CN108376191A - A kind of disk brake friction element torque adaptation design method - Google Patents
A kind of disk brake friction element torque adaptation design method Download PDFInfo
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- CN108376191A CN108376191A CN201810127262.2A CN201810127262A CN108376191A CN 108376191 A CN108376191 A CN 108376191A CN 201810127262 A CN201810127262 A CN 201810127262A CN 108376191 A CN108376191 A CN 108376191A
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
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Abstract
The present invention relates to a kind of disk brake friction element torque adaptation design methods, analyze the braking process of vehicle first, are calculated by vehicle and ground brake force and the performance parameter of on-position analyzes the running total brake force F of work for determining brakezWith torque M, and disk brake pressure law cloud atlas is drawn by finite element loaded tooth contact analysis according to parameters such as the number of friction pairs of brake, contacts area and calculates the friction pair pressing force reduction coefficient C of brake by on-load pressure F additive processes, to obtain the attenuation degree of braking torque.Then the torque M that brake friction element is capable of providing is calculated by formula；It relatively determines whether design result meets design condition finally by checking, the conditions such as equivalent redius, the contact area of brake is adjusted if being unsatisfactory for design condition, the final torque design result for obtaining the condition that meets.The invention enables dry plate disk brake friction elements by original static Experience Design, develops into dynamic digital design, greatly facilitates engineering staff.
Description
Technical field
The invention belongs to endless-track vehicle transmission field brake dynamic design technical fields, and in particular to a kind of disc type brake
Device friction element torque adaptation design method.
Background technology
High-energy density friction driven system is the key that high performance power transmission, continuous with height, higher with car speed
Working condition while improving mobility performance, the challenge of bigger is also brought for the braking of transmission system.Which disk
Formula brake is noteworthy characterized by that power is big, rotating speed is high.Since vehicle travel process is the process of dynamic change, brake start
Process contains friction loss, the factors such as load unevenness and concussion impact toward contact.This gives brake, especially its core
The design of part --- friction element brings difficulty.The design of this part at present still use it is traditional it is static, with experience be
Main passive design, such design method tend not to the needs for meeting brake real work, brake mistake usually occur
The problems such as heat, braking torque decline, friction plate ablation, brake vibrates.This is all mainly since brake design is unreasonable, in fact
Caused by the operating condition overrunning brake design objective of border.But increases brake indices simply and not only increase braking
The volume and weight of device, the performance for also making friction element extra cannot use, and often bring waste.So in the past with
It far can not have been met the requirements by means of the design method based on experience.
Invention content
The technical problem to be solved in the present invention is：Overcome the deficiencies in the prior art, solve existing brake design technology with
The problem of Static Design process based on experience, a kind of matched brake friction Design Method of Fixture Elements of dynamic torque is provided, is made
It obtains the problem of pressure loss caused by loading procedure influences brake design to be resolved, optimizes the design process of brake,
Brake can be effectively reduced and provide the problems such as insufficient using process braking torque.
The technology of the present invention solution is as follows：
A kind of disk brake friction element torque adaptation design method realizes that steps are as follows：
Step 1: by calculating vehicle and the brake force on ground and the performance parameter of on-position, including：The braking on ground
Power Fb, engine brake force Fez, ground deformation resistance Fd, windage FkWith transmission system resistance Fc, determine the work fortune of brake
Total brake force F in rowz, determine the transmission ratio i from brake to driving wheelcWith the equivalent redius r of brakezAnd it calculates and obtains
Obtain torque M；
Step 2: determine friction pairs of brake number Z according to brake structural, the contact area A of brake friction element and
Friction coefficient μ between brake friction element.
Step 3: the equivalent redius for the brake being had determined according to above-mentioned brake, number of friction pairs, transmission ratio, contact
The parameters such as area and friction coefficient.Point of the pressure p on the unit area of brake friction element is determined by finite element simulation
Cloth rule, the friction pair pressing force to integrate the brake for determining brake on-load pressure F additive processes by surface reduce
Coefficient C；
Step 4: the friction pair pressing force after being superimposed according to above-mentioned on-load pressure F reduces the member that rubs in coefficient C and step 3
Pressure p on the unit area of part calculates the torque that brake friction element is capable of providing by following formula：
[M]=μ pArzZC
P is the pressure on the unit area of brake friction element, unit MPa；A is the contact of brake friction element
Area, C, which is the friction pair pressing force of brake, reduces coefficient, rzIt is the equivalent redius of brake, Z is the friction pair of friction element
Number, friction coefficient of the μ between brake friction element.
