CN109383255A - A kind of superduty chassis independent suspension electric drive axle - Google Patents
A kind of superduty chassis independent suspension electric drive axle Download PDFInfo
- Publication number
- CN109383255A CN109383255A CN201811108722.3A CN201811108722A CN109383255A CN 109383255 A CN109383255 A CN 109383255A CN 201811108722 A CN201811108722 A CN 201811108722A CN 109383255 A CN109383255 A CN 109383255A
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- Prior art keywords
- cross arm
- lower cross
- arm assembly
- coordinate
- electric drive
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/14—Torque-transmitting axles composite or split, e.g. half- axles; Couplings between axle parts or sections
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
- B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
- B60G11/30—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs having pressure fluid accumulator therefor, e.g. accumulator arranged in vehicle frame
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/18—Resilient suspensions for a single wheel with two or more pivoted arms, e.g. parallelogram
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
- B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2200/00—Indexing codes relating to suspension types
- B60G2200/10—Independent suspensions
- B60G2200/14—Independent suspensions with lateral arms
-
- 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
- B60G2202/154—Fluid spring with an accumulator
Abstract
A kind of superduty chassis independent suspension electric drive axle, including two driving units in left and right and suspension system, each driving unit include motor, reduction gearbox, semiaxis, wheel group；Each suspension system includes oil and gas spring and guiding mechanism, and guiding mechanism includes Top Crossbeam assembly, lower cross arm assembly；Input of the output of motor as reduction gearbox, the output of reduction gearbox connect semiaxis one end, the other end fifth wheel group of semiaxis；It is connect, and can be swung in YZ plane around pin shaft with vehicle frame by pin shaft on the inside of upper, lower horizontal arm assembly；It is connect respectively by flexural pivot with the upper lower interface of wheel group on the outside of upper lower cross arm assembly, the freedom degree that wheel can be achieved and move up and down and swing is provided by flexural pivot；The aperture on lower cross arm assembly, for installing oil and gas lower spring end, the upper end of oil and gas spring is connect with vehicle frame, and oil and gas spring is swung in YZ plane and XZ plane；The YZ plane is in the undefined coordinate plane of vehicle axis system.
Description
Technical field
The invention belongs to special vehicle chassis technologies.
Background technique
Electromechanical integration is necessity of modern development in science and technology as a result, having wide development scene.Electric drive axle is as machine
Product of the tool in conjunction with electronics, final developing direction are undoubtedly electromechanical integration, integrated.Integrated electric drive axle knot
Structure can not only accomplish volume minimum, but also can mention in the lightweight for guaranteeing to accomplish vehicle bridge while driving bridge reliability again
The economy of high vehicle guarantees the course continuation mileage that electricity is driven.
However drive in drive axle development process in electricity, the development of electric drive axle does not form a kind of motor, one of slowing down
The high reliability structure of the integrated level of change seriously constrains the popularization that electric especially heavy electricity of driving is driven.Therefore how to design
The problem of a kind of electric drive axle that the integrated integrated level of decelerating through motor is high is urgent need to resolve.
Summary of the invention
Technology of the invention solves the problems, such as: designing a kind of independent suspension electric drive axle, meets superduty chassis and use need
It asks.
The technical solution of the invention is as follows: a kind of superduty chassis independent suspension electric drive axle, including left and right two
Driving unit and suspension system, each driving unit include motor, reduction gearbox, semiaxis, wheel group；Each suspension system includes oil and gas
Spring and guiding mechanism, guiding mechanism include Top Crossbeam assembly, lower cross arm assembly；Input of the output of motor as reduction gearbox,
The output of reduction gearbox connects semiaxis one end, the other end fifth wheel group of semiaxis；Pass through pin shaft and vehicle on the inside of upper, lower horizontal arm assembly
Frame connection, and can be swung in YZ plane around pin shaft；Pass through the upper lower interface of flexural pivot and wheel group on the outside of upper lower cross arm assembly respectively
Connection is provided the freedom degree that wheel can be achieved and move up and down and swing by flexural pivot；The aperture on lower cross arm assembly, for pacifying
Charge of oil vapour lower spring end, the upper end of oil and gas spring are connect with vehicle frame, and oil and gas spring is put in YZ plane and XZ plane
It is dynamic；The YZ plane is in the undefined coordinate plane of vehicle axis system.
