CN104989758A - Spiral spring for vehicle suspension, independent suspension assembly and vehicle - Google Patents
Spiral spring for vehicle suspension, independent suspension assembly and vehicle Download PDFInfo
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- CN104989758A CN104989758A CN201510417072.0A CN201510417072A CN104989758A CN 104989758 A CN104989758 A CN 104989758A CN 201510417072 A CN201510417072 A CN 201510417072A CN 104989758 A CN104989758 A CN 104989758A
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- helical spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/06—Wound springs with turns lying in cylindrical surfaces
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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
- B60G11/14—Resilient suspensions characterised by arrangement, location or kind of springs having helical, spiral or coil springs only
- B60G11/16—Resilient suspensions characterised by arrangement, location or kind of springs having helical, spiral or coil springs only characterised by means specially adapted for attaching the spring to axle or sprung part of the vehicle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F1/00—Springs
- F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
- F16F1/04—Wound springs
- F16F1/12—Attachments or mountings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Springs (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention provides a spiral spring for a vehicle suspension. The spiral spring has continuous pitch identical sections and pitch transition sections; the pitch transition sections are configured to be gradually pressed when the sprung mass is changed from no load to full load; and in the section from no load to full load, the sprung mass and the working lap number of the spiral spring satisfy the following relation as shown in the description, wherein G is the material elastic modulus of the spiral spring, f is the vehicle offset frequency, d is the spring wire diameter of the spiral spring, D is the spring medium diameter of the spiral spring, m is the sprung mass, n is the working lap number, and f is the constant. The invention further provides an independent suspension assembly adopting the spiral spring and a vehicle adopting the spiral spring. The spiral spring for the vehicle suspension, the independent suspension assembly and the vehicle have the advantages of good smoothness and long service life.
Description
Technical field
The present invention relates to automobile chassis field, be specifically related to for the helical spring of automotive suspension, independent suspension assembly and automobile.
Background technique
Automotive suspension is the vitals ensureing riding comfort.Simultaneously, automotive suspension is as the force-transmitting member connected between vehicle body (or vehicle frame) and axletree (or wheel), it is again the vitals ensureing ride safety of automobile, its Main Function transmits to act on wheel and moment, and cushion the impact of road surface to vehicle, ensure the smoothness that vehicle travels and control stability.
Independent suspension is under two, the left and right wheel on automobile axletree is individually installed on vehicle body (or vehicle frame), vehicle bridge adopts disconnecting type, middle one section is fixed on vehicle body (or vehicle frame), independent suspension two sidecar wheel is independent of each other when being hit, and because this sprung mass is comparatively light, buffering and damping capacity very by force, riding comfort is good.Indices is all better than dependent formula suspension, but independent suspension structure is complicated.
Independent suspension comprises macpherson suspension, double cross arm independent suspension, multi-connecting-rod separated suspension, independent suspension by trailing arms etc., and these independent suspensions or spring are contained on vibration damper, or spring and vibration damper are contained on diverse location.
The independent suspension of prior art as shown in Figure 1, vibration damper 5) be all that lower end is fixed on lower swing arm 8) on, upper end is directly fixed on vehicle body or vehicle frame 1) on, general lower end is with running shaft, and upper end is directly fixed on vehicle body by rubber pad.General independent suspension is also provided with rear stabilizer 2), helical spring 3), top link 4), knuckle 6), buffer stopper 7) etc., helical spring 3) with vibration damper 5) connecting rod be synchronized with the movement and helical spring 3) lateral force can be transmitted to connecting rod when being subject to lateral force.
At automobile in movement process, lower swing arm 8) relatively vehicle body have relative movement in left and right and fore-and-aft direction, vibration damper 5) upper end rubber pad by the relative movement of self-deformation Absorbable rod avoid interfere, but rubber pad hardness ratio is larger, absorbing simultaneously very large to the damper linking member generation lateral force of relative movement, these lateral forces not only increase the frictional force of damper piston and cylinder body, the temperature of vibration damper is raised very soon, the rubber parts of vibration damper inside and working of plastics are aging very soon, cause damper leakage, the failure phenomenons such as damping force decay, greatly affect the life-span of vibration damper.
