CN109318675B - Interconnection formula ISD suspension - Google Patents
Interconnection formula ISD suspension Download PDFInfo
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- CN109318675B CN109318675B CN201810966497.0A CN201810966497A CN109318675B CN 109318675 B CN109318675 B CN 109318675B CN 201810966497 A CN201810966497 A CN 201810966497A CN 109318675 B CN109318675 B CN 109318675B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/06—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid
- B60G21/073—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
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Abstract
The invention relates to an interconnected ISD suspension, which comprises an energy accumulator, a damping valve, a hydraulic cylinder, a piston rod, a spiral pipe, a connecting pipeline and an electro-hydraulic control module, wherein the piston divides the hydraulic cylinder into an upper cavity and a lower cavity, the upper cavity of the hydraulic cylinder is communicated with the energy accumulator, the damping valve is arranged at the inlet of the energy accumulator, the upper end of the hydraulic cylinder is hinged with a suspended mass, the lower end of the piston rod is hinged with a non-suspended mass, and the hydraulic cylinders are interconnected through the spiral pipe, the electro-hydraulic control module and a high-pressure oil pipe. Compared with the traditional interconnected suspension, the suspension can not only fully utilize the rigidity and the damping of each suspension for vibration reduction, but also utilize oil liquid in high-speed motion to generate inertia capacity, greatly improve the dynamic load and the high-frequency peak value of a tire, enhance road friendliness and improve driving safety.
Description
Technical Field
The invention relates to an oil-gas suspension system, in particular to an oil-gas interconnected suspension system with an inertial container.
Background
The hydro-pneumatic suspension is widely applied to military vehicles, engineering vehicles and car racing cars, can realize the functions of anti-roll, anti-pitch, axle load balancing and the like through different communicating structures, has the characteristic of anti-vehicle reverse motion in various forms such as transverse interconnection, cross interconnection, mixed interconnection and the like, can increase the pitch/vertical mode rigidity of a suspension system when the hydraulic interconnected suspension is arranged on a front wheel set and a rear wheel set, and can improve the lateral/warp rigidity of the suspension system when the hydraulic interconnected suspension is arranged on a left wheel set and a right wheel set.
Road friendliness is used to describe the damage and destruction of the road surface by the dynamic load of a car tyre. The increased use of heavy-duty commercial and special vehicles is a major cause of road surface damage, which can result in significant urban road maintenance and management costs. The dynamic wheel load is caused by vibration generated by the vehicle excited by road surface unevenness.
The inerter is a new element proposed based on the electromechanical analogy theory, having the same inertial characteristics as the mass element. The inertial container is introduced into a vehicle suspension system, an inertial-spring-damper (ISD) suspension becomes a new direction for the technical development of a passive suspension, and the ISD suspension can inhibit the low-frequency resonance of a vehicle body, improve the comfort of a vehicle, reduce the wheel bounce and improve the grounding property of a tire.
Disclosure of Invention
The invention aims to provide an interconnected ISD suspension which can reduce the dynamic load of a tire and the dynamic stroke of a suspension, improve the grip of the tire and improve the road friendliness.
In order to achieve the purpose, the invention adopts the technical scheme that the interconnected ISD suspension comprises an electro-hydraulic control module, a first oil cylinder and a second oil cylinder, wherein a first spiral pipe is arranged between the electro-hydraulic control module and a rodless cavity of the first oil cylinder, a rodless cavity of the first oil cylinder is also connected with a first energy accumulator, and a first damping valve is arranged at an inlet of the first energy accumulator; a second spiral pipe is arranged between the electrohydraulic control module and a rodless cavity of the second oil cylinder, a second energy accumulator is further connected to the rodless cavity of the second oil cylinder, and a second damping valve is arranged at an inlet of the second energy accumulator; the rodless cavities of the first oil cylinder and the second oil cylinder are hinged with the suspension mass, and piston rods of the first oil cylinder and the second oil cylinder are hinged with the non-suspension mass.