Further, motor and reduction gearbox are the integrated design for sharing end cap.
Further, the hydro-pneumatic spring includes cylinder barrel, piston, orifice valve, accumulator, upper journal, down journal；Lower branch
Ear and piston are connected, and cylinder barrel is covered in piston exterior, and cylinder barrel is double-layer structure, and orifice valve is arranged between two layers；Oil in cylinder barrel is logical
Pipeline is crossed to connect with the accumulator outside cylinder barrel；Upper journal is fixed with cylinder barrel；By the inert gas compression in accumulator and stretch
It opens and provides elastic force for suspension system, oil liquid flows through orifice valve and provides damping force for suspension system；Upper journal, down journal respectively with
Oscillating bearing, pin shaft mode connect with vehicle frame and lower cross arm assembly.
Further, opens outward is as deep as possible on the inside of it under the premise of meeting structural strength for the lower cross arm assembly
Gap.
Further, by the optimization to guiding mechanism hard spot, guarantee that the characteristic K&C of suspension is met the requirements；Pair
Optimization of the optimization of guiding mechanism hard spot including Top Crossbeam, the Y, Z coordinate of lower cross arm assembly medial center points.
Further, the optimization to guiding mechanism hard spot is realized especially by following manner: setting Top Crossbeam, under
The Y of transverse arm assembly medial center points, Z coordinate changes in coordinates range；One group of Top Crossbeam, lower cross arm are chosen within the scope of changes in coordinates
Y, the Z coordinate of assembly medial center points make wheel work under desired limiting condition, obtain for the coordinate of every group of selection
To the corresponding kingpin inclination of every group of coordinate, camber angle, wheelspan, height of roll center change curve；Therefrom choose stub
Four leaning angle, camber angle, wheelspan, height of roll center change curves are all satisfied corresponding Top Crossbeam when requiring, lower cross
Y, the Z coordinate of arm assembly medial center points.
Further, Top Crossbeam, the Y of lower cross arm assembly medial center points, Z coordinate changes in coordinates range specifically: upper cross
Arm assembly Z coordinate variation range is the upper interface Z coordinate ± 100mm of knuckle；Top Crossbeam assembly Y-coordinate variation range be A ±
100mm；The A is the half of vehicle frame upper longitudinal beam spacing.Lower cross arm assembly Z coordinate variation range is the lower interface Z of knuckle
Coordinate ± 100mm；Lower cross arm assembly Y-coordinate variation range is B ± 100mm；The B is the half of stringer spacing under vehicle frame.
Further, the gap shape is determined as follows:
The first step, according to the ultimate load under desired limiting condition, received at installation flexural pivot on the outside of lower cross arm assembly；It is right
The lower cross arm assembly of not open and clear mouth carries out structural Topology Optimization, determines optimal load transmission path；
Second step, open and clear mouth in the region formed on the inside of optimal load transmission path and lower cross arm；
Third step carries out structural strength and Sports Checking, if structural strength and movement interference are all satisfied requirement, when
Preceding gap is final gap；If structural strength meets, safety coefficient is required, movement interference is unsatisfactory for requiring, dry according to movement
Position or size that gap is changed at position in above-mentioned zone are related to, third step is re-executed；If structural strength is unsatisfactory for
Number requires, movement interference is met the requirements, then installs reinforcing rib on the inside of gap, re-execute third step；Or gap is reduced, weight
It is new to execute third step；If requirement is not satisfied in structural strength and movement interference, changes on the inside of lower cross arm assembly and connect with vehicle frame
Position spacing and lower cross arm assembly brachium, executed since the first step again.
Further, the Top Crossbeam assembly includes Top Crossbeam, metal bearing, oil sealing, metal gasket, positioning pin；Institute
The lower cross arm assembly stated is by lower cross arm, metal bearing, oil sealing, metal gasket, positioning pin；Setting pin on the inside of Top Crossbeam/lower cross arm
Shaft mounting hole, mounting hole is interior to install metal bearing, and metal bearing outer end installs oil sealing, installs metal gasket on the outside of oil sealing, and lead to
Cross the position of the fixed metal gasket of positioning pin.