The commercial car independent suspension larger to axle load, because relative movement is comparatively large, defective shock absorber problem is especially outstanding.Simultaneously fixed buffer 5) rubber pad of upper end is at lower swing arm 8) and vehicle body between constantly compressed in relative movement frequently and also can be lost efficacy very soon.
In addition, the excessive smoothness also affecting motor racing of lateral force that is subject to of vibration damper.
Helical spring of the prior art is widely used in passenger car and commercial car, and in passenger car suspension, the elastic element of about about 80% is all helical spring.Helical spring diameter, wire diameter, the number of turns, highly, pitch etc. directly affects helical spring performance.
Offset frequency passes judgment on an extremely important parameter of car load smoothness, refer to the vibration frequency of certain suspension of vehicle, the one-sided vibration frequency of certain suspension in particular, the sprung weight m that offset frequency f is made up of a part of quality of the body quality on spring, quality of loads and suspension self and spring rate determine, are specifically tried to achieve by following formula:
Wherein, f is automobile offset frequency, and m is helical spring sprung weight, and k is helical spring rigidity.
Therefore sprung weight m, helical spring rigidity k directly affect the offset frequency of vehicle, only have the passenger when offset frequency is stablized just can feel the stability that vehicle travels, and along with the load of vehicle and the change of passenger quantity, sprung weight also changes thereupon, cause offset frequency to change, the riding comfort of passenger is also changed thereupon.
Meanwhile, vehicle because of the load of left and right, front and back different, and when spring rate is constant, just produce the offset frequency difference of left and right, front and back, namely the vibration frequency of left and right or front and back is different, and the natural frequency of these different vibration frequencies and each component of vehicle influences each other, and affects riding comfort.
In sum, helical spring and the mounting structure in automotive suspension thereof all have impact for the lateral force of vibration damper, automobile offset frequency.
The helical spring 3 of prior art suspension frame structure), general rigidity is constant, even change also just the rigidity of two states is different, as different in rigidity that is unloaded and that be fully loaded with, make the offset frequency of sky, fully loaded two states close, and can not make to be suspended in any state offset frequency and remain unchanged.Exist in prior art by change helical spring 3) pitch change rigidity, helical spring 3 when the vehicle is fully laden) the little part of pitch pressed also, the helical spring number of effective coils reduces, rigidity increases, vehicle is fully loaded with there is comparatively large rigidity, although the helical spring of different pitch has two different rigidity, make sky, the offset frequency of fully loaded 2 is basically identical, but at sky, between fully loaded, the car that such as instinct takes 5 people only has two people to take, the position difference that two people sit, make suspension left, right avertence is frequently different, or front and back offset frequency is different, cause smoothness unstable.And in prior art, the counteracting of lateral force is generally concentrated on for helical spring 3) improvement of shape own, but when road traveling condition is changeable, helical spring 3) specific shape just offsets for certain lateral force, and the reduction effect of lateral force is unsatisfactory.
Summary of the invention
The object of the invention is to 1, this body structure of helical spring is improved thus ensure unloaded constant to automobile offset frequency in fully loaded change procedure, improve travelling comfort; 2, make vibration damper avoid being subject to the effect of lateral force, increase the life and reliability of vibration damper; 3, the life-span of the rubber pad of fixed buffer is increased; 4, the convenience of the installation and removal of vibration damper and spring is increased; 5, smoothness and the travelling comfort of suspension is improved; 6, suspension bulk life time is improved.
For achieving the above object, The embodiment provides following technological scheme:
On the one hand, provide a kind of helical spring for automotive suspension, described helical spring has continuous print pitch same section and pitch transition section, described pitch transition section is constructed to when sprung weight is from zero load to fully loaded change, described pitch transition section is pressed also gradually, in zero load to fully loaded interval, between sprung weight and the described helical spring number of effective coils, meet following relation:
Wherein, G is the Young's modulus of described helical spring material, f is automobile offset frequency, d is described helical spring spring wire diameter, D is described helical spring mean diameter of coil, m is sprung weight, n is the number of effective coils, and f is constant.
Preferably, described helical spring two ends are parallel spring doubling-up.
