CN106143034B - A kind of passive type stiffness variable trailing link and the air suspension for installing the trailing link - Google Patents
A kind of passive type stiffness variable trailing link and the air suspension for installing the trailing link Download PDFInfo
- Publication number
- CN106143034B CN106143034B CN201610698261.4A CN201610698261A CN106143034B CN 106143034 B CN106143034 B CN 106143034B CN 201610698261 A CN201610698261 A CN 201610698261A CN 106143034 B CN106143034 B CN 106143034B
- Authority
- CN
- China
- Prior art keywords
- working chamber
- trailing link
- piston
- vehicle frame
- rod
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G7/00—Pivoted suspension arms; Accessories thereof
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
- B60G15/08—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having fluid spring
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/152—Pneumatic spring
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The present invention provides a kind of passive type stiffness variable trailing link and installs the air suspension of the trailing link, and trailing link includes front and rear hanging ring, front and rear spring, working chamber, supporting rod, front and rear piston, piston rod, rubber sleeve, connecting rod and fluid；Air suspension includes double leval jib guiding mechanism, damper, air spring, connecting plate and equalizer；The double leval jib guiding mechanism includes two trailing links and V shape pole；Suddenly accelerating under anxious decelerating mode, trailing link rigidity value becomes larger and is equivalent to a rigid rod, so as to protect air spring from longitudinal force, improves the stability of automobile；Under other driving cycles, trailing link overall stiffness becomes smaller, and fluid flows through intermediate elongated pipeline can generate larger damping force, improves the ride comfort of running car；Realize taking into account for stability of automobile and ride comfort under different operating modes；In addition, by the rigidity of trailing link damping action can be reconciled, further improve the characteristic of double leval jib guiding mechanism.
Description
Technical field
The invention belongs to air suspension of automobile guiding mechanism research fields, and in particular to one kind is used for air suspension Guiding machine
The passive type stiffness variable trailing link of structure and the air suspension for installing the trailing link.
Background technology
With the increasingly raising that people require car comfort and ride comfort, air suspension is increasingly by the weight of people
Depending on air suspension is relatively low with rigidity, and rigidity can change with the load change of vehicle, and under unloaded or fully loaded, suspension is intrinsic
Frequency is held essentially constant, and therefore, compared with traditional suspension, air suspension can further improve automobile ride so that multiply
Sit comfort more preferably.
Air suspension can realize that rigidity is adjustable and better ride comfort as a result of air spring, but by
Vertical load can only be born in air spring, it is impossible to bear longitudinal force and cross force, therefore one of main function of guiding mechanism
The power and torque for being subject to and transmitting other than vertical force.
There are many forms for guiding mechanism, and including leaf spring, double leval jib, A shape framves etc., the optimization of guiding mechanism is main at present
It is the form from guiding mechanism, arrangement etc. is set out, and trailing link mainly from material, intensity etc. is optimized and is set
Meter, but these design and optimizations not can solve the contradiction between automobile ride and stability.Suddenly slow down with
Under anxious accelerating mode, automobile needs better stability and protects air spring not by longitudinal force, therefore traditional longitudinal thrust
Bar can protect air spring and improve anti-" nodding " or " facing upward head " property by transmitting longitudinal loading, but in other operating modes
Under, under at the uniform velocity travelling, longitudinal force very little suffered by air spring, therefore automobile ride becomes main problem, due to traditional
Trailing link rigidity is immutable, therefore vibration can be transmitted to vehicle frame and vehicle body by trailing link caused by Uneven road,
So as to cause automobile ride bad.Additionally while in traditional design trailing link both ends can be played equipped with rubber bushing it is limited
Cushioning effect, but as the increase of number of shocks, the easy fatigue failure of rubber bushing even come off, lead to automobile ride
Decline.
Invention content
It is vertical the purpose of the present invention is providing a kind of passive type stiffness variable trailing link regarding to the issue above and installing this
To the air suspension of distance rod, take into account and the requirement of regularity and stability, the present invention are set trailing link under different operating modes
It is adjustable to be calculated as rigidity, while also there is damping action, to the vibration for the road surface transmission that decays, so as to improve automobile ride.