Step 5: according to the braking determined in the running torque M of brake operation and step 4 determined in step 1
The torque [M] that device friction element is capable of providing checks whether torque meets condition by following formula：
M≤[M]
If cannot meet the requirements, can suitably modified brake equivalent redius rz, number of friction pairs Z, brake transmission ratio
ic, the parameters such as friction minor face product A, until reaching design objective.
In the step 1, the method for determining the total brake force of brake and torque is：
Fz=Fb+Fez+Fd+Fk+Fc
FbRepresent brake force, the F on groundezThe brake force of engine, FdGround deformation resistance, FkWindage and FcTransmission system
Several aspects such as resistance, FzIt is total brake force,For the force of sliding friction of wheel, m is vehicle mass, and g is acceleration of gravity,For the coefficient of sliding friction of wheel and ground.According to power and torque conversion relation, being converted to the brake force generated at driving wheel can
To be expressed as：
Fz=ic·M/rz
Torque M is obtained to calculate.
In the step 3, determine that the secondary pressing force of the friction of the brake of on-load pressure F additive processes reduces the side of coefficient C
Method is：
Vector sum of the power not under overlapping feature is obtained, nonoverlapping feature includes：The direction of power and the weight of position
Close, summed by excluding the stress of identical overlapping feature to which remaining power to be carried out to the vector of three dimensions, then according to
The friction pair pressing force that lower formula finds out brake reduces coefficient C.
Wherein R1For the inside radius of brake, R2For the outer radius of brake, rzFor the equivalent redius of brake, E* is to rub
Element elastic modulus is wiped, F is on-load pressure, and gaps of the h between friction element, α is the on-load pressure F and axis side after superposition
To angle.
The advantages of the present invention over the prior art are that：The present invention is no longer rely on traditional design process and needs to propose such as
Safety coefficient, original not realistic hypothesis coefficient such as empirical coefficient, but pressure is obtained by finite element simulation technology
The decaying of pressure is calculated after distribution, and proposes the design parameter after optimization, it is this to more accurate than traditional design
Disk brake friction element torque matching process can not only meet design and need and will not excessively be protected due to designer
It keeps and results in waste of resources.
Description of the drawings
Fig. 1 is the method for the present invention implementation flow chart；
Fig. 2 is brake structural 3D models in the present invention；Wherein a is chlamydate brake structural；B is uncanned system
Dynamic device structure；
Fig. 3 is brake bush pressure cloud charts of the present invention；Wherein a is from first friction element of upper number；B is
Two friction elements, c are third piece friction elements.
Specific implementation mode
Present disclosure is further illustrated with reference to specific design example：
As shown in Figure 1, step of the present invention is specifically described.
Disk brake friction element braking process, the heat that when friction generates mainly are inhaled by the structural detail of brake
It receives, another part heat is directly dissipated in air.Brake in this example is pressurizeed using tray type structure, braking torque
Low to the susceptibility of friction coefficient, core design index is braking torque.
Step 1: by calculating vehicle and the brake force on ground and the performance parameter of on-position, including：The braking on ground
Power Fb, engine brake force Fez, ground deformation resistance Fd, windage FkWith transmission system resistance Fc, determine the work fortune of brake
Total brake force F in rowz。
The brake force on ground must satisfy attachment condition, i.e.,：
Wherein, according to the operation conditions of vehicle, it is determined that m=30 tons, g=9.8m/s2,It calculates and obtains FbIt is less than
Equal to 58800N, F is taken hereb=40000N, Fez=12000N, Fd=5000N, Fk=2000N and Fc=500N.Then by such as
Lower formula calculates FzFor 59500N.
Fz=Fb+Fez+Fd+Fk+Fc
Rotation ratio i between brake and driving wheelc=11.2, the equivalent redius r of brakez=0.2m：
Fz=ic·M/rz
Then calculate the torque M=1062.5Nm of acquisition.
Step 2: determine friction pairs of brake number Z according to brake structural, the contact area A of brake friction element and
Friction coefficient μ between brake friction element.For brake structural as shown in Fig. 2, a is the structure chart there are shell, b is to remove
The internal structure chart of shell.It is 2 by number of friction pairs known to analysis, the contact area A=of brake device friction element
44800mm2.Since brake friction element is sintered metal product, thus by query material handbook its friction coefficient μ=
0.25 or so.