Further, the end face of the prominent bearing pin mounting hole of the metal gasket thickness.
Further, the rotational angle of the flexural pivot is at least up to 40 °, and bearing capacity is not less than 20t.
The present invention has the beneficial effect that compared with prior art
The present invention adapts to vehicle electrical gasification and intelligence to improve multi-axle heavy type vehicle function efficiency and level of integrated system
The development trend of change designs a kind of electric drive axle equipped with independent suspension.
The use of electric drive axle, eliminate the gearbox of conventional truck transmission system, transfer case, main reducing gear, differential mechanism,
The systems such as longitudinal drive shaft or component, have simplified system structure significantly, save vehicle installation space；Electric drive axle by motor,
Reduction gearbox, semiaxis composition, level of integrated system is high, forms modular event driven unit, improves drive system flexibility ratio, can basis
Demand is flexibly equipped with.
Since multi-axle heavy type car load is big, the number of axle is more, applying working condition is complicated, using double cross arm independent suspension, pass through knot
Structure optimization design and use wide-angle flexural pivot meet the big stroke bounce demand of wheel；It is connected to and is designed by hydro-pneumatic spring, realized flat
The function of weighing apparatus axle load；It is designed by suspension system stiffness and damping Optimized Matching, guarantees that vehicle has good ride performance；It is logical
The optimization of guiding mechanism hard spot is crossed, makes suspension system that there is good K&C characteristic, guarantees that vehicle has good control stability.
Suspension system uses communication type hydro-pneumatic spring, designs unilateral hydro-pneumatic spring connection, before point left front, right, left back, right
Afterwards, vehicle uses four-point supporting, ensure that the load equalization between each axis of multiple-axle vehicle, and avoids single when driving in concave-convex road surface
The case where a tire is hanging or overloads.
Suspension system is furnished with hydro-pneumatic spring, is connected to accumulator in oil circuit, and the inert gas compression and extension in accumulator are
Suspension system provides elastic force；Hydro-pneumatic spring cylinder barrel is built-in by orifice valve, and oil liquid flows through orifice valve and provides damping for suspension system
Power；Comprehensively consider whole-car parameters, vehicle body offset frequency, driving cycle, Proper Match design is carried out to stiffness and damping, there is vehicle good
Good ride performance.
Electric drive axle is furnished with double cross arm independent suspension, is meeting superduty chassis to bearing capacity, the special need of driving cycle
While asking, there is good passability and control stability.
Electricity drives bridge and is furnished with hub reduction type wheel group, and power reaches wheel group by semiaxis, slows down torque increase through Wheel-side planetary reducer
After be transferred to wheel, realize driving of the motor to wheel.
Detailed description of the invention
Fig. 1 is principle of the invention figure；
Fig. 2 is schematic diagram of the present invention；
Fig. 3 is Top Crossbeam assembly diagram of the present invention；
Fig. 4 is lower cross arm assembly diagram of the present invention；
Fig. 5 is suspension system assembling schematic diagram of the present invention；
Fig. 6 is suspension kinematical simulation model schematic diagram of the present invention；
Fig. 7 is the upper and lower transverse arm topological optimization result figure of the present invention；
Fig. 8 is the upper and lower transverse arm strength Calculation Result figure of the present invention；
Fig. 9 is hydro-pneumatic spring structural schematic diagram of the present invention.
Specific embodiment
With reference to the accompanying drawing and example elaborates to the present invention.