On the other hand, provide a kind of independent suspension assembly, comprise spring support, lower swing arm, support, helical spring, vibration damper, rubber pad, top link, vehicle body and knuckle as above, described spring support comprises dish portion, lays respectively at protuberance and a pair ear of both sides, described dish portion, described protuberance be upper end have diapire, lower ending opening barrel-shaped, and described diapire has the first through hole, described ear is spaced with the opening of dodging described protuberance, described ear has the second coaxial through hole, and the axis of described first through hole is vertical with the axial space of described second through hole, described top link, one end of described lower swing arm is connected by ball pin with described knuckle respectively, described lower swing arm is provided with installation base, rotate around X-axis direction to enable described spring support with described spring support rotatable engagement between the ear that described installation base stretches into a described spring support, described support is fixedly connected with described vehicle body, described support is flute profile, spring support described in another is upside down positioned at the groove of described support and rotates around X-axis direction to enable described spring support with described support rotatable engagement, the bottom bar of described vibration damper is successively through first described rubber pad, the first through hole on described protuberance, fastening after second described rubber pad, the upper end bar of described vibration damper is successively through the 3rd described rubber pad, the first through hole on the described protuberance of inverted described spring support, fastening after 4th described rubber pad, second described rubber pad and the 4th described rubber pad are positioned at the inside of described protuberance, described helical spring is between two described spring supports and be enclosed within described protuberance.
Preferably, above-mentioned independent suspension assembly also comprises vehicle bridge, and the other end of described lower swing arm is rotatably connected with described vehicle bridge.
Preferably, the other end of described top link is rotatably connected with described support.
Preferably, described support has the first side wall, the second sidewall and the 3rd sidewall between described the first side wall and described second sidewall, described second sidewall has third through-hole, the position of the other end corresponding described third through-hole between described the first side wall with described 3rd sidewall of described top link.
Preferably, inverted described spring support between described second sidewall and described 3rd sidewall, and described ear and described second sidewall, is provided with spacer ring between described 3rd sidewall.
Preferably, above-mentioned independent suspension assembly also comprises buffer stopper, is positioned at directly over described top link in the groove that described buffer stopper is arranged on described support.
Again on the other hand, provide a kind of automobile, described automobile adopts helical spring as above, or adopts independent suspension assembly as above.
In an embodiment of the present invention, helical spring pitch transition section is constructed to when sprung weight is from zero load to fully loaded change, pitch transition section is pressed also gradually, the helical spring number of effective coils is made to reduce gradually to ensure that automobile offset frequency is constant, but not only consider that the offset frequency of unloaded and fully loaded two ultimate state points is constant, that is, still so that the automobile of 5 people can be taken, after adopting the helical spring of the present embodiment, take at nobody, 1 people takes until when 5 people take, automobile offset frequency is equal all the time, no matter how personnel amount and position change, each helical spring change makes the front and back of automobile, left and right offset frequency is equal all the time, therefore smoothness and driving comfortability are improved.
In an embodiment of the present invention, because spring support has the second through hole, therefore after mounting, spring support is not fixedly mounted on vibration damper or lower swing arm, but can rotate around X-axis direction, like this, when side is stressed, spring support just can pivot, helical spring is made also to be subject to same lateral force in this side, this power is passed on another spring support, another spring support is also pivoted, and the toroidal surface that spring support contacts with helical spring is parallel to each other always, ensure that helical spring can not create lateral force to vibration damper, and the upper/lower terminal of vibration damper is separately fixed on two spring supports, the rotating center of two spring supports is parallel to each other, therefore when the relative vehicle body of suspension or the motion of vehicle frame left and right directions, vibration damper also can not be subject to lateral force, therefore vibration damper can not be subject to the effect of any lateral force in whole movement process, improves the life-span of vibration damper and the smoothness of vehicle traveling.And the barrel-shaped protuberance of the one end open of spring support, a rubber pad can be contained in the inside of protuberance, another rubber pad is in outside, and rubber pad rotates along with the rotation of spring support, and non-immediate is fixed on vehicle body or vehicle frame, the friction of therefore bearing is less, longer service life.
Further, the boss of the ear of spring support towards mutual away from direction extend, boss can either play the effect strengthened intensity, improve the wear resistance of spring support rotating shaft place, does not hinder again rubber pad to enter protuberance inside, thus makes dismounting convenient.
