CN109583079A - A kind of sliding bearing modeling method based on ADAMS - Google Patents
A kind of sliding bearing modeling method based on ADAMS Download PDFInfo
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- CN109583079A CN109583079A CN201811433992.1A CN201811433992A CN109583079A CN 109583079 A CN109583079 A CN 109583079A CN 201811433992 A CN201811433992 A CN 201811433992A CN 109583079 A CN109583079 A CN 109583079A
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- G—PHYSICS
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- G06F30/20—Design optimisation, verification or simulation
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
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- G06F30/17—Mechanical parametric or variational design
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
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Abstract
The sliding bearing modeling method based on ADAMS that the present invention relates to a kind of, by the threedimensional model for establishing axle journal and bearing shell in ADAMS, and using the constraint added between the method simulation axle journal of generalized force and axis between axle journal and bearing shell, the wear phenomenon in sliding bearing use process can be simulated.Modeling method is quick and easy, does not need calling external program or script.
Description
[technical field]
The invention belongs to simulation technical field more particularly to a kind of sliding bearing modeling methods based on ADAMS.
[background technique]
One of the most common means that dynamics simulation is machinery system dynamics analysis are carried out using software, utilize emulation energy
It is enough that rapidly the state of mechanical system is analyzed, to improve design efficiency, and the performance of system can be made rationally
Prediction.Wherein Dynamics Simulation software ADAMS is that most authoritative, most widely used multi-body Dynamic Analysis is soft in the world
Part.
Sliding bearing is a kind of important bearing type, the machinery especially run under the operating conditions such as low-speed heave-load, large impact
It is had a wide range of applications in system.Since the coefficient of friction and workload of sliding bearing are usually larger, in the course of work
In be easy to happen wear phenomenon, influence equipment operation, this phenomenon simulated in emulation to the accident analysis of mechanical system and pre-
Measuring tool is significant.But due in the model library of ADAMS software and do not include sliding bearing, currently being capable of mould yet
The simulation model of wear phenomenon in quasi- bearing operational process, therefore establish sliding bearing running-in wear model and realize emulation mould
It is necessary to property for draw up.
[summary of the invention]
To solve the above-mentioned problems, the sliding bearing modeling method based on ADAMS that the invention proposes a kind of.
The technical solution adopted by the invention is as follows:
A kind of sliding bearing modeling method based on ADAMS, comprising the following steps:
Step 1: the threedimensional model of axle journal and bearing shell is established in ADAMS；
Step 2: between axle journal and bearing shell add generalized force (General Force), power active position selection axle journal with
The about beam center of bearing shell；
Step 3: system variable is established to indicate the gap between axle journal and bearing shell, is added by Function Builder
Add model as follows:
Wherein, δx+、δx-、δy+, δy-Respectively axle journal and bearing shell in positive direction of the x-axis, negative direction and positive direction of the y-axis and are born
The gap in direction, δx0+、δx0-、δy0+, δy0-Respectively axle journal and bearing shell in positive direction of the x-axis, negative direction and positive direction of the y-axis and are born
The primary clearance in direction, ω are rate of depreciation,For the angular speed that axle journal rotates in bearing shell, Fx、FyRespectively axle journal and bearing shell
Between along the direction x, y active force, r is diameter of axle radius, and t represents the time；
Step 4: defining restraining force by Function Builder, radial constraint, axial direction including bearing shell to axle journal
Restraining force, around radial constraint torque；
Step 5: the moment of friction that bearing shell acts on axis is defined by Function Builder.
Further, in the step 4, bearing shell is defined to the radial constraint of axle journal are as follows:
Wherein, Fx、FyRespectively restraining force of the bearing shell to axle journal in the direction x, y, k, c are respectively represented between bearing shell and axle journal
Radial constraint rigidity and damping, x, y,Respectively represent offset distance of the axle journal relative to initial position in the direction x, y
With speed.
