CN105799443B - The quantitative pump truck appearance regulating system of single group single-acting cylinder - Google Patents
The quantitative pump truck appearance regulating system of single group single-acting cylinder Download PDFInfo
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- CN105799443B CN105799443B CN201610171841.8A CN201610171841A CN105799443B CN 105799443 B CN105799443 B CN 105799443B CN 201610171841 A CN201610171841 A CN 201610171841A CN 105799443 B CN105799443 B CN 105799443B
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- 230000001105 regulatory effect Effects 0.000 title claims abstract description 27
- 239000000725 suspension Substances 0.000 claims abstract description 74
- 238000006073 displacement reaction Methods 0.000 claims abstract description 56
- 239000000203 mixture Substances 0.000 claims abstract description 13
- 239000003921 oil Substances 0.000 claims description 139
- 238000013016 damping Methods 0.000 claims description 22
- 239000010729 system oil Substances 0.000 claims description 6
- 230000035939 shock Effects 0.000 claims description 4
- 230000009514 concussion Effects 0.000 claims description 2
- 230000008054 signal transmission Effects 0.000 claims description 2
- 230000000903 blocking effect Effects 0.000 description 22
- 238000010586 diagram Methods 0.000 description 10
- 238000007599 discharging Methods 0.000 description 7
- 230000009471 action Effects 0.000 description 5
- 230000001276 controlling effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000002828 fuel tank Substances 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000033228 biological regulation Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 238000012544 monitoring process Methods 0.000 description 3
- 230000002457 bidirectional effect Effects 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000000605 extraction Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 230000003026 anti-oxygenic effect Effects 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000009355 double cropping Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 229910001095 light aluminium alloy Inorganic materials 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000004886 process control Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000004043 responsiveness Effects 0.000 description 1
- 238000012163 sequencing technique Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 208000016261 weight loss Diseases 0.000 description 1
- 230000004580 weight loss Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/0152—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/015—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements
- B60G17/019—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the type of sensor or the arrangement thereof
- B60G17/01941—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load the regulating means comprising electric or electronic elements characterised by the type of sensor or the arrangement thereof characterised by the use of piezoelectric elements, e.g. sensors or actuators
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The present invention relates to a kind of quantitative pump truck appearance regulating system of single group single-acting cylinder, by constant displacement pump main pressure control valve group, the first from left single-acting cylinder load-sensitive proportional throttle valve group, constant displacement pump and the first from left oleo-pneumatic suspension composition, wherein constant displacement pump with main pressure control valve group and the first from left single-acting cylinder load-sensitive proportional throttle valve group the sequential series between constant displacement pump and the first from left oleo-pneumatic suspension, the first from left single-acting cylinder is connected with the load pressure feedback control terminal of load-sensitive proportional throttle valve group with constant displacement pump with the control terminal of main pressure control valve group, make system in-line pressure higher 0.6Mpa~0.9Mpa than load pressure all the time.
Description
Technical field
The present invention relates to a kind of quantitative pump truck appearance regulating system of single group single-acting cylinder of oil gas hanging unwheeling appearance regulating system, category
In hydraulic machinery and road vehicle application field.
Background technology
By using oil-gas suspension technology, the handling stability energy and ride performance of vehicle greatly improved, solve tradition
The nonadjustable technical barrier of elastic element rigidity characteristic of suspension.It is but with the raising required vehicle transport power and steady to vehicle
Property, the raising of security, comfortableness requirement, the particularly larger storage transporting equipment of load change, how can guarantee that empty fully loaded
State car appearance governing speed is consistent, when how to ensure to adjust particularly under full load condition during height of the carbody regulation on loading thing put down
Surely, how to realize system high efficiency save, reduce loss in efficiency the problems such as, become current domestic vehicles production firm face and
All the time the technological difficulties that can not effectively solve, so modular cart appearance regulating system of the exploitation based on load-sensitive principle just seems
It is particularly necessary.
The content of the invention
According to an aspect of the present invention, there is provided a kind of modular cart appearance regulating system based on load-sensitive principle is right
The posture of vehicle is adjusted, and the system is by system dynamic source, hydraulic system (the hereinafter referred to as hydraulic pressure system based on load-sensitive principle
System), oleo-pneumatic suspension, electric control gear and sensor group into.System dynamic source, hydraulic system and oleo-pneumatic suspension are connected by pipeline
Connect, oleo-pneumatic suspension includes at least two left oleo-pneumatic suspensions and at least two right oleo-pneumatic suspensions, it is characterised in that：Hydraulic system includes
Main oily filter, oil return filter, fuel tank, main pressure control valve group, load-sensitive proportional throttle valve group, the accumulator with blocking function subtract
Valve group of shaking and all kinds of pipelines, joint etc. form.Main pressure control valve group includes overflow valve, two-bit triplet flow control valve, defibrillation
Valve, wherein overflow valve and two-bit triplet flow control valve are in parallel, and defibrillation valve passes through load pressure feed back loop and two three
Through-flow control valve control terminal is connected.The structures such as the throttle orifice that defibrillation valve passes through setting were carried out to system pressure feedback signal
Filter, realizes that the stabilization of system pressure and flow accurately controls；System maximum working pressure is limited by overflow valve, prevents superpressure from producing
Raw influence system safety；Two-bit triplet flow control valve is real by internal pressure balanced structure, control system actual working pressure
Existing system actual working pressure and the load of system highest are related in real time, reduce pressure loss during due to system zero load.Using quantitative
Pump and variable pump systems it is supporting main pressure control valve group composition be slightly different.