In the scheme, the hydraulic control system further comprises a third oil cylinder and a fourth oil cylinder, a third spiral pipe is installed between the electro-hydraulic control module and a rodless cavity of the third oil cylinder, a third energy accumulator is further connected to the rodless cavity of the third oil cylinder, and a third damping valve is arranged at an inlet of the third energy accumulator; a fourth spiral pipe is arranged between the electrohydraulic control module and a rodless cavity of the fourth oil cylinder, a rodless cavity of the fourth oil cylinder is also connected with a fourth energy accumulator, and a fourth damping valve is arranged at an inlet of the fourth energy accumulator; and the rodless cavities of the third oil cylinder and the fourth oil cylinder are hinged with the suspended mass, and the piston rods of the third oil cylinder and the fourth oil cylinder are hinged with the non-suspended mass.
In the above scheme, the first accumulator, the second accumulator, the third accumulator and the fourth accumulator all use gas as elastic media, gas in gas springs in the first accumulator, the second accumulator, the third accumulator and the fourth accumulator is separated from oil in a pipeline system through a rubber diaphragm or a floating piston, and the gas springs generate elastic force.
The invention also protects the application of the interconnected ISD suspension in the process of rolling or pitching of the vehicle.
The invention also protects the application of the interconnected ISD suspension in the process of generating side rolling, pitching, warping and vertical vibration of the vehicle.
The invention has the beneficial effects that: the invention adopts an 'interconnection' mode, increases the spiral pipe to realize inertia energy storage, and can greatly improve the grounding property of the tire compared with the interconnection suspension in the traditional meaning; the difference with the oil gas suspension with the inerter is that the suspension rigidity is further reduced, the driving smoothness is improved, and the suspension dynamic stroke is improved through different interconnection forms.
Drawings
Fig. 1 is a schematic diagram of a left-right communication type interconnected ISD suspension.
Fig. 2 is a schematic diagram of a front-back communication type interconnection type ISD suspension.
Fig. 3 is a schematic diagram of a hybrid communication type interconnected ISD suspension.
Fig. 4 shows 5 communication modes of the hybrid communication type suspension realized by the electro-hydraulic control module.
FIG. 5 is a tire dynamic load power spectral density contrast plot.
Fig. 6 is a power spectral density contrast plot for suspension dynamic travel.
FIG. 7 is a body acceleration power spectral density contrast plot.
FIG. 8 is a side rake acceleration power spectral density contrast plot.
Detailed Description
The invention is further illustrated by the following figures and examples.
In a first embodiment, as shown in fig. 1 and 2, an interconnected ISD suspension comprises an electro-hydraulic control module 8, a first oil cylinder 4-1 and a second oil cylinder 4-2, wherein a first spiral pipe 6-1 is installed between the electro-hydraulic control module 8 and a rodless cavity of the first oil cylinder 4-1, a rodless cavity of the first oil cylinder 4-1 is also connected with a first energy accumulator 1-1, and a first damping valve 2-1 is arranged at an inlet of the first energy accumulator 1-1; a second spiral pipe 6-2 is arranged between the electrohydraulic control module 8 and a rodless cavity of the second oil cylinder 4-2, a second energy accumulator 1-2 is connected to the rodless cavity of the second oil cylinder 4-1, and a second damping valve 2-2 is arranged at an inlet of the second energy accumulator 1-2; the rodless cavities of the first oil cylinder 4-1 and the second oil cylinder 4-2 are hinged with the suspended mass, and the piston rods of the first oil cylinder 4-1 and the second oil cylinder 4-2 are hinged with the non-suspended mass.
On the basis of a transverse hydraulic interconnection suspension, a spiral pipe is connected to a high-pressure pipeline communicated with a hydraulic cylinder of the vehicle suspension, the area of a piston is larger than the sectional area of the spiral pipe, so that oil can rotate at high speed in the spiral pipe and store a large amount of kinetic energy to generate an inertial volume; when the vehicle body vibrates vertically, the left wheel and the right wheel jump uniformly, the oil pressure in the left hydraulic cylinder and the right hydraulic cylinder is basically uniform, the oil is in the communicating pipeline and the spiral pipe, at the moment, the gas spring in the energy accumulator relaxes the impact, the vibration amplitude is reduced, and the throttle valve attenuates the vibration; when the automobile body takes place to heels, the left and right wheels are jumped inconsistently, and the hypothesis is under the effect that the tire is jumped, and the oil pressure in the pneumatic cylinder of left side is higher than the right side, and fluid will be under left side piston promotion, flows to the pneumatic cylinder of right side from the pneumatic cylinder of left side, and fluid high-speed rotation in the spiral pipe converts hydraulic energy into kinetic energy, and the interior pressure differential of left and right sides pneumatic cylinder reduces for left and right sides suspension stroke reduces, improves tire dynamic load simultaneously, has improved road friendship nature.