Further, in the step 4, axial constraint power is defined are as follows:
Wherein, FzRestraining force for bearing shell to axle journal in the axial direction, kz、czIt respectively represents axial constraint rigidity and damps, z,Respectively axial dipole field and migration velocity of the axle journal relative to initial position.
Further, it in the step 4, defines around radial constraint torque are as follows:
Wherein, Mx、MyRespectively bearing shell is to axle journal around x, the restraint moment of y-axis, kr、crRespectively constraint rigidity and damping,Respectively represent deviation angle and angular speed of the axle journal relative to initial position around the direction x, y.
Further, in the step 5, the defined formula of the moment of friction are as follows:
Wherein, MzFor the moment of friction that bearing shell acts on axis, coefficient of friction of the μ between axle journal and bearing shell.
The invention has the benefit that the wear phenomenon in sliding bearing use process can be simulated by modeling；And
And modeling method is quick and easy, only need to establish a generalized force in ADAMS and define its constraint equation can be realized, and be not required to
Want calling external program or script.
[Detailed description of the invention]
Described herein the drawings are intended to provide a further understanding of the invention, constitutes part of this application, but
It does not constitute improper limitations of the present invention, in the accompanying drawings:
Fig. 1 is the structural schematic diagram of sliding bearing.
[specific embodiment]
Come that the present invention will be described in detail below in conjunction with attached drawing and specific embodiment, illustrative examples therein and says
It is bright to be only used to explain the present invention but not as a limitation of the invention.
It is illustrated herein in conjunction with 1 pair of attached drawing sliding bearing modeling method of the invention, method includes the following steps:
Step 1: the threedimensional model of axle journal and bearing shell is established in ADAMS, or establishes the diameter of axle and bearing shell in three-dimensional software
Threedimensional model after import ADAMS in.
Step 2: between axle journal and bearing shell add generalized force (General Force), power active position selection axle journal with
The about beam center of bearing shell.
Step 3: system variable is established to indicate the gap between axle journal and bearing shell, is added by Function Builder
Add model as follows:
Such as Fig. 1, δ in formula (1)x+、δx-、δy+, δy-Respectively axle journal and bearing shell positive direction of the x-axis, negative direction and y-axis just
The gap in direction and negative direction, δx0+、δx0-、δy0+, δy0-Respectively axle journal and bearing shell positive direction of the x-axis, negative direction and y-axis just
The primary clearance in direction and negative direction, ω are rate of depreciation,For the angular speed that axle journal rotates in bearing shell, Fx、FyRespectively axis
Along the active force in the direction x, y between neck and bearing shell, r is diameter of axle radius, and t represents the time.
Assuming that δx+、δx-、δy+, δy-Corresponding differential variable title is respectively as follows: Clearence_x_p, Clearence_x_
N, Clearence_x_p, Clearence_x_n；δx0+、δx0-、δy0+, δy0-Corresponding system variable title is respectively
Clearence_xO_p, Clearence_xO_n, Clearence_xO_p, Clearence_xO_n；System corresponding to ω becomes
Measure entitled Omega；System variable corresponding to θ entitled Velocity, Fx、FyCorresponding name variable is respectively
Force_X and Force_Y；The entitled Radius of system variable corresponding to r, then it is as follows to implement code:
Step 4: defining restraining force by Function Builder, radial constraint, axial direction including bearing shell to axle journal
Restraining force, around radial constraint torque.
Specifically, defining bearing shell to the radial constraint of axle journal are as follows:
In formula (2), Fx、FyRespectively restraining force of the bearing shell to axle journal in the direction x, y, k, c respectively represent bearing shell and axle journal it
Between radial constraint rigidity and damping, x, y,Respectively represent offset distance of the axle journal relative to initial position in the direction x, y
From with speed.
Define axial constraint power:
In formula (3), FzRestraining force for bearing shell to axle journal in the axial direction, kz、czRespectively represent axial constraint rigidity and resistance
Buddhist nun, z,Respectively axial dipole field and migration velocity of the axle journal relative to initial position.