Accompanying drawing explanation
Fig. 1 is the plan view of the independent suspension assembly of prior art;
Fig. 2 is the stereogram of the spring support of embodiments of the invention;
Fig. 3 is the stereogram of the independent suspension assembly of embodiments of the invention;
Fig. 4 is the plan view of the independent suspension assembly of embodiments of the invention;
Fig. 5 is the right side view of the independent suspension assembly of embodiments of the invention;
Fig. 6 is the sectional view along the A-A line in Fig. 4;
Fig. 7 is the sectional view along the B-B line in Fig. 5;
Fig. 8 is the sectional view along the C-C line in Fig. 5;
Fig. 9 is the partial enlarged drawing of the I part in Fig. 8;
Figure 10 is the plan view in a free state of the helical spring for automotive suspension of embodiments of the invention;
Figure 11 is the helical spring plan view for automotive suspension of embodiments of the invention;
Figure 12 is the plan view in the unloaded state of the helical spring for automotive suspension of embodiments of the invention;
Figure 13 is the plan view in a fully loaded state of the helical spring for automotive suspension of embodiments of the invention;
Figure 14 be the helical spring for automotive suspension of embodiments of the invention in zero load to the relation schematic diagram of fully loaded interval sprung weight and the number of effective coils.
1), vehicle frame description of symbols in figure:; 2), rear stabilizer; 3), helical spring; 4), top link; 5), vibration damper; 6), knuckle; 7), buffer stopper; 8), lower swing arm; 1, lower swing arm; 101, installation base; 2, spring support; 201, dish portion; 202, protuberance; 203, ear; 204, the first through hole; 205, boss; 206, the second through hole; 207, opening; 208, diapire; 3, support; 301, support diapire; 302, the first side wall; 303, the second sidewall; 304, the 3rd sidewall; 305, third through-hole; 4, helical spring; 401, spring doubling-up; 402, pitch same section; 403, pitch transition section; 5, vibration damper; 501, bottom bar; 502, upper end bar; 6, buffer stopper; 7, top link; 8, live axle; 9, knuckle; 10, spring support; 11, the first bolt; 12, the second bolt; 13, spacer ring; 14, the first rotating shaft; 1401, annular groove; 15, the second rotating shaft; 16, first rubber pad; 17, second rubber pad; 18, the 3rd rubber pad; 19, the 4th rubber pad; 20, clamp.
Embodiment
In ensuing description, X-direction refers to the fore-and-aft direction of automobile; Y-direction refers to the width direction of automobile, is also referred to as side direction; Z-direction refers to the short transverse of automobile.
With reference to figure 2, the spring support 2 for automotive suspension in the present embodiment comprises dish portion 201, is positioned at the protuberance 202 of upside and a pair ear 203 of downside in diagram mid-game portion 201.Wherein, protuberance 202 for upper end have diapire 208, lower ending opening barrel-shaped, its opening 207 is more shown clearly in figure 6.The diapire 208 of protuberance 202 has the first through hole 204.Ear 203 is spaced with the opening 207 of dodging protuberance 202, and ear 203 has the second coaxial through hole 206, and the axis B spatial vertical of the axis A of the first through hole 204 and the second through hole 206, namely axis A is vertical with axis B and crossing or non-intersect.Each ear 203 all has boss 205, two boss 205 towards mutual away from direction extend, the second through hole 206 is opened on boss 205.
Composition graphs 3 to Fig. 8, the independent suspension assembly in the present embodiment have employed two spring supports, and one of them is labeled as 2, and another is labeled as 10, although have employed different reference characters, spring support 2 have employed identical structure with spring support 10.In figure 6, relative to spring support 2, spring support 10 is inverted.The independent suspension assembly of the present embodiment also comprises lower swing arm 1, support 3, helical spring 4, vibration damper 5, rubber pad, damping block 6, top link 7, vehicle body, knuckle 9 etc.Lower swing arm 1 one end is connected by ball pin with knuckle 9, the other end with the vehicle bridge of live axle 8 or non-driven vehicle bridge or vehicle body or support 3 be installed be rotatably connected by the first rotating shaft 14.One end of top link 7 is also connected by ball pin with knuckle 9, and the other end is rotatably connected with support 3 by the second rotating shaft 15.
