018-11-28 CN CN201811434237.5A patent/CN109466263A/en not_active Withdrawn
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110525156A (en) * | 2019-07-17 | 2019-12-03 | 广东工业大学 | A kind of U-shaped balancing pole for university student's equation motorcycle race |
| CN110696578A (en) * | 2019-11-27 | 2020-01-17 | 浙江科技学院 | Variable-rigidity third damping suspension for equation racing vehicle |
| CN110696578B (en) * | 2019-11-27 | 2021-08-17 | 浙江科技学院 | Variable-rigidity third damping suspension for equation racing vehicle |
| CN111516447A (en) * | 2020-05-07 | 2020-08-11 | 广东工业大学 | Shock absorber suspension of formula car and formula car |
| CN112046227A (en) * | 2020-08-24 | 2020-12-08 | 湖北文理学院 | Formula suspension and cycle racing |
| CN111923675A (en) * | 2020-09-10 | 2020-11-13 | 吉林大学 | Front independent suspension system of ultra-flat robot |
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Application publication date: 20190315 |
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