As shown in Figure 1, 2, a kind of superduty chassis independent suspension electric drive axle, the form that electric drive axle uses axis to drive,
Including two driving units in left and right and suspension system；Left and right sides driving unit individually controls, and can be provided according to duty requirements different
Torque and revolving speed, realize full wheel independent control driving, considerably increase drive system freedom degree；
Each driving unit includes motor 11, reduction gearbox 12, semiaxis 13, wheel group 14；Motor and reduction gearbox carry out sharing end
The integrated design of lid improves level of integrated system, reduces installation space；Each suspension system includes oil and gas spring 15 and Guiding machine
Structure, guiding mechanism include Top Crossbeam assembly 16, lower cross arm assembly 17；Input of the output of motor as reduction gearbox, reduction gearbox
Output connection semiaxis one end, the other end fifth wheel group of semiaxis；It is connect by pin shaft with vehicle frame on the inside of upper, lower horizontal arm assembly,
And it can be swung in YZ plane around pin shaft；It is connect respectively by flexural pivot with the upper lower interface of wheel group on the outside of upper lower cross arm assembly, by
Flexural pivot, which provides, can be achieved the freedom degree that wheel moves up and down and swings；The aperture on lower cross arm assembly, for installing oil and gas
The upper end of lower spring end, oil and gas spring is connect with vehicle frame, and oil and gas spring is swung in YZ plane and XZ plane；It is described
YZ plane be in the undefined coordinate plane of vehicle axis system.Hydro-pneumatic spring upper and lower end is divided in a manner of oscillating bearing+pin shaft
It is not connect with vehicle frame, lower cross arm, oil cylinder caused by oscillating bearing is avoided because of the non-coaxial power of hydro-pneumatic spring piston and cylinder barrel damages
It is bad.
Motor gives motor that control signal, motor output power is added in the case where obtaining electric situation, and power reaches deceleration by motor
Case is transferred to wheel group 4 after the epicyclic gear train deceleration torque increase in reduction gearbox, then through semiaxis, and then drives vehicle driving.
Guiding mechanism includes Top Crossbeam assembly and lower cross arm assembly.Top Crossbeam assembly by Top Crossbeam, metal bearing, oil sealing,
Metal gasket, pin bank at, lower cross arm assembly by lower cross arm, metal bearing, oil sealing, metal gasket, pin bank at.In upper and lower transverse arm
Side is connect by pin shaft with vehicle frame, and transverse arm can be swung in YZ (vehicle axis system) plane around pin shaft；Pass through on the outside of upper lower cross arm
Flexural pivot is connect with wheel group, provides the freedom degree that achievable wheel moves up and down and swings.By to guiding mechanism hard spot
Optimization, the wheel alignment parameter and height of roll center variation when moving up and down wheel are small as far as possible, and it is good to guarantee that suspension has
Characteristic K&C, and then make vehicle have good control stability.Suspension Top Crossbeam, lower cross arm are carried out according to hard spot information
Three-dimensional preliminary design, then uses Topology Optimization Method, optimizes to cross arm structure, under the premise of guaranteeing use intensity,
Meet light-weighted design requirement.
Fig. 3 is the Top Crossbeam assembly of the guiding mechanism for superduty chassis independent suspension, and Top Crossbeam assembly 16 is by upper cross
Arm 1, metal bearing 5, oil sealing 4, metal gasket 3, pin 2 form.Top Crossbeam is Steel material, meets the design strength under shock loading
It is required that；Metal bearing is copper product, in addition the lubricating action of lubricating grease, can greatly reduce the friction mill between transverse arm and pin shaft
Damage；Oil sealing plays sealing function, not only prevents oil seepage, but also has separated extraneous dust, water etc. and entered metal bearing and pin shaft
Between；Metal gasket play the role of protect oil sealing, in addition, it is often more important that allow metal gasket thickness protrude from transverse arm end face with
With support assorted；Pin is used to for metal gasket being fixed on transverse arm end face.
Fig. 4 is the lower cross arm assembly of the guiding mechanism for superduty chassis independent suspension, and lower cross arm assembly 17 is by lower cross
Arm 6, metal bearing 10, oil sealing 9, metal gasket 8, pin 7 form, and the effect of each of which components is identical as Top Crossbeam assembly.Under
Transverse arm assembly and vehicle frame connecting pin are equipped with metal gasket, the outside of supporting leg and support assorted in the outside of two supporting legs.In lower cross
An elongated hole is provided at arm shoulder, for installing spring down journal.