Load-sensitive proportional throttle valve group includes constant pressure difference control valve, proportional throttle valve, locking-valve, is mainly used in controlling stream
Amount, realizes the flow purpose unrelated with load.Wherein constant pressure difference control valve, proportional throttle valve, locking-valve are cascaded structure, fixed
Two pressure feedback control terminals of differential pressure control valve are connected in parallel at the oil inlet and outlet of proportional throttle valve respectively, for controlling ratio section
Flow valve inlet outlet pressure differential.For the sequencing connected between single-acting cylinder proportional throttle valve and constant pressure difference control valve, determine
Control the difference of oil circuit；One 3-position 4-way guiding valve of series connection can then be increased for double acting cylinder by controlling the speed of in-line
Reach the purpose of control oil return speed.For locking-valve between oleo-pneumatic suspension and other hydraulic valves, main function is locking oil gas
High-pressure in suspension, realize system high pressure locking.
Oleo-pneumatic suspension damper valve constitutes the accumulator vibration damping valve group with blocking function.Accumulator with blocking function
It is connected in parallel on after vibration damping valve group series connection accumulator between oleo-pneumatic suspension and load-sensitive proportional throttle valve group, for buffering faces car
The impact and absorption system hydraulic shock of body.
Car appearance regulating system of the present invention by main pressure control valve group, load-sensitive proportional throttle valve group, with blocking function
Accumulator vibration damping valve group and the composition such as respective line, sensor, wherein used by variable pump systems main pressure control valve with
It is slightly different used by Constant Pump System；For single-acting cylinder and double acting cylinder difference oleo-pneumatic suspension form load-sensitive ratio
Throttling valve group is slightly different.
The magnetic valve used, the proportioning valve of all valve groups use plug-in structure to reduce arrangement space, and valve block uses
Light aluminum alloy materials, there is good mechanical performance, excellent anticorrosive antioxygenic property compared to traditional Steel material valve block, together
When can cause whole car appearance regulating system weight loss of weight nearly 60%.Flow valve is provided with system, is protected for adjusting flow system flow
Card system moves synchronization in the same direction, while for the responsiveness of control system.
Realize closed-loop control that car appearance highly controls by adding inbuilt displacement sensor and obliquity sensor, by
Pressure sensor is added on every group of oleo-pneumatic suspension pressure oil circuit and the main oil passage of system to carry out wheel load monitoring and pressure closed loop control
System.Car before and after car attitude control system is mainly located at car body as control system collection measured by the inbuilt displacement sensor of four suspensions
Body height relative data, positioned at the car body levelness absolute data measured by obliquity sensor at car body barycenter, two compare, and lead to
The control algolithm of system is crossed, to ensure whether car appearance height meets design requirement, realizes the accurate control to vehicle body attitude.It is built-in
Displacement transducer uses magnetostriction type inbuilt displacement sensor, and it has the characteristics of precision is high, measurement range is big, and by anti-
The raising of shield grade disclosure satisfy that particular/special requirement of the vehicle to Electro Magnetic Compatibility and environmental suitability etc..Wheel load is monitored and pressure is closed
Ring control is come acquisition system actual working pressure and different oil gas by five pressure sensors being arranged in hydraulic system
Suspended load pressure, judge whether each wheel load meets requirement, and whether system is working properly by control system.
Brief description of the drawings
Fig. 1 is the quantitative pump truck appearance regulating system theory of constitution figure using single-acting cylinder oleo-pneumatic suspension；
Fig. 2 is the quantitative pump truck appearance regulating system theory of constitution figure using double acting cylinder oleo-pneumatic suspension；
Fig. 3 is the quantitative pump truck appearance regulating system theory of constitution figure of single group single-acting cylinder；
Fig. 4 is the quantitative pump truck appearance regulating system theory of constitution figure of single group double acting cylinder；
Fig. 5 is constant displacement pump main pressure control valve group composition and schematic diagram；
Fig. 6 is defibrillation valve schematic diagram；
Fig. 7 is single-acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram；
Fig. 8 is double acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram；
Fig. 9 is the variable pump truck appearance regulating system theory of constitution figure using single-acting cylinder oleo-pneumatic suspension；
Figure 10 is accumulator vibration damping valve group composition and schematic diagram with blocking function；
Figure 11 is system logic principle；
Figure 12 is working-flow.