More high-visible from Fig. 5, Fig. 6 and Fig. 7, lower swing arm 1 is provided with installation base 101, installation base 101 stretches between the ear 203 of spring support 2, second bolt 12 is through tightening nut after the second through hole 206 and installation base 101, make installation base 101 and spring support 2 rotatable engagement, the direction of insertion of the second bolt 12 is X-axis direction, and therefore spring support 2 can rotate around X-axis direction.Certainly, those skilled in the art also can realize spring support 2 and the rotatable engagement of installation base 101 to ship and resell on another market etc., should be regarded as equivalent replacement at this.Support 3 is fixedly connected with vehicle body (not shown).As seen from Figure 7, support 3 forms flute profile by support diapire 301, the first side wall 302, second sidewall 303, and also has the 3rd sidewall 304 in groove folded between the first side wall 302 and the second sidewall 303.Spring support 10 is upside down positioned at the groove of support 3, first bolt 11 is through fastening nut after the second through hole 206 of the second sidewall 303 of support 3, the ear 203 of spring support 10 and the 3rd sidewall 304, make spring support 10 and support 3 rotatable engagement, and spring support 10 also can rotate around X-axis direction.Similarly, those skilled in the art also can realize the rotatable engagement of inverted spring support 10 and support 3 in the mode such as to ship and resell on another market.Inverted spring support 10 between the second sidewall 303 and the 3rd sidewall 304, and between the ear 203 of spring support 10 and the second sidewall 303, be provided with spacer ring 13 between ear 203 and the 3rd sidewall 304, to improve wear resistance.
From Fig. 6 and Fig. 7, in the bottom bar 501 of vibration damper 5 for being fixed on a bar on the housing of vibration damper 5, second rubber pad 17 is penetrated bottom bar 501 through after the first through hole 204 on the protuberance 201 of first rubber pad 16, spring support 2 at opening 207 place by this bottom bar 501 successively, then with fastening nuts, thus it is inner the second rubber pad 17 to be remained on protuberance 202.The upper end bar 502 of vibration damper 5 can be a part for damper piston connecting rod, this upper end bar 502 is successively through after the first through hole 204 on the protuberance 202 of the 3rd rubber pad 18, inverted spring support 10, the 4th rubber pad 19 is penetrated at opening 207 place, then with fastening nuts, the 4th rubber pad 19 is made to be positioned at the inside of protuberance 202.Helical spring 4 is between spring support 2 and spring support 10 and be enclosed within protuberance 202, directly be not connected with vibration damper 5 because helical spring 4 is resisted against in dish portion 201, therefore from loading angle, helical spring 4 is in parallel with vibration damper 5, but not series connection of the prior art.
Composition graphs 8 and Fig. 9, the first rotating shaft 14 is through lower swing arm 1 and vehicle bridge, and first rotating shaft 14 one end has annular groove 1401, and clamp 20 is fastened by bolts on lower swing arm 1 after inserting annular groove.
Composition graphs 3 and Fig. 8, second sidewall 303 has third through-hole 305, the position of the other end corresponding third through-hole 305 between the first side wall 302 with the 3rd sidewall 304 of top link 7, like this, stretch into instrument from third through-hole 305, just can dismantle the second rotating shaft 15 easily.
As seen from Figure 7, be positioned at directly over top link 7 in the groove that buffer stopper 6 is arranged on support 3, thus buffer stopper 6 top link 7 of conflicting provides vibration damping when top link 7 swings excessive.