Fig. 5 is suspension system installation diagram, is connect by pin shaft with bracket on the inside of Top Crossbeam assembly, can be around X-axis (vehicle coordinate
System) it makes rotating motion；It is connect, can be made rotating motion around X-axis, Z axis with wheel group by flexural pivot on the outside of Top Crossbeam, realize wheel or more
Bounce and left and right turn movement；Lower cross arm assembly inner and outer is identical in structure and forms of motion as Top Crossbeam assembly, only
It is during wheel hop, hydro-pneumatic spring can make small sway in lower cross arm elongated hole.
Fig. 6 is suspension kinematical simulation model.Upper and lower transverse arm is simulated by quality bar, on the inside of transverse arm by revolute with
Vehicle frame connection, transverse arm outside are connect by typed ball bearing pair with wheel group；Hydro-pneumatic spring is simulated by the quality bar of two relative motions, oil
Gas spring lower end is connect by typed ball bearing pair with lower cross arm, and upper end is connect by typed ball bearing pair with vehicle frame, hydro-pneumatic spring piston and cylinder body
Between pass through cylindrical pair connect；The movement of wheel and guiding mechanism is realized in the connection of above each structure and kinematic pair.Above and below suspension
The flexural pivot that polarizers of big angle scope is used between transverse arm and wheel group has wheel and turns to freedom degree, while meeting the big stroke of wheel and jumping
Dynamic demand guarantees wheel when jumping extreme position above and below, and flexural pivot corner has certain design in its tolerance zone
Surplus.The rotational angle of flexural pivot is at least up to 40 °, and bearing capacity is not less than 20t.
Using suspension kinematical simulation model, wheel alignment parameter and height of roll center when being moved up and down with wheel become
Changing small as far as possible is optimization aim, by the optimization to guiding mechanism hard spot, guarantees that suspension has good characteristic K&C, and then make
Vehicle has good control stability.Specific Optimization Steps are as follows:
(1) Top Crossbeam, the Y of lower cross arm assembly medial center points, Z coordinate changes in coordinates range are set:
Top Crossbeam assembly Z coordinate variation range is the upper interface Z coordinate ± 100mm of knuckle；Top Crossbeam assembly Y-coordinate becomes
Change range is A ± 100mm；The A is the half of vehicle frame upper longitudinal beam spacing.Lower cross arm assembly Z coordinate variation range is to turn to
Lower interface Z coordinate ± the 100mm of section；Lower cross arm assembly Y-coordinate variation range is B ± 100mm；The B is stringer under vehicle frame
The half of spacing.
(2) Y, the Z coordinate that one group of Top Crossbeam, lower cross arm assembly medial center points are chosen within the scope of changes in coordinates, for
The coordinate of every group of selection makes wheel work under desired limiting condition, obtain the corresponding kingpin inclination of every group of coordinate,
Camber angle, wheelspan, height of roll center change curve；Therefrom choose kingpin inclination, camber angle, wheelspan, inclination
Four change curves of centre-height are all satisfied Y, the Z coordinate of corresponding Top Crossbeam when requiring, lower cross arm assembly medial center points.
Lower cross arm assembly opens outward gap as deep as possible on the inside of it, gap shape under the premise of meeting structural strength
It is determined as follows:
The first step, according to the ultimate load under desired limiting condition, received at installation flexural pivot on the outside of lower cross arm assembly；It is right
The lower cross arm assembly of not open and clear mouth carries out structural Topology Optimization, determines optimal load transmission path；Fig. 7 is upper and lower transverse arm topology
Optimized model, material model use density variable method (SIMP method).
Second step, open and clear mouth in the region formed on the inside of optimal load transmission path and lower cross arm assembly；
Third step carries out structural strength and Sports Checking, if structural strength and movement interference are all satisfied requirement, when
Preceding gap is final gap；If structural strength meets, safety coefficient is required, movement interference is unsatisfactory for requiring, dry according to movement
Position or size that gap is changed at position in above-mentioned zone are related to, third step is re-executed；If structural strength is unsatisfactory for
Number requires, movement interference is met the requirements, then installs reinforcing rib on the inside of gap, re-execute third step；Or gap is reduced, weight
It is new to execute third step；If requirement is not satisfied in structural strength and movement interference, changes on the inside of lower cross arm assembly and connect with vehicle frame
Position spacing and lower cross arm assembly brachium, executed since the first step again.
