CN110362938A - A kind of suspension load calculation method based on ADAMS - Google Patents
A kind of suspension load calculation method based on ADAMS Download PDFInfo
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- CN110362938A CN110362938A CN201910654330.5A CN201910654330A CN110362938A CN 110362938 A CN110362938 A CN 110362938A CN 201910654330 A CN201910654330 A CN 201910654330A CN 110362938 A CN110362938 A CN 110362938A
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Abstract
The suspension load calculation method based on ADAMS that the invention discloses a kind of, it is the following steps are included: according to the Top Crossbeam in double cross arm independent suspension, the hard spot coordinate of lower cross arm and spring, double cross arm independent suspension rigid model is established in ADAMS, according to the connection type of the Top Crossbeam and vehicle frame and wheel group, the connection type of the connection type and spring and vehicle frame and lower cross arm of lower cross arm and vehicle frame and wheel group, the constraint between each rigid rod is established in the double cross arm independent suspension rigid model, load needs the operating loading value checked at tire, the load value between each rigid rod at constraint is calculated.Its purpose is to provide a kind of suspension load calculation method based on ADAMS, the space loading at suspension guide mechanism and vehicle frame, wheel group interface can be calculated in it, Strength co-mputation for suspension guide mechanism topological optimization and Strength co-mputation and vehicle frame, wheel group and suspension guide mechanism junction.
Description
Technical field
The present invention relates to vehicular fields, more particularly to a kind of calculation method of vehicle suspension load.
Background technique
When chassis suspension fork of vehicle system designs, guiding mechanism needs to carry out topological optimization and Strength co-mputation；Vehicle frame, wheel group knot
When structure designs, it is also desirable to calculate the intensity of itself and suspension guide mechanism interface；Therefore, it is necessary to carry out the suspension under limiting condition
LOAD FOR.
Conventional theoretical formula method method, only calculating suspension guide mechanism and vehicle frame connecting interface are flat in a certain stress
The load in face, space loading are difficult to calculate, and when connecting interface is greater than 1, theoretical formula method method is just not suitable for.
Summary of the invention
The suspension load calculation method based on ADAMS that the technical problem to be solved in the present invention is to provide a kind of, can count
It calculates and obtains the space loading at suspension guide mechanism and vehicle frame, wheel group interface, be used for suspension guide mechanism topological optimization and intensity
The Strength co-mputation of calculating and vehicle frame, wheel group and suspension guide mechanism junction.
The present invention is based on the suspension load calculation methods of ADAMS, comprising the following steps:
According to the hard spot coordinate of Top Crossbeam, lower cross arm and spring in double cross arm independent suspension, established in ADAMS double horizontal
Arm independent suspension rigid model,
According to the connection type of connection type, lower cross arm and the vehicle frame and wheel group of the Top Crossbeam and vehicle frame and wheel group and
The connection type of spring and vehicle frame and lower cross arm is established between each rigid rod in the double cross arm independent suspension rigid model
Constraint,
Load needs the operating loading value checked at tire, and the load between each rigid rod at constraint is calculated
Value.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the hard spot coordinate of the Top Crossbeam is in Top Crossbeam
Side point coordinate and Top Crossbeam points outside coordinate.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the hard spot coordinate of the lower cross arm is in lower cross arm
Side point coordinate and lower cross arm points outside coordinate.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the hard spot coordinate of the spring is fulcrum on spring
Coordinate and spring lower fulcrum coordinate.
The present invention is based on the suspension load calculation methods of ADAMS, wherein described in the double cross arm independent suspension rigid body mould
The constraint established between each rigid rod in type includes: that revolute is all made of between the Top Crossbeam and lower cross arm and vehicle frame about
Beam is all made of typed ball bearing pair constraint, adopts between the upper journal and vehicle frame of the spring between the Top Crossbeam and lower cross arm and wheel group
It is constrained with typed ball bearing pair, is also constrained using typed ball bearing pair between the down journal and lower cross arm of the spring.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the load at tire needs the operating condition checked
Load value specifically: in the operating loading value that ground contact point load needs to check, the operating loading value is typical condition
Input load, the input load of the typical condition include static load operating condition, 3 times of static load operating conditions, rollover condition and emergency braking work
Condition.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is the input of static load operating condition
When load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point and bullet
The stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is the defeated of 3 times of static load operating conditions
When entering load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point and
The stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is the input of rollover condition
When load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point and bullet
The stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is emergency braking operating condition
When input load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point
With the stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS to be based on ADAMS Dynamics Simulation software for calculation, establishes
Double cross arm independent suspension system dynamics computation model, can be calculated the guiding mechanism (i.e. Top Crossbeam and lower cross arm) of suspension with
Load at vehicle frame, wheel group interface, for suspension guide mechanism topological optimization and Strength co-mputation and vehicle frame, wheel group and suspension
The Strength co-mputation of guiding mechanism junction.
The present invention will be further explained below with reference to the attached drawings.