Automobile is after completing above-mentioned spring support 2 and the installation of whole independent suspension assembly, spring support 2 and spring support 10 are not fixedly mounted on support 3 or lower swing arm 1, but can rotate around X-axis direction, like this, in driving procedure, during automotive suspension motion, top link 7 and lower swing arm 1 are owing to being fixed on support 3 by bolt or rotating shaft, therefore relative frame does not have relative movement in the X direction, and vibration damper 5 is not subject to lateral force at the fore-and-aft direction of automobile, and the left and right directions on the width direction of automobile, helical spring 4 upper, lower two end faces are resisted against in dish portion 201 abreast, when side is stressed, spring support 2 and inverted spring support 10 just can rotate around X-axis, spring support swings in Y-Z plane in other words, helical spring 4 is made also to be subject to same lateral force in this side, this power is passed on another spring support 10, another spring support 10 is also rotated around X-axis, and spring support 2, the toroidal surface that spring support 10 contacts with helical spring 4 is parallel to each other always, ensure that helical spring 4 can not produce lateral force to vibration damper 5, and the upper/lower terminal of vibration damper 5 is separately fixed on two spring supports 2 and inverted spring support 10, the rotating center of two spring supports is parallel to each other, therefore, when the relative vehicle body of independent suspension assembly or the motion of vehicle frame left and right directions, vibration damper 5 also can not be subject to lateral force.Therefore vibration damper 5 can not be subject to the effect of any lateral force in whole movement process, improves the life-span of vibration damper and the smoothness of vehicle traveling.At the upper/lower terminal of vibration damper 5, the barrel-shaped protuberance 202 of the one end open of spring support 2 or spring support 10, rubber pad can be contained in the inside of protuberance 202, another rubber pad is in outside, and rubber pad along with spring support 2 and spring support 10 rotation and rotate, and non-immediate is fixed on vehicle body or vehicle frame, the friction of therefore bearing is less, longer service life.And the boss 205 of spring support 2 can either play the effect strengthened intensity, improve the wear resistance of rotating shaft place of spring support 2, do not hinder again rubber pad to enter protuberance inside, thus make dismounting convenient.
Figure 10 to Figure 13 illustrate in further detail structure and the deformation process of helical spring 4.
In conjunction with Figure 10 and Figure 11, helical spring 4 is generally be rolled at material heating mould after flaying machine processing, and the two ends of helical spring 4 are parallel spring doubling-up 401, and spring doubling-up 401 is nonelastic, formed with forging or grinding, remaining part is effective elasticity part.Be installed to after on independent suspension assembly, spring doubling-up 401 is fitted with the dish portion 201 in Fig. 2, plays installation fixation.With the dotted line C in diagram for boundary, helical spring 4 has continuous print pitch same section 402 and pitch transition section 403.
Any vehicle suspension all needs the stroke necessarily moved up and down, and stroke is the most fundamental of suspension.The effective elasticity part of helical spring 4 must ensure the stroke of suspension, stroke be divided into slip a line journey and under to slip a line journey, same pitch section 402 not only ensure independent suspension for vehicle assembly maximum on to slip a line journey, and ensure that stress is no more than the allowable stress of spring material when maximum compression stroke, journey of slipping a line simultaneously ensure suspension together with pitch transition section 403 under.
Pitch transition section 403 is being fully loaded with the number of effective coils between zero load, namely still keep elasticity not by the pressure number of turns also, change along with sprung weight change: when sprung weight increases, the number of effective coils reduces, offset frequency is constant, otherwise when sprung weight reduces, the number of effective coils increases, the offset frequency of vehicle suspension is also constant, ensures riding comfort and the control stability of vehicle.
The mentality of designing of the helical spring 4 in the present embodiment is as follows:
The rigidity k of helical spring 4 is tried to achieve by following formula (1):
Wherein, G is the Young's modulus of the material of structure helical spring 4, and the mean diameter of coil that the spring wire diameter that d is helical spring 4, D are helical spring 4, n is the number of effective coils, C=D/d.For selected material, G and d is constant, and from formula, mean diameter of coil D is larger, and rigidity is less, and number of effective coils n is more, and rigidity is less, and wire diameter d is larger, and rigidity is also larger.
Automobile offset frequency passes judgment on an extremely important parameter of car load smoothness, refer to the vibration frequency of certain suspension of vehicle, the one-sided vibration frequency of certain suspension in particular, the sprung weight m that offset frequency f is made up of a part of quality of the body quality on spring, quality of loads and suspension self and rigidity k determine, are specifically tried to achieve by following formula (2):
Therefore the rigidity k of sprung weight m and helical spring 4 directly affects the offset frequency of vehicle, only have the passenger when offset frequency is stablized just can feel the stability that vehicle travels, and along with the load of vehicle and the change of passenger quantity, sprung weight also changes thereupon, cause offset frequency to change, the riding comfort of passenger is also changed thereupon.
Meanwhile, vehicle because of the load of left and right, front and back different, and when rigidity k is constant, just produce the offset frequency difference of left and right, front and back, namely the vibration frequency of left and right or front and back is different, and the natural frequency of these different vibration frequencies and each component of vehicle influences each other, and affects riding comfort.