Cell density indicates that the material at the cell position is critically important for 1 after Optimization Solution, needs to retain, cell density leans on
Nearly 0 indicates that the material at the cell position is inessential, can remove, so that the high efficiency for reaching material utilizes, realizes that structure is light
Quantitative design makes upper, lower horizontal arm configuration obtain more reasonable material distribution and Path of Force Transfer after topological optimization.It is set in satisfaction
Under the premise of meter requires, subtracts complete vehicle weight as far as possible, improve the service performances such as the mobility, cross-country power, reliability of vehicle.
Fig. 8 is upper and lower transverse arm stress diagram, for calculating whether typical condition lower cross arm intensity meets the requirements；It is calculated
Operating condition includes 3 times of static load operating conditions, emergency braking operating condition and rollover condition, it is desirable that the upper and lower transverse arm Strength Safety system of every kind of operating condition
Number is not less than 2；If transverse arm local stress is unsatisfactory for intensity requirement, optimization need to be iterated to transverse arm, until meeting intensity requirement.
As shown in figure 9, hydro-pneumatic spring 15 includes cylinder barrel 151, piston 152, orifice valve 153, accumulator 154, upper journal
155, down journal 156；Down journal and piston are connected, and cylinder barrel is covered in piston exterior, and cylinder barrel is double-layer structure, and resistance is arranged between two layers
Buddhist nun's valve；Oil in cylinder barrel is connect by pipeline with the accumulator outside cylinder barrel；Upper journal is fixed with cylinder barrel；By in accumulator
Inert gas, which is compressed and upheld, provides elastic force for suspension system, and oil liquid flows through orifice valve and provides damping force for suspension system；On
Trunnion, down journal are connect in a manner of oscillating bearing, pin shaft with vehicle frame and lower cross arm assembly respectively.
Unspecified part of the present invention belongs to common sense well known to those skilled in the art.
Claims (11)
1. a kind of superduty chassis independent suspension electric drive axle, it is characterised in that: including two driving units in left and right and suspension
System, each driving unit include motor, reduction gearbox, semiaxis, wheel group；Each suspension system includes oil and gas spring and Guiding machine
Structure, guiding mechanism include Top Crossbeam assembly, lower cross arm assembly；Input of the output of motor as reduction gearbox, the output of reduction gearbox
Connect semiaxis one end, the other end fifth wheel group of semiaxis；It is connect by pin shaft with vehicle frame on the inside of upper, lower horizontal arm assembly, and can
It is swung in YZ plane around pin shaft；It is connect respectively by flexural pivot with the upper lower interface of wheel group on the outside of upper lower cross arm assembly, by flexural pivot
It provides and the freedom degree that wheel moves up and down and swings can be achieved；The aperture on lower cross arm assembly, for installing oil and gas spring
The upper end of lower end, oil and gas spring is connect with vehicle frame, and oil and gas spring is swung in YZ plane and XZ plane；The YZ
Plane is in the undefined coordinate plane of vehicle axis system.
2. electric drive axle according to claim 1, it is characterised in that: motor and reduction gearbox are to share the integration of end cap to set
Meter.
3. electric drive axle according to claim 1, it is characterised in that: the hydro-pneumatic spring includes cylinder barrel, piston, damping
Valve, accumulator, upper journal, down journal；Down journal and piston are connected, and cylinder barrel is covered in piston exterior, and cylinder barrel is double-layer structure, and two layers
Between orifice valve is set；Oil in cylinder barrel is connect by pipeline with the accumulator outside cylinder barrel；Upper journal is fixed with cylinder barrel；Pass through
Inert gas compression and extension in accumulator provide elastic force for suspension system, and oil liquid flows through orifice valve and provides for suspension system
Damping force；Upper journal, down journal are connect in a manner of oscillating bearing, pin shaft with vehicle frame and lower cross arm assembly respectively.