In figure：1- fuel tanks, 2- oil returns filter, 3- system dynamics source, 4- constant displacement pumps main pressure control valve group, 5- the first from left nonocultures
With cylinder load-sensitive proportional throttle valve group, 6- the first from left carries the accumulator vibration damping valve group of blocking function, 7- the first from left accumulators, 8-
The first from left inbuilt displacement sensor, 9- the first from left oleo-pneumatic suspensions, 10- the second from left carry the accumulator vibration damping valve group of blocking function, 11- the second from left
Accumulator, 12- the second from left inbuilt displacement sensors, 13- the second from left oleo-pneumatic suspensions, the 14- right sides one carry the accumulator vibration damping of blocking function
Valve group, one accumulator of the 15- right sides, one inbuilt displacement sensor of the 16- right sides, one oleo-pneumatic suspension of the 17- right sides, the 18- right sides two carry blocking function
Accumulator vibration damping valve group, 19- the right side two accumulators, 20- the right side two inbuilt displacement sensors, 21- the right side two oleo-pneumatic suspensions, the 22- right sides two
Shuttle valve, the 23- right sides two single-acting cylinders load-sensitive proportional throttle valve group, one shuttle valve of the 24- right sides, the one single-acting cylinder load of the 25- right sides
Sensitive ratio throttling valve group, 26- the second from left shuttle valves, 27- the second from left single-acting cylinder load-sensitive proportional throttle valve group, 28- the first from left shuttles
Valve, the main oily filters of 29-, 30- constant displacement pumps, 31- the first from left double acting cylinder load-sensitive proportional throttle valve group, two double acting cylinders of the 32- right sides
With load-sensitive proportional throttle valve group, the 33- right sides one double acting cylinder load-sensitive proportional throttle valve group, 34- the second from left double acting cylinders
With load-sensitive proportional throttle valve group, 35- defibrillation valves, 36- two-bit triplet flow control valves, 37- overflow valves, 38- oil return level pressure
Poor control valve, 39- oil return proportional throttle valves, 40- oil-feed constant pressure difference control valves, 41- oil-feed proportional throttle valves, 42- oil-feed lockings
Valve, 43- oil return locking-valves, 44- constant pressure difference control valves, 45- proportional throttle valves, 46- three position four-way directional control valves, 47- annular chambers close
Locking-valve, the main oil pocket locking-valves of 48-, 49- constant pressure variable displacement pumps, 50- variable pumps main pressure control valve group, the high-power damper valves of 51-,
52- rigid locking valves.
Embodiment
Car appearance regulating system is described in detail below in conjunction with the accompanying drawings：
The car appearance regulating system is by hydraulic system, the first from left oleo-pneumatic suspension 9, the second from left oleo-pneumatic suspension 13, a right oleo-pneumatic suspension
17, right two oleo-pneumatic suspensions 21, electric control gear and cable and sensor group are between hydraulic system each several part and hydraulic system and oil
It is connected between gas suspension by high pressure hard tube (or flexible pipe), electric control gear is connected by cable with hydraulic system solenoid valve block,
Control signal is provided.Hydraulic system in the present invention is different according to the applicable oleo-pneumatic suspension mode of action, and it is negative to be divided into single-acting cylinder use
Sensitive ratio throttling valve group and double acting cylinder load-sensitive proportional throttle valve group are carried, it is different according to the hydraulic pressure pumping function of use,
Main pressure control valve group form is also slightly different.Load-sensitive proportional throttle valve group can increase according to the quantity of corresponding executing agency
Subtract, 4-12 sets are generally for general vehicle.Those skilled in the art can be combined multiple integrated controls according to being actually needed
Valve processed, realize the regulation to car appearance.
It is the quantitative pump truck appearance regulating system theory of constitution figure using single-acting cylinder oleo-pneumatic suspension as shown in Figure 1, it is supporting fixed
Measure control terminal Kp mouth of the pump with main pressure control valve group 4 and the load feedback oil circuit (two-bit triplet through the noise reduction of defibrillation valve 35
First control terminal K1 of flow control valve 36) it is connected；First control terminal K1 of right two shuttle valves 22 loads with right two single-acting cylinders
The pressure feedback control terminal K mouths of sensitive ratio throttling valve group 23 are connected, the second control terminal K2 connections fuel tank 1；Right two shuttle valves 22
Oil return control terminal is connected with the second control terminal K2 of a right shuttle valve 24, the first control terminal K1 of a right shuttle valve 24 and a right single-acting
Cylinder is connected with the pressure feedback control terminal K mouths of load-sensitive proportional throttle valve group 25；The oil return control terminal of a right shuttle valve 24 and a left side
Second control terminal K2 of two shuttle valves 26 is connected, the first control terminal K1 and the second from left single-acting cylinder load-sensitive ratio of the second from left shuttle valve 26
The pressure feedback control terminal K mouths of example throttling valve group 27 are connected；The oil return control terminal of the second from left shuttle valve 26 and the second of the first from left shuttle valve 28
Control terminal K2 is connected, the first control terminal K1 and the first from left single-acting cylinder load-sensitive proportional throttle valve group 5 of the first from left shuttle valve 28
Pressure feedback control terminal K mouths are connected, and the oil return control terminal of the first from left shuttle valve 28 is connected with constant displacement pump with the Kp of main pressure control valve group 4,
So that in the system of multi-load effect, load pressure that the first control terminal K1 of two-bit triplet flow control valve 36 is fed back
Force signal be the corresponding load of each oleo-pneumatic suspension through shuttle valve relatively after maximum, set up system real work pressure on this basis
Power.Each oleo-pneumatic suspension and the corresponding accumulator vibration damping valve group with blocking function, load-sensitive proportional throttle valve group
One group is formed with corresponding shuttle valve, logic control can be carried out to each magnetic valve by the subsidiary electric control gear of system, in realization
Rise, decline, leaning forward, swinging back, arbitrarily setting the specific action such as ride-height, it is final to realize the purpose for changing car appearance state, simultaneously
As a result of Ioad-sensing control principle, it can cause during height is adjusted, car body rise and fall speed is not by negative
Loading effect is carried, it is only related to proportional flow valve opening, the steady accurate adjustment of height of the carbody is realized, while ensure heavy duty equipment
Safety.