Detailed description of the invention
Fig. 1 is that the present invention is based on the flow charts of the suspension load calculation method of ADAMS；
Fig. 2 is the suspension LOAD FOR ADAMS model in the present invention.
Specific embodiment
As shown in Figure 1, the present invention is based on the suspension load calculation methods of ADAMS, comprising the following steps:
According to the hard spot coordinate of Top Crossbeam, lower cross arm and spring in double cross arm independent suspension, established in ADAMS double horizontal
Arm independent suspension rigid model (as shown in Figure 2),
According to the connection type of connection type, lower cross arm and the vehicle frame and wheel group of the Top Crossbeam and vehicle frame and wheel group and
The connection type of spring and vehicle frame and lower cross arm is established between each rigid rod in the double cross arm independent suspension rigid model
Constraint,
Load needs the operating loading value checked at tire, and the load between each rigid rod at constraint is calculated
Value.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the hard spot coordinate of the Top Crossbeam is in Top Crossbeam
Side point coordinate and Top Crossbeam points outside coordinate.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the hard spot coordinate of the lower cross arm is in lower cross arm
Side point coordinate and lower cross arm points outside coordinate.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the hard spot coordinate of the spring is fulcrum on spring
Coordinate and spring lower fulcrum coordinate.
The present invention is based on the suspension load calculation methods of ADAMS, wherein described in the double cross arm independent suspension rigid body mould
The constraint established between each rigid rod in type includes: that revolute is all made of between the Top Crossbeam and lower cross arm and vehicle frame about
Beam is all made of typed ball bearing pair constraint, adopts between the upper journal and vehicle frame of the spring between the Top Crossbeam and lower cross arm and wheel group
It is constrained with typed ball bearing pair, is also constrained using typed ball bearing pair between the down journal and lower cross arm of the spring.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the load at tire needs the operating condition checked
Load value specifically: in the operating loading value that ground contact point load needs to check, the operating loading value is typical condition
Input load, the input load of the typical condition include static load operating condition, 3 times of static load operating conditions, rollover condition and emergency braking work
Condition.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is the input of static load operating condition
When load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point and bullet
The stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is the defeated of 3 times of static load operating conditions
When entering load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point and
The stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is the input of rollover condition
When load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point and bullet
The stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS, wherein the operating loading value is emergency braking operating condition
When input load, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm after point, lower cross arm exterior point
With the stress of spring lower fulcrum.
The present invention is based on the suspension load calculation methods of ADAMS to be based on ADAMS Dynamics Simulation software for calculation, establishes
Double cross arm independent suspension system dynamics computation model, can be calculated the guiding mechanism (i.e. Top Crossbeam and lower cross arm) of suspension with
Load at vehicle frame, wheel group interface, for suspension guide mechanism topological optimization and Strength co-mputation and vehicle frame, wheel group and suspension
The Strength co-mputation of guiding mechanism junction.
Below with reference to table, invention is further described in detail:
(1) according to double cross arm independent suspension hard spot coordinate, suspension system hard spot coordinate is established in ADAMS, it is required
Suspension hard spot coordinate is as shown in table 1.According to suspension practical structures, rigid rod is established between hard spot coordinate, establishes suspension system
Rigid model.
1 double cross arm independent suspension hard spot of table
(2) according to suspension system guiding mechanism (i.e. Top Crossbeam and lower cross arm) and vehicle frame, the kinematic pair type of wheel group,
The constraint between each rigid rod is established in ADAMS model.It is constrained between guiding mechanism and vehicle frame using revolute, guiding mechanism
It is constrained with wheel group using typed ball bearing pair, spring upper journal and vehicle frame are constrained using typed ball bearing pair, and spring down journal is also used with lower cross arm
Typed ball bearing pair constraint.
(3) suspension flexibility damping element is established in ADAMS model with helical spring+model of damper, settable bullet
The rigidity of spring and the damping of damper.
(4) in the input load of ground contact point load typical condition, the input load of typical condition is as shown in table 2, packet
Include static load operating condition, 3 times of static load operating conditions, rollover condition and emergency braking operating condition.
2 typical condition input load of table
(5) according to the input load of each typical condition, the stress of suspension system Yu other system junctions is calculated, such as
Shown in table 3, as the input of the load of suspension guide mechanism topological optimization and Strength co-mputation and carriage wheels group and suspension interface
The load of strength check inputs.
3 typical condition suspension loading conditions of table
Embodiment described above only describe the preferred embodiments of the invention, not to model of the invention
It encloses and is defined, without departing from the spirit of the design of the present invention, those of ordinary skill in the art are to technical side of the invention
The various changes and improvements that case is made should all be fallen into the protection scope that claims of the present invention determines.