The left-right interconnection structure of the embodiment is mainly operated when the vehicle rolls (fig. 1), and the up-down interconnection structure of the embodiment is mainly operated when the vehicle pitches (fig. 2).
Example two: fig. 3 is a second embodiment of the interconnected ISD suspension, on the basis of the first embodiment, a third oil cylinder 4-3 and a fourth oil cylinder 4-4 are added, a third spiral pipe 6-3 is installed between the electro-hydraulic control module 8 and a rodless cavity of the third oil cylinder 4-3, a third energy accumulator 1-3 is further connected to the rodless cavity of the third oil cylinder 4-3, and a third damping valve 2-3 is arranged at an inlet of the third energy accumulator 1-3; a fourth spiral pipe 6-4 is arranged between the electrohydraulic control module 8 and a rodless cavity of the fourth oil cylinder 4-4, a fourth energy accumulator 1-4 is connected to the rodless cavity of the fourth oil cylinder 4-4, and a fourth damping valve 2-4 is arranged at an inlet of the fourth energy accumulator 1-4; the rodless cavities of the third oil cylinder 4-3 and the fourth oil cylinder 4-4 are hinged with the suspended mass, and the piston rods of the third oil cylinder 4-3 and the fourth oil cylinder 4-4 are hinged with the non-suspended mass.
The difference from the first embodiment is that the electric/hydraulic control module according to the third embodiment is adjusted to adopt different interconnection forms (fig. 4) for different motion forms of vehicle roll, pitch, warp, vertical vibration and the like, so that the optimal adjustment of the posture of the vehicle body is realized while the grip of the tire is improved.
In two embodiments, the first accumulator 1-1, the second accumulator 1-2, the third accumulator 1-3 and the fourth accumulator 1-4 all use gas as elastic medium, gas in a gas spring in the first accumulator 1-1, the second accumulator 1-2, the third accumulator 1-3 and the fourth accumulator 1-4 is separated from oil in a pipeline system through a rubber diaphragm or a floating piston, and the gas spring generates elastic force.
In order to compare and analyze the performance difference of the interconnected type ISD suspension, the traditional interconnected suspension and the traditional passive suspension, simulation analysis is carried out in the method, the left and right communicated traditional interconnected suspension, the left and right communicated type ISD suspension and the traditional passive suspension are selected for comparison, the specific structure is shown in figures 1 and 2, and the traditional passive suspension is of a damping and spring parallel structure. In the simulation, a vehicle 20m/s drives through a B-level road surface as road surface spectrum input, the suspension stiffness, the damping and the inertia capacitance are assumed to be linear, the sprung mass, the unsprung mass and the tire stiffness of the three suspensions are equal, and other suspension parameters are obtained through optimization. Fig. 5 to 8, which are output power spectral density contrast charts of the left and right interconnected ISD suspension, the conventional passive suspension and the left and right interconnected conventional suspension, can be obtained through simulation.
As can be seen from fig. 5, although the peak value of the tire dynamic load of the conventional interconnected suspension is greatly improved in the low frequency band, the peak value of the tire dynamic load is obviously deteriorated in the high frequency band, and the performance of the interconnected ISD suspension is closer to that of the conventional passive suspension in the high frequency band. As can be seen from fig. 6, the suspension stroke resonance frequency band of the interconnected ISD suspension is narrower than that of the traditional interconnected suspension. As can be seen from FIG. 7, compared with the traditional suspension, the interconnected ISD suspension can obviously restrain the vibration of a vehicle body at 0-3 Hz, but the vibration isolation effect at a low frequency band is not as good as that of the traditional interconnected suspension.