The specific connected mode of other modules is in addition：System dynamic source 3 drive constant displacement pump 30 connect after main oily filter 29 with
The oil inlet P of constant displacement pump main pressure control valve group 40It is connected；The first from left single-acting cylinder load-sensitive proportional throttle valve group 5, a left side
Two single-acting cylinders load-sensitive proportional throttle valve group 27, right single-acting cylinder load-sensitive proportional throttle valve group 25, the right side two
Single-acting cylinder is with after the parallel connection of load-sensitive proportional throttle valve group 23, respective oil inlet P and constant displacement pump main pressure control valve group 4
Oil-out P1It is connected, respective oil return opening is connected with constant displacement pump with the oil return opening of main pressure control valve group 4；Constant displacement pump principal pressure control
After the oil return opening of valve group 4 processed is connected with oil return filter 2, fluid unloads oil return box 1.The inbuilt displacement sensor 8 of the first from left oleo-pneumatic suspension 9, its
Oil filled port is connected with the first from left single-acting cylinder with the oil inlet A of load-sensitive proportional throttle valve group 5, and the first from left carries the accumulation of energy of blocking function
Device vibration damping valve group 6 is connected between the first from left accumulator 7 and the first from left oleo-pneumatic suspension 9；The inbuilt displacement sensor of the second from left oleo-pneumatic suspension 13
12, its oil filled port is connected with the second from left single-acting cylinder with the oil inlet A of load-sensitive proportional throttle valve group 27, and the second from left carries blocking function
Accumulator vibration damping valve group 10 be connected between the second from left accumulator 11 and the second from left oleo-pneumatic suspension 13；Set in a right oleo-pneumatic suspension 17
Displacement sensor 16, its oil filled port are connected with a right single-acting cylinder with the oil inlet A of load-sensitive proportional throttle valve group 25, and the right side one carries
The accumulator vibration damping valve group 14 of blocking function is connected between a right accumulator 15 and a right oleo-pneumatic suspension 17；Right two oleo-pneumatic suspensions
21 inbuilt displacement sensors 20, its oil filled port are connected with right two single-acting cylinders with the oil inlet A of load-sensitive proportional throttle valve group 23,
Accumulator vibration damping valve group 18 of the right side two with blocking function is connected between right two accumulators 19 and right two oleo-pneumatic suspensions 21.
Fig. 2 show the quantitative pump truck appearance regulating system theory of constitution figure using double acting cylinder oleo-pneumatic suspension.Using double cropping
Oil-filled speed (the oil-filled chamber of oil-filled chamber is depended on the stretching speed of the car appearance regulating system of cylinder oleo-pneumatic suspension piston rod at work
Refer to the oil pocket that hydraulic oil acts on when system works, i.e., oil-filled chamber is main oil pocket when piston rod stretches out, and piston rod fills when withdrawing
Oil pocket is annular chamber), therefore used load-sensitive proportional throttle valve group used by single-acting oleo-pneumatic suspension with slightly having not
Together, flow control is only employed on oil-filled oil circuit, and the checker of oil-filled chamber is realized by increasing three-position four-way valve.Together
Reason, control terminal Kp mouth of the supporting constant displacement pump with main pressure control valve group 4 and the load feedback oil circuit through the noise reduction of defibrillation valve 35
(the first control terminal K1 of two-bit triplet flow control valve 36) is connected；First control terminal K1 of right two shuttle valves 22 and right two double actings
Cylinder is connected with the pressure feedback control terminal K mouths of load-sensitive proportional throttle valve group 32, the second control terminal K2 connections fuel tank 1；The right side two
The oil return control terminal of shuttle valve 22 is connected with the second control terminal K2 of a right shuttle valve 24, the first control terminal K1 and the right side of a right shuttle valve 24
One double acting cylinder is connected with the pressure feedback control terminal K mouths of load-sensitive proportional throttle valve group 33；The oil return control of a right shuttle valve 24
End processed is connected with the second control terminal K2 of the second from left shuttle valve 26, and the first control terminal K1 of the second from left shuttle valve 26 uses with the second from left double acting cylinder to be born
The pressure feedback control terminal K mouths for carrying sensitive ratio throttling valve group 34 are connected；The oil return control terminal of the second from left shuttle valve 26 and the first from left shuttle valve
28 the second control terminal K2 is connected, and the first control terminal K1 and the first from left double acting cylinder of the first from left shuttle valve 28 are throttled with load-sensitive ratio
The pressure feedback control terminal K mouths of valve group 31 are connected, the oil return control terminal of the first from left shuttle valve 28 and constant displacement pump main pressure control valve group 4
Kp is connected, so that in the system of multi-load effect, the first control terminal K1 of two-bit triplet flow control valve 36 is fed back
Load pressure signal for each oleo-pneumatic suspension corresponding load through shuttle valve relatively after maximum, set up system reality on this basis
Border operating pressure.Each oleo-pneumatic suspension and corresponding accumulator vibration damping valve group, load-sensitive ratio with blocking function
The valve group that throttles and corresponding shuttle valve form one group, can carry out logic control to each magnetic valve by the subsidiary electric control gear of system
System, realization rise, declined, leaning forward, swinging back, arbitrarily setting the specific action such as ride-height, and final realize changes car appearance state
Purpose, simultaneously because employing Ioad-sensing control principle, it can cause during height is adjusted, car body rise and fall speed
Degree is not influenceed by load, only related to proportional flow valve opening, realizes the steady accurate adjustment of height of the carbody, while ensures weight
Carry standby safety.