The technical scheme is that：A kind of passive type stiffness variable trailing link, including preceding spring, secondary piston, oil
Liquid, working chamber, rubber sleeve, connecting rod, rear piston, rear spring and piston rod；
The both ends of the working chamber are respectively cylindrical preceding working chamber and rear working chamber, and centre is diameter than preceding working chamber
The small cylindrical intermediate conduit with rear working chamber, preceding working chamber and rear working chamber are connected respectively by conical cavity and intermediate conduit both ends
It is logical；
The shape of the connecting rod is identical with working chamber, and the both ends of connecting rod are respectively cylinder, and centre is diameter than circle
The small cylindrical bar of cylinder, the cylinder at both ends connect respectively by the both ends transition of conical section and cylindrical bar；The connecting rod
In working chamber and the both ends of connecting rod are located at preceding working chamber and rear working chamber respectively, cylindrical bar be located at intermediate conduit it is interior,
And it can move left and right；
The side of the secondary piston and rear piston is fixedly connected respectively with the both ends of connecting rod and secondary piston and rear piston divide
Not with preceding working chamber and rear working chamber clearance fit；
The preceding spring one end is connect with preceding working chamber bottom, the opposite side connection of the other end and secondary piston；The piston
One end of bar is fixed as one with rear piston, the bottom of working chamber after the other end stretches out；It is described after spring pocket on the piston rod and
One end is connect with rear working chamber bottom, and the other end is connect with the opposite side of rear piston；Work between the secondary piston and rear piston
Make injecting oil liquid in chamber.
In said program, the conical cavity of the preceding working chamber and rear working chamber fills respectively close to the both ends inner wall of intermediate conduit
Rubber sleeve.
In said program, hanging ring and supporting rod before further including；The preceding hanging ring bottom end is welded as a whole with supporting rod one end,
Preceding hanging ring is connected by screw bolts with vehicle frame or vehicle bridge, and the supporting rod other end is welded and fixed with preceding working chamber.
In said program, rear hanging ring is further included；Hanging ring bottom end and one end of piston rod are welded as a whole after described, rear hanging ring
It is connected by screw bolts with vehicle bridge or vehicle frame.
A kind of air suspension for being equipped with the passive type stiffness variable trailing link, including double leval jib guiding mechanism,
Damper, air spring, connecting plate and equalizer；
The double leval jib guiding mechanism includes two trailing links and two V shape poles；
The connecting plate lower end and one end of trailing link connect, and upper end is mounted on vehicle frame, and the V shape pole is installed on
Between main reducing gear and vehicle frame and angled end is fixed on the shell of main reducing gear, in addition both ends are separately fixed on vehicle frame；
The equalizer is mounted in vehicle bridge, and air spring and damper are mounted between equalizer and vehicle frame.
The beneficial effects of the invention are as follows：
1. under anxious acceleration or anxious decelerating mode, stability of automobile is matter of utmost importance, due to middle brace rod both sides tapered portion
Divide and contacted with the rubber sleeve in work cavity wall, trailing link rigidity value is caused to become larger and is equivalent to a rigid rod, Ke Yigeng
Longitudinal force and most of load transfer are undertaken well, so that trailing link can protect air spring from longitudinal force,
It improves automobile and resists " nodding " and " facing upward head " performance, improve stability.
2. under other operating modes, automobile ride is matter of utmost importance, since connecting rod is not socketed with the rubber in work cavity wall
It touches, and with front and rear reciprocating motion of the pistons, therefore trailing link rigidity value is lower, the impact that vehicle frame is transmitted to by vehicle bridge subtracts
It is small, the vibration between vehicle bridge and vehicle frame can be buffered additionally by the reciprocating motion of piston, and during the fluid in working chamber flows through
Between slender pipeline can generate larger damping force again, the damping characteristic of fluid can decay vibrational energy, so longitudinal direction at this time
Distance rod can be impacted with extensional vibration of the snubber caused by the factors such as Uneven road between vehicle frame and vehicle bridge, realize vapour
The raising of vehicle riding comfort and ride comfort.