Step 3: the equivalent redius for the brake being had determined according to above-mentioned brake, number of friction pairs, transmission ratio, contact
The parameters such as area and friction coefficient.Point of the pressure p on the unit area of brake friction element is determined by finite element simulation
Cloth rule, the friction pair pressing force to integrate the brake for determining brake on-load pressure F additive processes by surface reduce
Coefficient C；
With reference to figure 2b, according to brake structural, from top to bottom each component is：Moving member-pressure plate-spring lower cover-the first rubs
Wipe the-the second friction element of element-third friction element-bottom plate.Assembling process pedestal is fixed, and friction element can be rotated with pedestal
It can move axially, then install the shell of brake additional, become as shown in a in Fig. 2.
Stopper material defines：
Pressurize plate material Steel material, elasticity modulus 2e20, density 7850, Poisson's ratio 0.3
Friction element is powder metallurgy, elasticity modulus 1.76e11, density 7850, Poisson's ratio 0.3
Other steel disc material Steel materials, elasticity modulus 2e11, density 7850, Poisson's ratio 0.3
The pressure distribution of each contact surface of friction element is obtained by finite element loaded tooth contact analysis, typically
Cloud atlas is as shown in figure 3, a, b, c are followed successively by the Pressure Simulation cloud atlas of the first, second, and third friction element.It is pressed by each surface
The regularities of distribution that the difference of power distribution can carry out pressure p on the unit area of friction element calculate, and calculating can be according to
Comprehensive characterization method integrates the pressure on each surface, obtains the power on each surface, then folds the power on each surface
The coincidence redundant force by the direction of power and position is added to delete, by excluding the stress of identical overlapping feature thus by remaining power
The vector summation for carrying out three dimensions, obtains vector sum of the power not under overlapping feature.
Then the friction pair pressing force of brake is found out according to following formula reduces coefficient C.
Wherein R1=0.18m, R2=0.22m, rz=0.2m, E*=1.76e11, F=3321N are to integrate and pass through superposition
On-load pressure afterwards, h=0.02m, α=16 ° are the angle of the on-load pressure F and axis direction after superposition.By calculating acquisition
Pressure reduction coefficient is：0.63.
Step 4: the friction pair pressing force after being superimposed according to above-mentioned on-load pressure F reduces the member that rubs in coefficient C and step 3
Pressure p on the unit area of part calculates the torque that brake friction element is capable of providing by following formula：
[M]=μ pArzZC
It brings above each data into, calculates and obtain [M]=1108.8Nm.
Step 5: according in the running torque M=1062.5Nm of brake operation and step 4 determined in step 1
Torque [M]=1108.8Nm that determining brake friction element is capable of providing checks whether torque meets by following formula
Condition：
M≤[M]
It can be seen that present invention design can meet the checking conditions of torque.If cannot meet the requirements, suitably modified can brake
The equivalent redius r of devicez, number of friction pairs Z, brake transmission ratio ic, the friction minor face product parameters such as A are until reaching design objective
Only.
If not having ignored load then in loading procedure according to traditional Static Design using the design method
Degenerative process, then accounted for by safety coefficient, then designed result is：
M·S≤[M]*=μ pArzZ
Wherein S is safety coefficient, herein designer due to without reference to, so must empirically be judged,
Generally than S=2 can be given if more conservative, if from economic considerations, S=1.2 can be given.But pass through above example
It can be seen that pressure loss C=0.63, it is practical by convert that is safety coefficient into 1.5873.So if not having
With the application of the invention, can cause to waste when S takes 2 according to traditional Static Design, design it is overly conservative, can be made when S takes 1.2
Index request is not achieved during the work time at torque.And after applying the present invention, by effective dynamic design, can see
It is S=1.5873 to design result, this is the design result that original traditional calculations can not be provided accurately.
So by above example and comparison as can be seen that the present invention no longer needs to propose such as according to traditional design process
Original not realistic hypothesis coefficient such as safety coefficient is designed, but obtains pressure point by finite element simulation technology
The decaying of pressure is calculated after cloth state, and proposes the design parameter after optimization, to more accurate than traditional design.
The content that description in the present invention is not described in detail belongs to the prior art well known to professional and technical personnel in the field.
Above example is provided just for the sake of the description purpose of the present invention, and is not intended to limit the scope of the present invention.This
The range of invention is defined by the following claims.It does not depart from spirit and principles of the present invention and the various equivalent replacements made and repaiies
Change, should all cover within the scope of the present invention.