The specific connected mode of other modules is in addition：System dynamic source 3 drive constant displacement pump 30 connect after main oily filter 29 with
The oil inlet P of constant displacement pump main pressure control valve group 40It is connected；The first from left double acting cylinder load-sensitive proportional throttle valve group 31, a left side
Two double acting cylinders load-sensitive proportional throttle valve group 34, right double acting cylinder load-sensitive proportional throttle valve group 33, the right side two
Double acting cylinder is with after the parallel connection of load-sensitive proportional throttle valve group 32, respective oil inlet P and constant displacement pump main pressure control valve group 4
Oil-out P1It is connected, respective oil return opening is connected with constant displacement pump with the oil return opening of main pressure control valve group 4；Constant displacement pump principal pressure control
After the oil return opening of valve group 4 processed is connected with oil return filter 2, fluid unloads oil return box 1.The inbuilt displacement sensor 8 of the first from left oleo-pneumatic suspension 9, its
Main oil pocket and annular chamber connect the oil charging-discharging A mouths and B mouths of the first from left double acting cylinder load-sensitive proportional throttle valve group 31 respectively, left
The one accumulator vibration damping valve group 6 with blocking function is connected between the first from left accumulator 7 and the first from left oleo-pneumatic suspension 9；The second from left oil gas
13 inbuilt displacement sensors 12 are hung, its main oil pocket and annular chamber connect the throttling of the second from left double acting cylinder load-sensitive ratio respectively
The oil charging-discharging A mouths and B mouths of valve group 34, accumulator vibration damping valve group 10 of the second from left with blocking function are connected on the He of the second from left accumulator 11
Between the second from left oleo-pneumatic suspension 13；The right inbuilt displacement sensor 16 of an oleo-pneumatic suspension 17, its main oil pocket and annular chamber connect the right side respectively
The oil charging-discharging A mouths and B mouths of one double acting cylinder load-sensitive proportional throttle valve group 33, accumulator of the right side one with blocking function subtract
Valve group of shaking 14 is connected between a right accumulator 15 and a right oleo-pneumatic suspension 17；The right inbuilt displacement sensor of two oleo-pneumatic suspension 21
20, its main oil pocket and annular chamber connect the oil charging-discharging A mouths and B of right two double acting cylinder load-sensitive proportional throttle valve groups 32 respectively
Mouthful, accumulator vibration damping valve group 18 of the right side two with blocking function is connected between right two accumulators 19 and right two oleo-pneumatic suspensions 21.
Fig. 3 is the quantitative pump truck appearance regulating system theory of constitution figure of single group single-acting cylinder, and wherein constant displacement pump is controlled with principal pressure
Valve group 4 and the first from left single-acting cylinder are sequentially gone here and there with load-sensitive proportional throttle valve group 5 between constant displacement pump 30 and the first from left oleo-pneumatic suspension 9
Connection, the first from left single-acting cylinder are controlled with the pressure feedback control terminal K mouths of load-sensitive proportional throttle valve group 5 with constant displacement pump with principal pressure
The control terminal Kp mouths connection of valve group 4, makes the first control terminal K1 pressure of two-bit triplet flow control valve 36 be equal to load pressure,
Reach system in-line pressure 0.6Mpa~0.9Mpa higher than load pressure all the time purpose.
As shown in figure 4, it is the quantitative pump truck appearance regulating system theory of constitution figure of single group double acting cylinder, the wherein main pressure of constant displacement pump
Force control valve group 4 and double acting cylinder with load-sensitive proportional throttle valve group 31 between constant displacement pump 30 and the first from left oleo-pneumatic suspension 9 it is suitable
Sequence is connected, pressure feedback control terminal K mouth and constant displacement pump principal pressure control of the double acting cylinder with load-sensitive proportional throttle valve group 31
The control terminal Kp mouths connection of valve group 4 processed, the first control terminal K1 pressure of two-bit triplet flow control valve 36 is set to be equal to load pressure
Power, reach system in-line pressure 0.6Mpa~0.9Mpa higher than load pressure all the time purpose；Double acting cylinder load-sensitive
The oil charging-discharging A mouths of proportional throttle valve group 31 and B mouths connect the main oil pocket and annular chamber of the first from left oleo-pneumatic suspension 9 respectively.