Definition is around radial constraint torque are as follows:
In formula (4), Mx、MyRespectively bearing shell is to axle journal around x, the restraint moment of y-axis, Kr、crRespectively constraint rigidity and resistance
Buddhist nun,Respectively represent deviation angle and angular speed of the axle journal relative to initial position around the direction x, y.
Assuming that the MARKER that the diameter of axle and bearing shell are bound in constraint is respectively MARKER_1 and MARKER_2, k, c, kz、cz、
kr、crCorresponding system variable be respectively as follows: STIFF, DAMPING, STIFF_Z, DAMPING_Z, STIFF_R, DAMPING_R,
The then specific code that constraint equation is realized are as follows:
Fx:
-if(DX(MARKER_1,MARKER_2,MARKER_2):0,1,1)*if(DX(MARKER_1,MA RKER_2,
MARKER_2)-VARVAL(Clearence_x_p):0,1,1)*VARVAL(STIFF_X)*(DX(MARKER_1,MARKER_2,
MARKER_2)-VARVAL(Clearence_x_p))-if(DX(MARKER_1,MARKER_2,MARKER_2):1,0,0)*if
(DX(MARKER_1,MARKER_2,MARKER_2)-VARVAL(Clearence_x_n):1,1,0)*VARVAL(STIFF_X)*
(DX(MARKER_1,MARKER_2,MARKER_2)-VARVAL(Clearence_x_n))-VARVAL(DAMPING)*VX
(MARKER_1,MARKER_2,MARKER_2,MARKER_1)
Fy:
-if(DY(MARKER_1,MARKER_2,MARKER_2):0,0,1)*if(DY(MARKER_1,MA RKER_2,
MARKER_2)-VARVAL(Clearence_y_p):0,0,1)*VARVAL(STIFF)*(DY(MARKER_1,MARKER_2,
MARKER_2)-VARVAL(Clearence_y_p))
-if(DY(MARKER_1,MARKER_2,MARKER_2):1,0,0)*if(DY(MARKER_1,MA RKER_2,
MARKER_2)-VARVAL(Clearence_y_n):1,0,0)*VARVAL(STIFF)*(DY(MARKER_1,MARKER_2,
MARKER_2)-VARVAL(Clearence_y_n))
-VARVAL(DAMPING)*VY(MARKER_1,MARKER_2,MARKER_2,MARKER_1)
Fz:
-VARVAL(STIFF_Z)*DZ(MARKER_1,MARKER_2,MARKER_2)-
-VARVAL(DAMPING_Z)*VZ(MARKER_1,MARKER_2,MARKER_2,MARKER_1)
Mx:
-STIFF_R*AX(MARKER_1,MARKER_2)-DAMPING_R*WX(MARKER_1,MARKER_2,MARKER_
2)
My:
-STIFF_R*AY(MARKER_1,MARKER_2)-DAMPING_R*WY(MARKER_1,MARKER_2,MARKER_
2)
Step 5: the moment of friction that bearing shell acts on axis is defined by Function Builder.
Specifically, the defined formula of the moment of friction are as follows:
In formula (5), MzFor the moment of friction that bearing shell acts on axis, coefficient of friction of the μ between axle journal and bearing shell.
Assuming that system variable corresponding to μ is FrictionCoef, then the specific implementation code of moment of friction are as follows:
Mz:
-FrictionCoef*Radius*SQRT(Force_X*Force_X+Force_Y*Force_Y)*SIGN(1,
VARVAL(Velocity))
The above description is only a preferred embodiment of the present invention, thus it is all according to the configuration described in the scope of the patent application of the present invention,
The equivalent change or modification that feature and principle are done, is included in the scope of the patent application of the present invention.