3. can take into account automobile under different operating modes the invention enables trailing link to stress stability and ride comfort, solve
Certainly traditional trailing link rigidity is non-adjustable, only focuses on protecting air spring from longitudinal force and stability of automobile, but damages one
As under operating mode the problem of the ride comfort and comfort of automobile.
4. the present invention, under different operating modes, stiffness tuning response is rapid, and belongs to passive adjusting, without consuming additional energy
Amount, simple in structure, practicality easy for installation.
5. the air suspension of the present invention for installing the trailing link includes four companies that trailing link is formed with V shape pole
Bar guiding mechanism, the present invention are primarily subjected to longitudinal force and can carry out stiffness tuning according to different operating modes, and V shape pole is primarily subjected to
Cross force and a part of longitudinal force can reconcile damping action by the rigidity of the present invention, further improve double leval jib Guiding machine
The characteristic of structure so that double leval jib guiding mechanism both suddenly can accelerate to protect air spring under anxious decelerating mode, improve automobile
Stability, and Low rigidity can be declined in other operating modes, improve automobile ride.
Description of the drawings
Fig. 1 is the trailing link structure diagram of an embodiment of the present invention；
Fig. 2 is trailing link working state schematic representation under the anxious decelerating mode of an embodiment of the present invention；
Fig. 3 is trailing link working state schematic representation under the anxious accelerating mode of an embodiment of the present invention；
Fig. 4 is trailing link working state schematic representation under other operating modes of an embodiment of the present invention；
Fig. 5 is the air suspension left view using the present invention of an embodiment of the present invention；
Fig. 6 is the air suspension vertical view using the present invention of an embodiment of the present invention.
In figure, 1, preceding hanging ring；2nd, supporting rod；3rd, preceding spring；4th, secondary piston；5th, fluid；6th, working chamber；601st, preceding work
Chamber；602nd, rear working chamber；603rd, intermediate conduit, 7, rubber sleeve；8th, connecting rod；9th, rear piston；10th, rear spring；11st, piston rod；
12nd, rear hanging ring；13rd, damper；14th, V shape pole；15th, vehicle frame；16th, air spring；17th, equalizer；18th, vehicle bridge；19th, wheel；
20th, trailing link；21st, connecting plate；22nd, main reducing gear.
Specific embodiment
The present invention is described in further detail with reference to the accompanying drawings and detailed description, but protection scope of the present invention
It is not limited to this.
Fig. 1 show a kind of embodiment of passive type stiffness variable trailing link of the present invention, the passive type
Stiffness variable trailing link, including preceding hanging ring 1, supporting rod 2, preceding spring 3, secondary piston 4, fluid 5, working chamber 6, rubber sleeve 7,
Connecting rod 8, rear piston 9, rear spring 10, piston rod 11 and rear hanging ring 12.
The both ends of the working chamber 6 are respectively the preceding working chamber 601 of cylinder and rear working chamber 602, and centre is diameter ratio
Preceding working chamber 601 and the small cylindrical intermediate conduit 603 of rear working chamber 602, preceding working chamber 601 and rear working chamber 602 lead to respectively
Conical cavity is crossed to connect with 603 both ends of intermediate conduit；The conical cavity of the preceding working chamber 601 and rear working chamber 602 is close to intermediate tube
The both ends inner wall in road 603 is respectively provided with rubber sleeve 7.
The shape of the connecting rod 8 is identical with working chamber 6, and the both ends of connecting rod 8 are respectively cylinder, and centre is diameter ratio
The small cylindrical bar of cylinder, the cylinder at both ends connect respectively by the both ends transition of conical section and cylindrical bar；The connection
Bar 8 is mounted in working chamber 6 and the both ends of connecting rod 8 are located at preceding working chamber 601 and rear working chamber 602 respectively, and cylindrical bar is located at
In intermediate conduit 603 and it can move left and right.