Fig. 5 is formed for constant displacement pump main pressure control valve group 4 and schematic diagram, mainly includes defibrillation valve 35, two-bit triplet stream
Control valve 36, overflow valve 37.Overflow valve 37, two-bit triplet flow control valve 36 are connected in parallel on pump oil-feed oil circuit and system oil return
Between road, defibrillation valve 35 is connected on the control oil circuit of two-bit triplet flow control valve 36.By setting up the pressure of overflow valve 37,
To limit system maximum working pressure, setting safety margins prevents superpressure, protects system.Defibrillation valve 35 is arranged in two three
On the through-flow control terminal K1 of control valve 36 first oil circuit, the first control terminal K1 simultaneously with constant displacement pump main pressure control valve group 4
Control terminal Kp mouths be connected so that system highest load pressure can enter defibrillation valve 35 through Kp mouths, will be steady by damping throttling
Fixed pressure signal transmission to two-bit triplet flow control valve 36 the first control terminal K1；First control terminal K1 and two-bit triplet stream
The back pressure spring of the valve element of control valve 36 is in the same side, and the second control terminal K2 of two-bit triplet flow control valve 36 enters with system
Oil communication, its pressure be consistently equal to the back pressure spring force of two-bit triplet flow control valve 36 and the first control terminal K1 pressure it
With pressure caused by the back pressure spring force of usual valve element is about 0.6Mpa~0.9Mpa, i.e., is entered using system after this structure
Oil circuit pressure is higher 0.6Mpa~0.9Mpa than load pressure all the time, compared with constant-voltage system, avoids the loss of excessive power.
Fig. 6 is the schematic diagram of defibrillation valve 35, and it is mainly by positive check valve 351, choke valve 352 and reverse check valve 353 3
Individual element in parallel composition, reach the purpose of bidirectional throttle, reduction hydraulic shock and surge wave concussion, to improve the work of system essence
Degree.
Fig. 7 is single-acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram.The first from left single-acting cylinder load-sensitive
Proportional throttle valve group 5 is by oil return constant pressure difference control valve 38, oil return proportional throttle valve 39, oil-feed constant pressure difference control valve 40, oil-feed ratio
Example choke valve 41, oil-feed locking-valve 42, oil return locking-valve 43 form.Oil-feed constant pressure difference control valve on oleo-pneumatic suspension oil-feed oil circuit
40th, oil-feed proportional throttle valve 41, oil-feed locking-valve 42 are from system to oleo-pneumatic suspension direction sequential series, oil-feed constant pressure difference control valve
First control terminal K3 is connected with the oil inlet end of oil-feed proportional throttle valve 41, oil-feed constant pressure difference control valve the second control terminal K4 and oil-feed
The oil outlet end connection of proportional throttle valve 41, oil-feed constant pressure difference control valve the second control terminal K4 and oil-feed constant pressure difference control valve 40 back of the body
Pressing spring is in the same side, i.e. the first control terminal of the oil-feed constant pressure difference control valve K3 pressure (oil-feed of oil-feed proportional throttle valve 41
End pressure) it is consistently equal to the back pressure spring force of oil-feed constant pressure difference control valve 40 and oil-feed constant pressure difference control the second control terminal of valve K4 pressure
Power (the fuel-displaced end pressure of oil-feed proportional throttle valve 41) sum, that is, the oil inlet and outlet pressure difference of oil-feed constant pressure difference control valve 40 begin
It is equal to the force value of its internal back pressure spring eventually, reaches the flow of oil-feed proportional throttle valve 41 and purpose that aperture linearly changes；
Oil return locking-valve 43 on oleo-pneumatic suspension oil return circuit, oil return constant pressure difference control valve 38, oil return proportional throttle valve 39 are from oleo-pneumatic suspension
To system oil return direction sequential series, oil return constant pressure difference control valve the first control terminal K5 and oil return proportional throttle valve 39 oil inlet end
Connection, oil return constant pressure difference control valve the second control terminal K6 are connected with the oil outlet end of oil return proportional throttle valve 39, the difference control of oil return level pressure
The back pressure spring of valve the second control terminal K6 processed and oil return constant pressure difference control valve 38 is in the same side, i.e. oil return constant pressure difference control valve the
One control terminal K5 pressure (the oil-feed end pressure of oil return proportional throttle valve 39) is consistently equal to the back pressure of oil return constant pressure difference control valve 38
Pressure (the fuel-displaced end pressure of oil return proportional throttle valve 39) sum of spring force and oil return constant pressure difference control the second control terminal of valve K6,
The oil inlet and outlet pressure difference of namely oil return constant pressure difference control valve 38 is consistently equal to the force value of its internal back pressure spring, reaches oil return ratio
The purpose that the flow of example choke valve 39 linearly changes with aperture.The exit of oil-feed proportional throttle valve 41 simultaneously with the first from left single-acting
Cylinder is connected with the pressure feedback control terminal K mouths of load-sensitive proportional throttle valve group 5, extraction system pressure feedback control signal.