Claims (5)
1. a kind of sliding bearing modeling method based on ADAMS, which comprises the following steps:
Step 1: the threedimensional model of axle journal and bearing shell is established in ADAMS；
Step 2: adding generalized force (General Force) between axle journal and bearing shell, the active position selection axle journal and bearing shell of power
About beam center；
Step 3: system variable is established to indicate the gap between axle journal and bearing shell, mould is added by Function Builder
Type is as follows:
Wherein, δx+、δx-、δy+, δy-Respectively axle journal and bearing shell are in positive direction of the x-axis, negative direction and positive direction of the y-axis and negative direction
Gap, δx0+、δx0-、δy0+, δy0-Respectively axle journal and bearing shell are in positive direction of the x-axis, negative direction and positive direction of the y-axis and negative direction
Primary clearance, ω is rate of depreciation,For the angular speed that axle journal rotates in bearing shell, Fx、FyEdge respectively between axle journal and bearing shell
X, the active force in the direction y, r are diameter of axle radius, and t represents the time；
Step 4: defining restraining force by Function Builder, radial constraint, axial constraint including bearing shell to axle journal
Power, around radial constraint torque；
Step 5: the moment of friction that bearing shell acts on axis is defined by Function Builder.
2. the method according to claim 1, wherein in the step 4, bearing shell is defined to the radial direction of axle journal about
Beam force are as follows:
Wherein, Fx、FyRespectively restraining force of the bearing shell to axle journal in the direction x, y, k, c respectively represent the diameter between bearing shell and axle journal
To constraint rigidity and damping, x, y,Axle journal is respectively represented relative to initial position in the offset distance in the direction x, y and speed
Degree.
3. method described in -2 any one according to claim 1, which is characterized in that in the step 4, define axial constraint
Power are as follows:
Wherein, FzRestraining force for bearing shell to axle journal in the axial direction, kz、czIt respectively represents axial constraint rigidity and damps, z,Point
It Wei not axial dipole field and migration velocity of the axle journal relative to initial position.
4. method according to claim 1 to 3, which is characterized in that in the step 4, define around radial direction about
Beam force square are as follows:
Wherein, Mx、MyRespectively bearing shell is to axle journal around x, the restraint moment of y-axis, Kr、crRespectively constraint rigidity and damping,Respectively represent deviation angle and angular speed of the axle journal relative to initial position around the direction x, y.
5. method according to any of claims 1-4, which is characterized in that in the step 5, the moment of friction
Defined formula are as follows:
Wherein, MzFor the moment of friction that bearing shell acts on axis, coefficient of friction of the μ between axle journal and bearing shell.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811433992.1A CN109583079B (en) | 2018-11-28 | 2018-11-28 | Sliding bearing modeling method based on ADAMS |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811433992.1A CN109583079B (en) | 2018-11-28 | 2018-11-28 | Sliding bearing modeling method based on ADAMS |
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| CN109583079B CN109583079B (en) | 2022-10-04 |
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007269295A (en) * | 2006-03-31 | 2007-10-18 | Toyota Central Res & Dev Lab Inc | Apparatus and method for controlling vehicle motion |
| CN104915481A (en) * | 2015-05-25 | 2015-09-16 | 安徽大学 | Spherical motor cooperative control based on virtual prototype modeling and periodic planning |
| CN105354395A (en) * | 2015-12-03 | 2016-02-24 | 湖南科技大学 | Dynamical equivalent modeling method for ball bearing based on ADAMS (Automatic Dynamic Analysis of Mechanical Systems) |
-
2018
- 2018-11-28 CN CN201811433992.1A patent/CN109583079B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007269295A (en) * | 2006-03-31 | 2007-10-18 | Toyota Central Res & Dev Lab Inc | Apparatus and method for controlling vehicle motion |
| CN104915481A (en) * | 2015-05-25 | 2015-09-16 | 安徽大学 | Spherical motor cooperative control based on virtual prototype modeling and periodic planning |
| CN105354395A (en) * | 2015-12-03 | 2016-02-24 | 湖南科技大学 | Dynamical equivalent modeling method for ball bearing based on ADAMS (Automatic Dynamic Analysis of Mechanical Systems) |
Non-Patent Citations (1)
| Title |
|---|
| 王云霞等: "基于ADAMS的内圆磨床与高速电主轴结构动力学模拟分析", 《制造业自动化》 * |
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| CN109583079B (en) | 2022-10-04 |
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