The side of the secondary piston 4 and rear piston 9 is fixedly connected respectively with the both ends of connecting rod 8 and secondary piston 4 and rear living
Plug 9 respectively with 602 clearance fit of preceding working chamber 601 and rear working chamber.
Described 3 one end of preceding spring is connect with preceding 601 bottom of working chamber, and the other end is connect with the opposite side of secondary piston 4；It is described
One end of piston rod 11 is fixed as one with rear piston 9, the bottom of working chamber 602 after the other end stretches out；10 sets of spring after described
On piston rod 11 and one end is connect with rear 602 bottom of working chamber, and the other end is connect with the opposite side of rear piston 9；It is living before described
Injecting oil liquid 6 in working chamber between plug 4 and rear piston 9.
1 bottom end of preceding hanging ring is welded as a whole with 2 one end of supporting rod, and preceding hanging ring 1 is connected with vehicle frame or vehicle bridge using bolt
It connects, 2 other end of supporting rod is welded and fixed with preceding working chamber 601.
12 bottom end of hanging ring and one end of piston rod 11 are welded as a whole after described, and rear hanging ring 12 uses spiral shell with vehicle bridge or vehicle frame
It tethers and connects.
Fig. 2 show trailing link working state schematic representation under anxious decelerating mode, after the trailing link is mounted on
In suspension, preceding hanging ring 1 and rear hanging ring 12 are separately mounted on vehicle frame 15 and vehicle bridge 18, and 20 installation site of trailing link is in vehicle
18 front of bridge, in anxious moderating process, due to inertia, vehicle bridge 18 and 15 instantaneous velocity difference of vehicle frame are very big, vehicle bridge 18 and vehicle frame 15
Larger relative motion is generated, 18 instantaneous velocity of vehicle bridge is less than vehicle frame 15, and longitudinal force is very big between vehicle bridge 18 and vehicle frame 15, vehicle bridge 18
Piston 9 moves backward rapidly after pulling, and connecting rod 8 is driven also to move backward, and leads to the preceding conical section of connecting rod 8 and preceding work
The rubber sleeve 7 of 601 taper cavity wall of chamber contacts, and hindered, can not continue to move to, and rubber sleeve 7 plays cushioning effect, reduces firm
The impact that degree variation generates, at this time trailing link be integrally equivalent to a rigid rod, longitudinal force by vehicle bridge by rubber sleeve 7,
Preceding 601 inner wall of working chamber, supporting rod 2 and preceding hanging ring 1 are transmitted to vehicle frame, and trailing link overall stiffness becomes larger and is equivalent to rapidly
One rigid rod.
Fig. 3 show trailing link working state schematic representation under anxious accelerating mode, and when automobile emergency accelerates, vehicle bridge is instantaneous
Speed is more than vehicle frame, and longitudinal force is very big between vehicle bridge 18 and vehicle frame 15, and piston 9 travels forward rapidly after vehicle bridge 18 pushes, and drives
Connecting rod 8 also to forward movement, causes the rubber sleeve 7 of the rear conical section and rear 602 taper cavity wall of working chamber of connecting rod 8 to connect
It touches, and hindered, can not continue to move to, rubber sleeve 7 plays cushioning effect, and trailing link has integrally been equivalent to one just at this time
Property bar, longitudinal force are transmitted to vehicle frame 15 by vehicle bridge 18 by rubber sleeve 7,602 inner wall of rear working chamber, supporting rod 2 and preceding hanging ring 1.