TABLE 1 random response output RMS value
As can be seen from table 1, compared with the conventional passive suspension, the root mean square values of the roll angular acceleration of the interconnected ISD suspension and the conventional interconnected suspension are respectively reduced by 7.3% and 21.2%; the vertical acceleration of the vehicle body is respectively reduced by 9.2 percent and 22.7 percent; the dynamic load of the tire is deteriorated by 1.3 percent and 20.1 percent; the suspension travel of the interconnected ISD suspension improved by 11.1%, compared to a 0.9% deterioration of the conventional interconnected suspension.
In conclusion, the interconnected ISD suspension is generally superior to the traditional passive suspension, although the vibration isolation performance at a low frequency band is slightly less than that of the traditional interconnected suspension, the deterioration of the dynamic load of the tire at a high frequency band can be compensated, the grounding performance of the tire is improved, and the road friendliness is improved.
Claims (4)
1. An interconnected ISD suspension comprises an electro-hydraulic control module (8), a first oil cylinder (4-1) and a second oil cylinder (4-2), and is characterized in that a first spiral pipe (6-1) is arranged between the electro-hydraulic control module (8) and a rodless cavity of the first oil cylinder (4-1), a first energy accumulator (1-1) is further connected to the rodless cavity of the first oil cylinder (4-1), and a first damping valve (2-1) is arranged at an inlet of the first energy accumulator (1-1); a second spiral pipe (6-2) is arranged between the electro-hydraulic control module (8) and a rodless cavity of the second oil cylinder (4-2), a second energy accumulator (1-2) is connected to the rodless cavity of the second oil cylinder (4-2), and a second damping valve (2-2) is arranged at an inlet of the second energy accumulator (1-2); the rodless cavities of the first oil cylinder (4-1) and the second oil cylinder (4-2) are hinged with the suspended mass, and piston rods of the first oil cylinder (4-1) and the second oil cylinder (4-2) are hinged with the non-suspended mass; the hydraulic control system is characterized by further comprising a third oil cylinder (4-3) and a fourth oil cylinder (4-4), a third spiral pipe (6-3) is installed between the electro-hydraulic control module (8) and a rodless cavity of the third oil cylinder (4-3), a third energy accumulator (1-3) is further connected to the rodless cavity of the third oil cylinder (4-3), and a third damping valve (2-3) is arranged at an inlet of the third energy accumulator (1-3); a fourth spiral pipe (6-4) is arranged between the electro-hydraulic control module (8) and a rodless cavity of the fourth oil cylinder (4-4), a fourth energy accumulator (1-4) is connected to the rodless cavity of the fourth oil cylinder (4-4), and a fourth damping valve (2-4) is arranged at an inlet of the fourth energy accumulator (1-4); the rodless cavities of the third oil cylinder (4-3) and the fourth oil cylinder (4-4) are hinged with the suspended mass, and the piston rods of the third oil cylinder (4-3) and the fourth oil cylinder (4-4) are hinged with the non-suspended mass.
2. An interconnected ISD suspension according to claim 1, characterized in that the first accumulator (1-1), the second accumulator (1-2), the third accumulator (1-3) and the fourth accumulator (1-4) all have gas as elastic medium, the gas in the gas springs inside the first accumulator (1-1), the second accumulator (1-2), the third accumulator (1-3) and the fourth accumulator (1-4) is separated from the oil in the pipe system by a rubber diaphragm or a floating piston, the gas springs generating elastic force.