After determining automobile offset frequency f, following formula (3) can be obtained from formula (2):
k＝4π
2f
2m
(3)
Formula (3) is substituted in formula (1), the relation (4) of sprung weight and active spring coils can be obtained:
Wherein, for the helical spring 4 be shaped, elastic modulus G, spring wire diameter d and mean diameter of coil D are known, and automobile offset frequency f is set to constant, have so just drawn the function relation of sprung weight m and number of effective coils n, have made plotted curve, as shown in figure 14.After knowing the unloaded sprung weight m1 and fully loaded sprung weight m2 of vehicle, according to formula (4), just can determine the number of effective coils n1 that identical offset frequency is corresponding and n2 respectively.
When designing suspension travel, when zero load, envoy is in pressure and state apart from transition section 403 lowest point, as shown in figure 12, all presses also at full load pitch transition section 403, as shown in figure 13, so just ensures that vehicle is in unloaded and load change and offset frequency is constant between being fully loaded with.
Ensure on slip a line journey and under slip a line journey prerequisite under, determine that helical spring 4 is empty, the pitch of full load, determine the pitch of free state again, so in the fabrication process completing the coiling of pitch transition section 403 of helical spring 4 with mould, meet the requirement of formula (4) when installing to back pitch transition section 403 on automobile.
That is, pitch transition section 403 is constructed to when sprung weight m is from unloaded m1 to fully loaded m2 change, and pitch transition section 403 is pressed also gradually, number of effective coils n is reduced gradually, is decreased to n2 from n1, to ensure that automobile offset frequency f is constant; Otherwise when sprung weight m makes from fully loaded m2 to unloaded m1 change, pitch transition section removes pressure also gradually, makes number of effective coils n become large gradually, increases to n1 from n2, to ensure that automobile offset frequency f is constant.
Due to interval to being fully loaded with in zero load, all the time relation (4) is met between sprung weight m and described helical spring number of effective coils n, therefore the structure of this helical spring 4 ensure that automobile offset frequency f is equal all the time, suspension offset frequency does not change, and suspension left and right offset frequency is identical, keeps good riding comfort.
Use the independent suspension assembly of the helical spring 4 of pitch gradual change, the inclination amount of automobile is little, at uneven road surface, when vehicle body floats, there is not the problem causing the disappearance of the earth-grasping force of wheel because stroke is not enough.Improving the control stability of vehicle simultaneously, improve the Security of vehicle.
Although the present invention is described in detail according to above-described embodiment; but protection scope of the present invention is not defined to above-described embodiment; and only by the restriction of claim; those of ordinary skill in the art can carry out equivalent modifications or equivalent replacement to above-described embodiment easily, but do not leave protection scope of the present invention.
Claims (9)
1. the helical spring for automotive suspension, it is characterized in that, described helical spring has continuous print pitch same section and pitch transition section, described pitch transition section is constructed to when sprung weight is from zero load to fully loaded change, described pitch transition section is pressed also gradually, in zero load to fully loaded interval, between sprung weight and the described helical spring number of effective coils, meet following relation:
Wherein, G is the Young's modulus of described helical spring material, f is automobile offset frequency, d is described helical spring spring wire diameter, D is described helical spring mean diameter of coil, m is sprung weight, n is the number of effective coils, and f is constant.
2. helical spring according to claim 1, is characterized in that, described helical spring two ends are parallel spring doubling-up.
3. an independent suspension assembly, is characterized in that, comprises spring support, lower swing arm, support, helical spring, vibration damper, rubber pad, top link, vehicle body and knuckle as claimed in claim 1 or 2, described spring support comprises dish portion, lays respectively at protuberance and a pair ear of both sides, described dish portion, described protuberance be upper end have diapire, lower ending opening barrel-shaped, and described diapire has the first through hole, described ear is spaced with the opening of dodging described protuberance, described ear has the second coaxial through hole, and the axis of described first through hole is vertical with the axial space of described second through hole, described top link, one end of described lower swing arm is connected by ball pin with described knuckle respectively, described lower swing arm is provided with installation base, rotate around X-axis direction to enable described spring support with described spring support rotatable engagement between the ear that described installation base stretches into a described spring support, described support is fixedly connected with described vehicle body, described support is flute profile, spring support described in another is upside down positioned at the groove of described support and rotates around X-axis direction to enable described spring support with described support rotatable engagement, the bottom bar of described vibration damper is successively through first described rubber pad, the first through hole on described protuberance, fastening after second described rubber pad, the upper end bar of described vibration damper is successively through the 3rd described rubber pad, the first through hole on the described protuberance of inverted described spring support, fastening after 4th described rubber pad, second described rubber pad and the 4th described rubber pad are positioned at the inside of described protuberance, described helical spring is between two described spring supports and be enclosed within described protuberance.