Fig. 4 show trailing link working state schematic representation under other operating modes, under other driving cycles, due to vehicle body
Acceleration is relatively low and the factors such as pavement behavior cause between vehicle frame and vehicle bridge there are small high-frequency vibration, is indulged suffered by air spring
Anxious acceleration and anxious decelerating mode, the small high-frequency vibration between vehicle frame 15 and vehicle bridge 18 are much smaller than to power so that secondary piston 4 is with after
Piston 9 drives connecting rod 8 to move reciprocatingly in working chamber 6, the preceding spring 3 of stretching and rear spring 10 so that trailing link is whole
Body rigidity reduces, since longitudinal force is smaller between vehicle bridge 18 and vehicle frame 15 at this time, and preceding spring 3 and 10 rigidity of rear spring compared with
Greatly, so 8 displacement distance of connecting rod is smaller, the conical section of connecting rod 8 will not be contacted with the rubber sleeve 7 on 6 inner wall of working chamber,
Secondary piston 4 and rear piston 9 push fluid to be flowed in elongated intermediate conduit 603 simultaneously, generate damping force.Vehicle frame 15 and vehicle bridge
Extensional vibration between 18 is transferred to vehicle frame by trailing link, and since rigidity is relatively low, vehicle bridge 18 is transmitted to vehicle frame 15
Impact reduce, car comfort and ride comfort are improved.Flowing through elongated intermediate conduit 603 additionally, due to fluid can generate
Larger damping force, therefore the vibration between vehicle frame 15 and vehicle bridge 18 that can decay, further improve ride comfort.
Figures 5 and 6 show the air suspension schematic diagram for being equipped with the passive type stiffness variable trailing link, including four
Connecting rod guiding mechanism, damper 13, air spring 16, connecting plate 21 and equalizer 17.
The double leval jib guiding mechanism includes two trailing links 20 and two V shape poles 14；21 lower end of connecting plate
It is connect with one end of trailing link 20, upper end is mounted on vehicle frame, and the V shape pole 14 is installed on main reducing gear 22 and vehicle frame 15
Between and angled end is fixed on the shell of main reducing gear 22, in addition both ends are separately fixed on vehicle frame 15；The equalizer 17
In vehicle bridge 18, air spring 16 and damper 13 are mounted between equalizer 17 and vehicle frame 15.
Two stiffness variable trailing links 20 be mainly responsible for bear longitudinal force and for different operating modes convert rigidity, two
Root V shape pole 14 is primarily subjected to cross force and a part of longitudinal force, and double leval jib guiding mechanism using the present invention can not only add
Vertical and horizontal load is undertaken under speed and damped condition so as to protect air spring 16 and improve stability of automobile, it can also be
Under other operating modes, reduce rigidity and increase damping so as to improve automobile ride.
One aspect of the present invention can suddenly accelerate and anxious decelerating mode under, due to 8 both sides conical section of middle brace rod with
Rubber sleeve 7 in work cavity wall contacts, and 20 rigidity value of trailing link is caused to become larger and is equivalent to a rigid rod, so that
Trailing link 20 can protect air spring 16 from longitudinal force, and undertake more load transfers, improve automobile and resist " point
Head " and " facing upward head " property improve the stability of automobile.On the other hand, under other driving cycles, due to connecting rod 8 not with work
Rubber sleeve 7 in cavity wall contacts, and with front and rear reciprocating motion of the pistons so that 20 overall stiffness of trailing link becomes smaller, and work
Make the fluid 5 in chamber 6 to flow through elongated intermediate conduit 603 and larger damping force can be generated, so trailing link at this time
20 can be impacted with extensional vibration of the snubber caused by the factors such as Uneven road between vehicle frame 15 and vehicle bridge 18, improve vapour
The ride comfort of vehicle traveling realizes taking into account for stability of automobile and ride comfort under different operating modes.In addition, trailing link 20 is main
Double leval jib guiding mechanism is formed with V shape pole 14, trailing link 20 undertakes most longitudinal force, and V shape pole is primarily subjected to laterally
Power and a part of longitudinal force can reconcile damping action by the rigidity of trailing link 20, further improve double leval jib Guiding machine
The characteristic of structure.
It should be appreciated that although this specification is described according to each embodiment, not each embodiment only includes one
A independent technical solution, this description of the specification is merely for the sake of clarity, and those skilled in the art should will say
Bright book is as an entirety, and the technical solutions in each embodiment can also be properly combined, and forming those skilled in the art can be with
The other embodiment of understanding.