Fig. 8 is double acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram.Double acting cylinder load-sensitive ratio
The valve group 31 that throttles is by constant pressure difference control valve 44, proportional throttle valve 45, three position four-way directional control valve 46, annular chamber locking-valve 47, main oil
Chamber locking-valve 48 forms.Annular chamber locking-valve 47 and main oil pocket locking-valve 48 respectively with the annular chamber of oleo-pneumatic suspension and main oil pocket,
And a ends of three position four-way directional control valve 46 are connected with b ends, the oil return opening connection system oil return oil circuit of three position four-way directional control valve 46,
The oil inlet of three position four-way directional control valve 46 with proportional throttle valve 45, is connected to system after the sequential series of constant pressure difference control valve 44 respectively
Oil-feed oil circuit.Constant pressure difference control valve the first control terminal K7 is connected with the oil inlet end of proportional throttle valve 45, constant pressure difference control valve second
Control terminal K8 is connected with the oil outlet end of proportional throttle valve 45, wherein constant pressure difference control valve the second control terminal K8 and constant pressure difference control valve
44 back pressure spring is in the same side, i.e. the first control terminal of the constant pressure difference control valve K7 pressure (oil inlet end of proportional throttle valve 45
Pressure) it is consistently equal to the back pressure spring force of constant pressure difference control valve 44 and the second control terminal of constant pressure difference control valve K8 pressure (ratio section
Flow the fuel-displaced end pressure of valve 45) sum, that is, the oil inlet and outlet pressure difference of constant pressure difference control valve 44 is consistently equal to its internal back pressure
The force value of spring, reaches the flow of proportional throttle valve 45 and purpose that aperture linearly changes.Other proportional throttle valve 45 is fuel-displaced
End is connected with double acting cylinder with the pressure feedback control terminal K mouths of load-sensitive proportional throttle valve group 31 simultaneously, extraction system pressure
Feedback control signal.
Fig. 9 is the variable pump truck appearance regulating system theory of constitution figure using single-acting cylinder oleo-pneumatic suspension.The system is using permanent
Pressure variable amount pump 49 provides power, except variable pump is former with main pressure control valve group 50 and the structure of constant displacement pump main pressure control valve group 4
Reason is different outer, remaining valve group function and system connected mode and the quantitative pump truck appearance regulating system using single-acting cylinder oleo-pneumatic suspension
It is identical.Similarly those skilled in the art can easily infer the variable pump truck appearance regulation system of double acting cylinder oleo-pneumatic suspension
System theory of constitution figure.
Variable pump mainly includes overflow valve 37 with main pressure control valve group 50, by setting up the pressure of overflow valve 37, to limit
Determine system maximum working pressure, setting safety margins prevents superpressure, protects system.Variable pump main pressure control valve group 50
Control terminal Kp mouths be connected with variable pump control terminal so that system highest load pressure can be controlled through Kp mouths with entering variable pump
End, will pass through the parameter such as output pressure and flow that load pressure adjusts variable pump in real time.
Figure 10 is accumulator vibration damping valve group composition and schematic diagram with blocking function.Accumulator with blocking function subtracts
Valve group of shaking 6 is connected between accumulator and pneumatic cylinder, plays buffering ground in face of suspension impact.With blocking function
Accumulator vibration damping valve group 6 is composed in series by high-power damper valve 51 and open type 2/2-way rigid locking valve 52.It is high-power to subtract
The valve 51 that shakes is consistent with the structural principle of defibrillation valve 35, and as shown in Figure 10, it is mainly by positive check valve 351, choke valve 352 and anti-
To 353 3 element in parallel compositions of check valve, reach the purpose that bidirectional throttle vibration damping, reduction hydraulic shock and surge wave shake；
After the 52 energization locking of rigid locking valve, whole chassis forms rigid platfor, improves job stability.
Figure 11 is system logic principle.System provides high voltage power using motor (or engine), pump as power source, with oil gas
Suspension is used as executive component, controls oleo-pneumatic suspension oil charging-discharging to realize the change of car appearance by duty valve block, passes through sensing system
Realize the monitoring and closed-loop control of height, levelness and spring carried mass.It is maximum negative to bear in system self-regulating process
Control object of the wheel position of load as system pressure and flow, other wheel positions pressure monitored in real time by sensor and with maximum
Load is compared, and the reasonable distribution of each wheel bit traffic is realized by linear ratio relation, reaches the purpose steadily lifted.
Figure 12 is working-flow.System control mode is divided into controls and automatically controls both of which manually.Automatic control
Under state processed, as long as driver operates corresponding car appearance Action Button, system will pass through collecting vehicle appearance position according to program setting
Signal, reach program state set in advance.When under manual state of a control, driver is by controlling car appearance Action Button
Time length determines the time length of oleo-pneumatic suspension oil charging-discharging, so as to reach the effect of control car appearance height；System is led to
Cross the inbuilt displacement sensor being arranged in inside oleo-pneumatic suspension and be arranged in the obliquity sensor of body gravity position to enter driving
The control of appearance direction Bit andits control and car body load-carrying plane levelness perpendicular to the ground, meeting and alarm when stroke transfinites；Pass through
Pressure sensor is added to carry out axle load monitoring and pressure closed loop control, meeting and alarm when pressure limit.
It should be noted that skilled person can easily appreciate that, the adjustable oil gas of car appearance involved in the present invention
Suspension arrangement can be arranged on different types of vehicle in the above described manner, and is not departing from the sheet that is defined by the following claims
In the case of the spirit and scope of invention, various various forms of changes and change can be carried out to the present invention.