4. independent suspension assembly according to claim 3, is characterized in that, also comprise vehicle bridge, and the other end of described lower swing arm is rotatably connected with described vehicle bridge.
5. independent suspension assembly according to claim 3, is characterized in that, the other end of described top link is rotatably connected with described support.
6. independent suspension assembly according to claim 5, it is characterized in that, described support has the first side wall, the second sidewall and the 3rd sidewall between described the first side wall and described second sidewall, described second sidewall has third through-hole, the position of the other end corresponding described third through-hole between described the first side wall with described 3rd sidewall of described top link.
7. independent suspension assembly according to claim 6, is characterized in that, inverted described spring support between described second sidewall and described 3rd sidewall, and described ear and described second sidewall, is provided with spacer ring between described 3rd sidewall.
8. independent suspension assembly according to claim 3, is characterized in that, also comprise buffer stopper, is positioned at directly over described top link in the groove that described buffer stopper is arranged on described support.
9. an automobile, is characterized in that, described automobile adopts helical spring as claimed in claim 1 or 2, or adopts the independent suspension assembly as described in any one in claim 3 to 8.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510417072.0A CN104989758B (en) | 2015-07-14 | 2015-07-14 | Helical spring, independent suspension assembly and automobile for automotive suspension |
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| CN201510417072.0A CN104989758B (en) | 2015-07-14 | 2015-07-14 | Helical spring, independent suspension assembly and automobile for automotive suspension |
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| CN104989758A true CN104989758A (en) | 2015-10-21 |
| CN104989758B CN104989758B (en) | 2016-10-05 |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107323200A (en) * | 2017-07-06 | 2017-11-07 | 郑海 | A kind of suspension for electric vehicle |
| CN109073019A (en) * | 2016-04-13 | 2018-12-21 | 新确有限公司 | Helical spring |
| CN111877098A (en) * | 2017-01-30 | 2020-11-03 | 哈姆股份公司 | Road roller |
| CN112498523A (en) * | 2020-11-16 | 2021-03-16 | 东风柳州汽车有限公司 | Vehicle assembling method and device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN204852112U (en) * | 2015-07-14 | 2015-12-09 | 安徽江淮汽车股份有限公司 | A coil spring , independent suspension assembly and car for automotive suspension |
-
2015
- 2015-07-14 CN CN201510417072.0A patent/CN104989758B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN204852112U (en) * | 2015-07-14 | 2015-12-09 | 安徽江淮汽车股份有限公司 | A coil spring , independent suspension assembly and car for automotive suspension |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109073019A (en) * | 2016-04-13 | 2018-12-21 | 新确有限公司 | Helical spring |
| CN111877098A (en) * | 2017-01-30 | 2020-11-03 | 哈姆股份公司 | Road roller |
| CN111877098B (en) * | 2017-01-30 | 2022-05-31 | 哈姆股份公司 | Road roller |
| CN107323200A (en) * | 2017-07-06 | 2017-11-07 | 郑海 | A kind of suspension for electric vehicle |
| CN107323200B (en) * | 2017-07-06 | 2018-11-06 | 嘉兴尚云自动化设备有限公司 | A kind of suspension for electric vehicle |
| CN112498523A (en) * | 2020-11-16 | 2021-03-16 | 东风柳州汽车有限公司 | Vehicle assembling method and device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104989758B (en) | 2016-10-05 |
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Address after: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669 Patentee after: Anhui Jianghuai Automobile Group Limited by Share Ltd Address before: 230601 Anhui Province, Hefei City Industrial Park, the Peach Blossom Road No. 669 Patentee before: Anhui Jianghuai Automotive Co., Ltd. |