4. electric drive axle according to claim 1, it is characterised in that: the lower cross arm assembly is meeting structural strength
Under the premise of on the inside of it opens outward gap as deep as possible.
5. electric drive axle according to claim 1, it is characterised in that: by the optimization to guiding mechanism hard spot, guarantee outstanding
The characteristic K&C of frame is met the requirements；Described includes Top Crossbeam, lower cross arm assembly medial center points to the optimization of guiding mechanism hard spot
Y, Z coordinate optimization.
6. electric drive axle according to claim 5, it is characterised in that: the optimization to guiding mechanism hard spot is specifically led to
Cross following manner realization: setting Top Crossbeam, the Y of lower cross arm assembly medial center points, Z coordinate changes in coordinates range；Become in coordinate
Change Y, the Z coordinate for choosing one group of Top Crossbeam, lower cross arm assembly medial center points in range, makes wheel for the coordinate of every group of selection
It works under desired limiting condition, obtains the corresponding kingpin inclination of every group of coordinate, camber angle, wheelspan, inclination
Centre-height change curve；Therefrom choose kingpin inclination, camber angle, four wheelspan, height of roll center change curves
It is all satisfied Y, the Z coordinate of corresponding Top Crossbeam when requiring, lower cross arm assembly medial center points.
7. electric drive axle according to claim 6, it is characterised in that: Y, Z of Top Crossbeam, lower cross arm assembly medial center points
Coordinates variation range specifically: Top Crossbeam assembly Z coordinate variation range is the upper interface Z coordinate ± 100mm of knuckle；On
Transverse arm assembly Y-coordinate variation range is A ± 100mm；The A is the half of vehicle frame upper longitudinal beam spacing.Lower cross arm assembly Z coordinate
Variation range is the lower interface Z coordinate ± 100mm of knuckle；Lower cross arm assembly Y-coordinate variation range is B ± 100mm；Described
B is the half of stringer spacing under vehicle frame.
8. electric drive axle according to claim 4, it is characterised in that: the gap shape is determined as follows:
The first step, according to the ultimate load under desired limiting condition, received at installation flexural pivot on the outside of lower cross arm assembly；To not opening
The lower cross arm assembly of gap carries out structural Topology Optimization, determines optimal load transmission path；
Second step, open and clear mouth in the region formed on the inside of optimal load transmission path and lower cross arm；
Third step carries out structural strength and Sports Checking, current to slit if structural strength and movement interference are all satisfied requirement
Mouth is final gap；If structural strength meets, safety coefficient is required, movement interference is unsatisfactory for requiring, according to movement interference portion
Position or the size of gap are changed in position in above-mentioned zone, re-execute third step；It is wanted if structural strength is unsatisfactory for safety coefficient
Ask, movement interference is met the requirements, then reinforcing rib is installed on the inside of gap, re-execute third step；Or gap is reduced, it holds again
Row third step；If requirement is not satisfied in structural strength and movement interference, the position connecting on the inside of lower cross arm assembly with vehicle frame is changed
The brachium for setting spacing and lower cross arm assembly, executes since the first step again.
9. electric drive axle according to claim 1, it is characterised in that: the Top Crossbeam assembly includes Top Crossbeam, metal
Bearing, oil sealing, metal gasket, positioning pin；The lower cross arm assembly is by lower cross arm, metal bearing, oil sealing, metal gasket, fixed
Position pin；Bearing pin mounting hole is set on the inside of Top Crossbeam/lower cross arm, metal bearing, metal bearing outer end installation oil are installed in mounting hole
Metal gasket is installed in envelope, oil sealing outside, and passes through the position of the fixed metal gasket of positioning pin.
10. electric drive axle according to claim 9, it is characterised in that: the prominent pin shaft installation of the metal gasket thickness
The end face in hole.
11. electric drive axle according to claim 1, it is characterised in that: the rotational angle of the flexural pivot is at least up to
40 °, bearing capacity is not less than 20t.
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| CN201811108722.3A Pending CN109383255A (en) | 2018-09-21 | 2018-09-21 | A kind of superduty chassis independent suspension electric drive axle |
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