Claims (4)
- A kind of 1. quantitative pump truck appearance regulating system of single group single-acting cylinder, by constant displacement pump main pressure control valve group, the first from left single-acting Cylinder load-sensitive proportional throttle valve group, constant displacement pump and the first from left oleo-pneumatic suspension composition, wherein constant displacement pump main pressure control valve group Mainly comprising defibrillation valve, 2/2-way flow control valve, overflow valve, it is characterised in that：Constant displacement pump with main pressure control valve group and The first from left single-acting cylinder sequential series between constant displacement pump and the first from left oleo-pneumatic suspension with load-sensitive proportional throttle valve group；Constant displacement pump is used Overflow valve, 2/2-way flow control valve in main pressure control valve group be connected in parallel on pump oil-feed oil circuit and system oil return road it Between, 2/2-way flow control valve has two control ports, and defibrillation valve is arranged in 2/2-way flow control valve first and controlled On the oil circuit at end, the first control terminal is connected with constant displacement pump with the control terminal of main pressure control valve group simultaneously, the first from left single-acting in addition The load pressure feedback control terminal also control with constant displacement pump main pressure control valve group of cylinder load-sensitive proportional throttle valve group End connection so that system load pressure can enter defibrillation valve, by damping throttling by stable pressure signal transmission to two First control terminal of two through-flow control valves；The back pressure spring of first control terminal and 2/2-way flow control valve valve element is in same Side, the second control terminal of 2/2-way flow control valve connect with system in-line, and its pressure is consistently equal to 2/2-way stream The pressure sum of control valve back pressure spring force and the first control terminal, pressure set caused by the back pressure spring force of valve element are 0.6Mpa~0.9Mpa；The defibrillation valve is composed in parallel by positive check valve, choke valve and reverse check valve, reaches two-way section Stream, the purpose for reducing hydraulic shock and surge wave concussion, to improve the operating accuracy of system.
- 2. the quantitative pump truck appearance regulating system of single group single-acting cylinder according to claim 1, it is characterised in that：The first from left single-acting Cylinder mainly includes oil return constant pressure difference control valve, oil return proportional throttle valve, the difference control of oil-feed level pressure with load-sensitive proportional throttle valve group Valve, oil-feed proportional throttle valve, oil-feed locking-valve and oil return locking-valve processed, the oil return constant pressure difference control valve, the throttling of oil return ratio Valve, oil-feed constant pressure difference control valve, oil-feed proportional throttle valve, oil-feed locking-valve and oil return locking-valve are 2/2-way valve arrangement, Wherein oil return constant pressure difference control valve and oil-feed constant pressure difference control valve have two control ports respectively；On oleo-pneumatic suspension oil-feed oil circuit Oil-feed constant pressure difference control valve, oil-feed proportional throttle valve, oil-feed locking-valve are fixed from system to oleo-pneumatic suspension direction sequential series, oil-feed The control terminal of differential pressure control valve first is connected with the oil inlet end of oil-feed proportional throttle valve, the second control terminal of oil-feed constant pressure difference control valve with The oil outlet end connection of oil-feed proportional throttle valve, the second control terminal of oil-feed constant pressure difference control valve and the back pressure of oil-feed constant pressure difference control valve Spring is in the same side, i.e. the pressure of the control terminal of oil-feed constant pressure difference control valve first is consistently equal to oil-feed constant pressure difference control valve back pressure The pressure sum of spring force and oil-feed constant pressure difference control the second control terminal of valve.
- 3. the quantitative pump truck appearance regulating system of single group single-acting cylinder according to claim 2, it is characterised in that：The oil return is closed Locking-valve, oil return constant pressure difference control valve, oil return proportional throttle valve are from oleo-pneumatic suspension to system oil return direction sequential series, oil return level pressure The poor control terminal of control valve first is connected with the oil inlet end of oil return proportional throttle valve, and the second control terminal of oil return constant pressure difference control valve is with returning The oil outlet end connection of oily proportional throttle valve, the second control terminal of oil return constant pressure difference control valve and the back pressure bullet of oil return constant pressure difference control valve Spring is in the same side, i.e. the pressure of the control terminal of oil return constant pressure difference control valve first is consistently equal to oil return constant pressure difference control valve back pressure bullet The pressure sum of spring force and oil return constant pressure difference control the second control terminal of valve.
- 4. the quantitative pump truck appearance regulating system of single group single-acting cylinder according to claim 2, it is characterised in that：The oil-feed ratio Example choke valve exit is connected with the first from left single-acting cylinder with the pressure feedback control terminal of load-sensitive proportional throttle valve group simultaneously, is drawn Go out system pressure feedback control signal.
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| US11787255B2 (en) | 2021-09-20 | 2023-10-17 | Caterpillar Inc. | Suspension system with individual ride height and dampening control |
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| CN108256195B (en) * | 2018-01-10 | 2021-03-30 | 太原科技大学 | Pressure impact calculation method for hydraulic system of longitudinal rolling shear |
| CN110497760B (en) * | 2019-08-07 | 2020-09-18 | 燕山大学 | Active and passive dual-mode switchable vehicle suspension system and switching method thereof |
| CN112895832B (en) * | 2021-01-29 | 2022-10-28 | 中国北方车辆研究所 | Vehicle posture and damping adjustment control method |
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| CN104421241A (en) * | 2013-09-05 | 2015-03-18 | 阮慎锐 | Engineering machinery open center load adaption device |
| CN204677524U (en) * | 2015-05-29 | 2015-09-30 | 大洋泊车股份有限公司 | Multi-storied garage combined power unit formula one-way cylinder hydraulic control system |
| CN105179383A (en) * | 2015-09-28 | 2015-12-23 | 北汽福田汽车股份有限公司 | Engineering machinery, hydraulic system for constant displacement pump of engineering machinery and controlling method of hydraulic system |
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