Claims (3)
1. a kind of disk brake friction element torque adaptation design method, which is characterized in that include the following steps：
Step 1: calculating vehicle and the brake force on ground and the performance parameter of on-position, the performance parameter include：Ground
Brake force Fb, engine brake force Fez, ground deformation resistance Fd, windage FkWith transmission system resistance Fc, determine the work of brake
Make running total brake force Fz, determine the transmission ratio i from brake to driving wheelcWith the equivalent redius r of brakez, and count
It calculates and obtains the running torque M of brake operation；
Step 2: according to structure determination the friction pairs of brake number Z, the contact area A and system of brake friction element of brake
Friction coefficient μ between dynamic device friction element；
Step 3: according to the equivalent redius r of brakez, friction pairs of brake number Z, the transmission ratio i from brake to driving wheelc、
Friction coefficient μ between the contact area A and brake friction element of brake friction element, it is true by finite element simulation method
Determine the regularity of distribution of the pressure p on the unit area of brake friction element, adding for brake is determined to be integrated by surface
Carrying the friction pair pressing force of the brake of pressure F additive processes reduces coefficient C；
Step 4: reducing the pressure p on coefficient C and unit area according to the secondary pressing force of friction, is calculated and braked by following formula
The torque [M] that device friction element is capable of providing：
[M]=μ pArzZC
Step 5: the torque being capable of providing for the running torque M of the brake operation and the brake friction element
[M] judges whether to meet the following conditions by following formula：
M≤[M]
If conditions above cannot be met, the equivalent redius r of brake is changedz, friction pairs of brake number Z, brake transmission ratio
ic, friction minor face accumulates A parameters, until reaching conditions above, that is, until reaching design objective.
2. a kind of disk brake friction element torque adaptation design method according to claim 1, it is characterised in that：Institute
It states in step 1, determines total brake force FzMethod with the running torque M of brake operation is：
Fz=Fb+Fez+Fd+Fk+Fc
FbRepresent brake force, the F on groundezThe brake force of engine, FdGround deformation resistance, FkWindage and FcTransmission system resistance,
FzIt is total brake force,For the force of sliding friction of wheel, m is vehicle mass, and g is acceleration of gravity,For wheel and ground
The coefficient of sliding friction；According to power and torque conversion relation, it is converted to the brake force generated at brake and is expressed as：
Fz=ic·M/rz
The running torque M of brake operation is obtained to calculate.
3. a kind of disk brake friction element torque adaptation design method according to claim 1, it is characterised in that：Institute
It states in step 3, determines that the method that the secondary pressing force of the friction of the brake of on-load pressure F additive processes reduces coefficient C is：
Vector sum of the power not under overlapping feature is obtained, nonoverlapping feature includes：The direction of power and the coincidence of position are led to
It crosses and excludes the stress of identical overlapping feature to which the vector that remaining power is carried out to three dimensions is summed, then according to following formula
Finding out the friction pair pressing force of brake reduces coefficient C：
Wherein R1For the inside radius of brake, R2For the outer radius of brake, E* is friction element elasticity modulus, and h is friction element
Between gap, α be superposition after on-load pressure F and brake axis direction angle.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810127262.2A CN108376191B (en) | 2018-02-08 | 2018-02-08 | Torque matching design method for friction element of disc brake |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810127262.2A CN108376191B (en) | 2018-02-08 | 2018-02-08 | Torque matching design method for friction element of disc brake |
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| CN108376191B CN108376191B (en) | 2020-11-06 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109115680A (en) * | 2018-08-29 | 2019-01-01 | 北京航空航天大学 | A kind of conical friction element equivalent friction factor evaluation method |
| CN114021411A (en) * | 2021-11-11 | 2022-02-08 | 南方天合底盘系统有限公司 | Method for calculating pressure center position value of fixed caliper type automobile brake block |
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| US20150204398A1 (en) * | 2012-07-24 | 2015-07-23 | Haisheng Qiang | Dual-directions braking method of disc brake, braking mechanism and application thereof |
| CN106814029A (en) * | 2017-01-13 | 2017-06-09 | 北京航空航天大学 | A kind of many band integration disk-type friction pair frictional behaviour Forecasting Methodologies |
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| US20150204398A1 (en) * | 2012-07-24 | 2015-07-23 | Haisheng Qiang | Dual-directions braking method of disc brake, braking mechanism and application thereof |
| CN106814029A (en) * | 2017-01-13 | 2017-06-09 | 北京航空航天大学 | A kind of many band integration disk-type friction pair frictional behaviour Forecasting Methodologies |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109115680A (en) * | 2018-08-29 | 2019-01-01 | 北京航空航天大学 | A kind of conical friction element equivalent friction factor evaluation method |
| CN114021411A (en) * | 2021-11-11 | 2022-02-08 | 南方天合底盘系统有限公司 | Method for calculating pressure center position value of fixed caliper type automobile brake block |
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