Claims (10)
1. a kind of suspension load calculation method based on ADAMS, which comprises the following steps:
According to the hard spot coordinate of Top Crossbeam, lower cross arm and spring in double cross arm independent suspension, it is only that double transverse arms are established in ADAMS
Vertical suspension rigid model,
According to the connection type and spring of connection type, lower cross arm and the vehicle frame and wheel group of the Top Crossbeam and vehicle frame and wheel group
With the connection type of vehicle frame and lower cross arm, the pact between each rigid rod is established in the double cross arm independent suspension rigid model
Beam,
Load needs the operating loading value checked at tire, and the load value between each rigid rod at constraint is calculated.
2. the suspension load calculation method according to claim 1 based on ADAMS, it is characterised in that: the Top Crossbeam
Hard spot coordinate is side point coordinate and Top Crossbeam points outside coordinate in Top Crossbeam.
3. the suspension load calculation method according to claim 2 based on ADAMS, it is characterised in that: the lower cross arm
Hard spot coordinate is side point coordinate and lower cross arm points outside coordinate in lower cross arm.
4. the suspension load calculation method according to claim 3 based on ADAMS, it is characterised in that: the spring it is hard
Point coordinate is fulcrum coordinate and spring lower fulcrum coordinate on spring.
5. the suspension load calculation method according to claim 4 based on ADAMS, which is characterized in that described described double
The constraint established in cross arm independent suspension rigid model between each rigid rod include: the Top Crossbeam and lower cross arm and vehicle frame it
Between be all made of revolute constraint, be all made of between the Top Crossbeam and lower cross arm and wheel group typed ball bearing pair constraint, the spring it is upper
It is constrained between trunnion and vehicle frame using typed ball bearing pair, is also constrained using typed ball bearing pair between the down journal and lower cross arm of the spring.
6. the suspension load calculation method according to claim 5 based on ADAMS, which is characterized in that described at tire
Load needs the operating loading value checked specifically: in the operating loading value that ground contact point load needs to check, the operating condition
Load value is the input load of typical condition, and the input load of the typical condition includes static load operating condition, 3 times of static load operating conditions, sides
Turn over operating condition and emergency braking operating condition.
7. the suspension load calculation method according to claim 6 based on ADAMS, it is characterised in that: the operating loading
When value is the input load of static load operating condition, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm
The stress of point, lower cross arm exterior point and spring lower fulcrum afterwards.
8. the suspension load calculation method according to claim 7 based on ADAMS, it is characterised in that: the operating loading
When value is the input load of 3 times of static load operating conditions, point in Top Crossbeam, Top Crossbeam exterior point, preceding point, lower cross arm in lower cross arm is calculated
The stress of point, lower cross arm exterior point and spring lower fulcrum after interior.
9. the suspension load calculation method according to claim 8 based on ADAMS, it is characterised in that: the operating loading
When value is the input load of rollover condition, point in Top Crossbeam, Top Crossbeam exterior point, preceding point in lower cross arm is calculated, in lower cross arm
The stress of point, lower cross arm exterior point and spring lower fulcrum afterwards.
10. the suspension load calculation method according to claim 9 based on ADAMS, it is characterised in that: the operating loading
When value is the input load of emergency braking operating condition, point in Top Crossbeam, Top Crossbeam exterior point, preceding point, lower cross in lower cross arm is calculated
The stress of point, lower cross arm exterior point and spring lower fulcrum after in arm.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910654330.5A CN110362938B (en) | 2019-07-19 | 2019-07-19 | ADAMS-based suspension load calculation method |
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| CN201910654330.5A CN110362938B (en) | 2019-07-19 | 2019-07-19 | ADAMS-based suspension load calculation method |
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| CN110362938B CN110362938B (en) | 2023-04-25 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113239453A (en) * | 2021-04-02 | 2021-08-10 | 陕西同力重工股份有限公司 | Off-highway dump truck frame load calculation method |
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| CN107784133A (en) * | 2016-08-25 | 2018-03-09 | 上汽通用汽车有限公司 | The collocation method of McPherson front suspension hard spot |
| CN109263423A (en) * | 2018-10-25 | 2019-01-25 | 北京航天发射技术研究所 | A kind of independent suspension guiding mechanism and its test device and method |
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2019
- 2019-07-19 CN CN201910654330.5A patent/CN110362938B/en active Active
Patent Citations (6)
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| CN102945307A (en) * | 2012-11-27 | 2013-02-27 | 北京汽车股份有限公司 | Automobile chassis key structural member structure optimization design method |
| US20140244224A1 (en) * | 2013-02-28 | 2014-08-28 | Ford Global Technologies, Llc | Rapid assessment of suspension geometry for loads |
| CN103310047A (en) * | 2013-05-30 | 2013-09-18 | 同济大学 | Optimization method facing lateral force of Macpherson suspension shock absorber |
| CN107784133A (en) * | 2016-08-25 | 2018-03-09 | 上汽通用汽车有限公司 | The collocation method of McPherson front suspension hard spot |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113239453A (en) * | 2021-04-02 | 2021-08-10 | 陕西同力重工股份有限公司 | Off-highway dump truck frame load calculation method |
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