Those listed above is a series of to be described in detail illustrating only for possible embodiments of the invention,
They are not to limit the scope of the invention, all equivalent embodiments made without departing from skill spirit of the present invention or change
It should all be included in the protection scope of the present invention.
Claims (5)
1. a kind of passive type stiffness variable trailing link, which is characterized in that including preceding spring (3), secondary piston (4), fluid
(5), working chamber (6), rubber sleeve (7), connecting rod (8), rear piston (9), rear spring (10) and piston rod (11)；
The both ends of the working chamber (6) are respectively the preceding working chamber (601) of cylinder and rear working chamber (602), and centre is diameter
The cylindrical intermediate conduit (603) smaller than preceding working chamber (601) and rear working chamber (602), preceding working chamber (601) and rear working chamber
(602) it is connected respectively by conical cavity with intermediate conduit (603) both ends；
The shape of the connecting rod (8) is identical with working chamber (6), and the both ends of connecting rod (8) are respectively cylinder, and centre is diameter
The cylindrical bar smaller than cylinder, the cylinder at both ends connect respectively by the both ends transition of conical section and cylindrical bar；The company
Extension bar (8) is in working chamber (6) and the both ends of connecting rod (8) are located at preceding working chamber (601) and rear working chamber respectively
(602), cylindrical bar is located in intermediate conduit (603) and can move left and right；
The side of the secondary piston (4) and rear piston (9) be fixedly connected respectively with the both ends of connecting rod (8) and secondary piston (4) and
Afterwards piston (9) respectively with preceding working chamber (601) and rear working chamber (602) clearance fit；
Described preceding spring (3) one end is connect with preceding working chamber (601) bottom, and the other end is connect with the opposite side of secondary piston (4)；Institute
The one end and rear piston (9) for stating piston rod (11) are fixed as one, the bottom of working chamber (602) after the other end stretches out；After described
Spring (10) is sleeved on piston rod (11) and one end is connect with rear working chamber (602) bottom, and the other end is another with rear piston (9)
Side connects；Injecting oil liquid (6) in working chamber between the secondary piston (4) and rear piston (9).
2. passive type stiffness variable trailing link according to claim 1, which is characterized in that the preceding working chamber
(601) and the conical cavity of rear working chamber (602) is respectively provided with rubber sleeve (7) close to the both ends inner wall of intermediate conduit (603).
3. passive type stiffness variable trailing link according to claim 1, which is characterized in that further include preceding hanging ring (1)
With supporting rod (2)；Preceding hanging ring (1) bottom end is welded as a whole with supporting rod (2) one end, preceding hanging ring (1) and vehicle frame or vehicle bridge
It is connected by screw bolts, supporting rod (2) other end is welded and fixed with preceding working chamber (601).
4. passive type stiffness variable trailing link according to claim 1, which is characterized in that further include rear hanging ring
(12)；Hanging ring (12) bottom end and one end of piston rod (11) are welded as a whole after described, and rear hanging ring (12) is adopted with vehicle bridge or vehicle frame
It is connected with.