3. Use of the interconnected ISD suspension of claim 1 in the roll or pitch of a vehicle.
4. Use of the interconnected ISD suspension of claim 1 in the roll, pitch, warp, vertical vibration of a vehicle.
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| CN201810966497.0A CN109318675B (en) | 2018-08-23 | 2018-08-23 | Interconnection formula ISD suspension |
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| CN201810966497.0A CN109318675B (en) | 2018-08-23 | 2018-08-23 | Interconnection formula ISD suspension |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110001340B (en) * | 2019-03-28 | 2022-03-22 | 江苏大学 | Air suspension system, oil liquid communication pipeline and control method of oil liquid communication pipeline |
| EP3822099B1 (en) | 2019-11-15 | 2022-03-02 | Ningbo Geely Automobile Research & Development Co. Ltd. | An anti-roll wheel suspension system for vehicles, and a method for performing anti-roll of a vehicle with an anti-roll wheel suspension system |
| CN113147298B (en) * | 2021-03-24 | 2024-01-05 | 江苏大学 | Multi-mode double-air-chamber oil-gas ISD suspension and working method thereof |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001047839A (en) * | 1999-08-06 | 2001-02-20 | Toyota Motor Corp | Suspension for vehicle |
| JP2009102015A (en) * | 2009-02-09 | 2009-05-14 | Toyota Motor Corp | Vehicular suspension device |
| CN103921647A (en) * | 2014-04-03 | 2014-07-16 | 江苏大学 | Rear suspension of hydraulic interconnected torsion eliminating suspension |
| CN104044429A (en) * | 2014-06-04 | 2014-09-17 | 江苏大学 | Hydraulic interconnection ISD (Inerter-Spring-Damper) hanger bracket |
| CN104228514A (en) * | 2014-08-25 | 2014-12-24 | 常州万安汽车部件科技有限公司 | Vehicle suspension system, working method thereof and motor vehicle |
| CN106379130A (en) * | 2016-11-03 | 2017-02-08 | 管中林 | Car hydraulic pressure suspension interconnection system for realizing twist elimination, pitching resistance and side inclination resistance |
| CN206416801U (en) * | 2017-01-19 | 2017-08-18 | 管中林 | One kind realizes multi-functional fluid interconnection suspension system |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4181768B2 (en) * | 2001-11-14 | 2008-11-19 | トヨタ自動車株式会社 | Vehicle suspension system |
| JP4151599B2 (en) * | 2004-04-08 | 2008-09-17 | トヨタ自動車株式会社 | Vehicle suspension system |
| US9452654B2 (en) * | 2009-01-07 | 2016-09-27 | Fox Factory, Inc. | Method and apparatus for an adjustable damper |
| CN103434361A (en) * | 2013-08-08 | 2013-12-11 | 常州万安汽车部件科技有限公司 | Passive hydraulic interconnection suspension capable of resisting pitch and improving vehicle comfortability |
| CN203818971U (en) * | 2014-04-04 | 2014-09-10 | 三一汽车制造有限公司 | Anti-overturning vehicle hydro-pneumatic suspension system and vehicle |
| CN104228515A (en) * | 2014-08-25 | 2014-12-24 | 常州万安汽车部件科技有限公司 | Vehicle suspension system, working method thereof and motor vehicle |
| CN106183686B (en) * | 2016-08-01 | 2018-12-14 | 江苏大学 | A kind of oil gas actively interconnects feed energy suspension |
-
2018
- 2018-08-23 CN CN201810966497.0A patent/CN109318675B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001047839A (en) * | 1999-08-06 | 2001-02-20 | Toyota Motor Corp | Suspension for vehicle |
| JP2009102015A (en) * | 2009-02-09 | 2009-05-14 | Toyota Motor Corp | Vehicular suspension device |
| CN103921647A (en) * | 2014-04-03 | 2014-07-16 | 江苏大学 | Rear suspension of hydraulic interconnected torsion eliminating suspension |
| CN104044429A (en) * | 2014-06-04 | 2014-09-17 | 江苏大学 | Hydraulic interconnection ISD (Inerter-Spring-Damper) hanger bracket |
| CN104228514A (en) * | 2014-08-25 | 2014-12-24 | 常州万安汽车部件科技有限公司 | Vehicle suspension system, working method thereof and motor vehicle |
| CN106379130A (en) * | 2016-11-03 | 2017-02-08 | 管中林 | Car hydraulic pressure suspension interconnection system for realizing twist elimination, pitching resistance and side inclination resistance |
| CN206416801U (en) * | 2017-01-19 | 2017-08-18 | 管中林 | One kind realizes multi-functional fluid interconnection suspension system |
Non-Patent Citations (1)
| Title |
|---|
| 油气ISD悬架建模仿真与试验;张华新;《工程科技Ⅱ辑》;20180110;C35-98页 * |
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