A kind of 5. air suspension for being equipped with passive type stiffness variable trailing link described in claim 1, which is characterized in that packet
Include double leval jib guiding mechanism, damper (13), air spring (16), connecting plate (21) and equalizer (17)；
The double leval jib guiding mechanism includes two trailing links (20) and two V shape poles (14)；
Connecting plate (21) lower end is connect with one end of trailing link (20), and upper end is mounted on vehicle frame, the V shape pole
(14) it is installed between main reducing gear (22) and vehicle frame (15) and angled end is fixed on the shell of main reducing gear (22), in addition
Both ends are separately fixed on vehicle frame (15)；
The equalizer (17) in vehicle bridge (18), air spring (16) and damper (13) mounted on equalizer (17) with
Between vehicle frame (15).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610698261.4A CN106143034B (en) | 2016-08-19 | 2016-08-19 | A kind of passive type stiffness variable trailing link and the air suspension for installing the trailing link |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610698261.4A CN106143034B (en) | 2016-08-19 | 2016-08-19 | A kind of passive type stiffness variable trailing link and the air suspension for installing the trailing link |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106143034A CN106143034A (en) | 2016-11-23 |
| CN106143034B true CN106143034B (en) | 2018-06-26 |
Family
ID=57342426
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610698261.4A Active CN106143034B (en) | 2016-08-19 | 2016-08-19 | A kind of passive type stiffness variable trailing link and the air suspension for installing the trailing link |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106143034B (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4309045A (en) * | 1980-01-21 | 1982-01-05 | Raidel John E | Air spring suspension system with parallelogram stabilized axle and anti-roll control |
| DE4338651A1 (en) * | 1993-11-12 | 1995-03-09 | Daimler Benz Ag | Suspension for a rigid axle of a vehicle, especially a truck or bus |
| CN1338997A (en) * | 1999-11-30 | 2002-03-06 | Zf雷姆伏尔德金属制品股份公司 | Axle suspension for rigid axles of vehicles |
| CN105539048A (en) * | 2015-12-17 | 2016-05-04 | 安徽江淮汽车股份有限公司 | Heavy truck lifting air suspension system |
-
2016
- 2016-08-19 CN CN201610698261.4A patent/CN106143034B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4309045A (en) * | 1980-01-21 | 1982-01-05 | Raidel John E | Air spring suspension system with parallelogram stabilized axle and anti-roll control |
| DE4338651A1 (en) * | 1993-11-12 | 1995-03-09 | Daimler Benz Ag | Suspension for a rigid axle of a vehicle, especially a truck or bus |
| CN1338997A (en) * | 1999-11-30 | 2002-03-06 | Zf雷姆伏尔德金属制品股份公司 | Axle suspension for rigid axles of vehicles |
| CN105539048A (en) * | 2015-12-17 | 2016-05-04 | 安徽江淮汽车股份有限公司 | Heavy truck lifting air suspension system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106143034A (en) | 2016-11-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201083245Y (en) | Oil gas spring with control valve | |
| CN110588269A (en) | Hydro-pneumatic suspension mechanism for dump truck | |
| CN201747842U (en) | Single barrel type oil and gas spring | |
| CN202867687U (en) | Shock absorber for automobile | |
| CN204821017U (en) | Adjustable height of car triangle -shaped inflatable shock absorber of preventing leaning forward | |
| CN108791138B (en) | Method for improving running stability of automobile | |
| CN113291402B (en) | Rear shock absorption structure of large-displacement pedal motorcycle | |
| CN103832236B (en) | A kind of motor vehicle suspension vibration insulating system | |
| CN103939518B (en) | A kind of one pole flat-faced tube magneto-rheological vibration damper | |
| CN106143034B (en) | A kind of passive type stiffness variable trailing link and the air suspension for installing the trailing link | |
| CN211308172U (en) | Automobile shock absorption chassis suspension device | |
| CN105443648A (en) | Motorcycle shock absorber with high viscoelasticity | |
| CN209600194U (en) | A kind of car-like robots independent suspension protective device | |
| CN106218335B (en) | A kind of stiffness variable trailing link and the air suspension and its method for installing the trailing link | |
| CN102381372B (en) | Two-way damping type rear suspension device for automobile cab | |
| CN206159355U (en) | Automobile shock absorber ware with buffer gear | |
| CN108662073A (en) | A kind of rear damping for new-energy automobile | |
| CN201961455U (en) | Electro-tricycle | |
| CN203142938U (en) | Damper device of motor tricycle torsion bar type front suspension device | |
| CN206206486U (en) | A kind of rearmounted damping of automobile cab | |
| CN210212636U (en) | Four-connecting-rod rear damping mechanism of motorcycle | |
| RU2696049C1 (en) | Rear wheel suspension | |
| CN2290727Y (en) | Isobaric damping shock reducer | |
| CN207539249U (en) | A kind of vehicle shock absorber | |
| CN219954062U (en) | Protective shock absorber for vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |