CN105751848A - Energy accumulator vibration attenuation valve group with locking function - Google Patents
Energy accumulator vibration attenuation valve group with locking function Download PDFInfo
- Publication number
- CN105751848A CN105751848A CN201610171844.1A CN201610171844A CN105751848A CN 105751848 A CN105751848 A CN 105751848A CN 201610171844 A CN201610171844 A CN 201610171844A CN 105751848 A CN105751848 A CN 105751848A
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- valve group
- pressure
- load
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/056—Regulating distributors or valves for hydropneumatic systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/021—Installations or systems with accumulators used for damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
- B60G2400/25—Stroke; Height; Displacement
- B60G2400/252—Stroke; Height; Displacement vertical
Abstract
The invention relates to an energy accumulator vibration attenuation valve group with a locking function. The energy accumulator vibration attenuation valve group is formed by connecting a large-power vibration attenuation valve and a normally opened two-position two-way rigid locking valve in series and is connected in series between an energy accumulator and a hydro-pneumatic suspension cylinder, wherein the large-power vibration attenuation valve is formed by connecting three elements, namely, a forward one-direction valve, a throttle valve and a backward one-direction valve in parallel, so as to achieve the purposes of bidirectional throttle vibration attenuation, hydraulic impact reduction and water surge wave oscillation reduction. After the rigid locking valve is powered on and locked, a whole chassis form a rigid platform, so that the working stability can be improved.
Description
Technical field
The present invention relates to a kind of oil gas hanging unwheeling appearance and regulate the accumulator damper valve group with blocking function of system, belong to hydraulic machinery and road vehicle application field.
Background technology
By adopting oil-gas suspension technology, handling stability energy and the ride performance of vehicle are greatly improved, solve the nonadjustable technical barrier of elastic element rigidity characteristic of traditional suspension.But along with the raising that vehicle transport power is required with to vehicle stability, safety, the raising that comfortableness requires, the storage transporting equipment that particularly load change is bigger, how can guarantee that sky full load condition car appearance governing speed is consistent, when how to ensure when height of the carbody regulates particularly to regulate under full load condition, upper loading thing is steady, how to realize system high efficiency energy-conservation, reduce the problems such as loss in efficiency, become current domestic vehicles production firm technological difficulties that are encountered and that cannot effectively solve all the time, so the modular cart appearance adjustment system based on load-sensitive principle of developing just seems particularly necessary.
Summary of the invention
According to an aspect of the present invention, a kind of modular cart appearance based on load-sensitive principle is provided to regulate system, the attitude of vehicle is adjusted, and this system is by system dynamic source, form based on the hydraulic system (hereinafter referred to as hydraulic system) of load-sensitive principle, oleo-pneumatic suspension, electric control gear and sensor.System dynamic source, hydraulic system are connected by pipeline with oleo-pneumatic suspension, oleo-pneumatic suspension includes the left oleo-pneumatic suspension of at least two and the right oleo-pneumatic suspension of at least two, it is characterised in that: hydraulic system includes the filter of main oil, oil return filter, fuel tank, main pressure control valve group, load-sensitive proportional throttle valve group, forms with the accumulator damper valve group of blocking function and all kinds of pipeline, joint etc..Main pressure control valve group comprises overflow valve, two-bit triplet flow control valve, defibrillation valve, and wherein overflow valve and two-bit triplet flow control valve are in parallel, and defibrillation valve controls end by load pressure feed back loop with two-bit triplet flow control valve and is connected.System pressure feedback signal is filtered by defibrillation valve by structures such as the throttle orifices of setting, it is achieved system pressure and the stable of flow accurately control；System maximum working pressure is limited, it is prevented that superpressure produces influential system safety by overflow valve；Two-bit triplet flow control valve passes through internal pressure balanced structure, controls system actual working pressure, it is achieved the most high capacity of system actual working pressure and system is relevant in real time, pressure loss when minimizing is due to system zero load.Adopt dosing pump and variable pump systems supporting main pressure control valve group composition be slightly different.
Load-sensitive proportional throttle valve group comprises constant pressure difference control valve, proportional throttle valve, locking-valve, is mainly used in controlling flow, it is achieved the purpose that flow is unrelated with load.Wherein constant pressure difference control valve, proportional throttle valve, locking-valve are cascaded structure, and two pressure feedback of constant pressure difference control valve control end and are connected in parallel on the oil inlet and outlet place of proportional throttle valve respectively, are used for controlling proportional throttle valve inlet outlet pressure differential.For the sequencing being connected between single-acting cylinder proportional throttle valve with constant pressure difference control valve, determine the difference of oil circuit control；Then can increase by one 3-position 4-way guiding valve of series connection for double acting cylinder and reach to control the purpose of oil return speed by controlling the speed of in-line.Locking-valve is between oleo-pneumatic suspension and other hydraulic valve, and Main Function is the high-pressure in locking oleo-pneumatic suspension, it is achieved system high pressure locking.
Oleo-pneumatic suspension damper valve constitutes the accumulator damper valve group with blocking function.It is connected in parallel between oleo-pneumatic suspension and load-sensitive proportional throttle valve group after accumulator damper valve group series connection accumulator with blocking function, for cushioning impact and the absorption system hydraulic shock of car body faced by ground.
Car appearance of the present invention regulates system and is made up of main pressure control valve group, load-sensitive proportional throttle valve group, accumulator damper valve group and respective line, sensor etc. with blocking function, and what the main pressure control valve that wherein variable pump systems adopts and Constant Pump System adopted is slightly different；It is slightly different for single-acting cylinder oleo-pneumatic suspension different from double acting cylinder form load-sensitive proportional throttle valve group.
The electromagnetic valve of use of all valve groups, proportioning valve all adopt plug-in structure to reduce arrangement space, valve block adopts light aluminum alloy materials, compared to conventional steel material valve block, there is good mechanical performance, excellent anticorrosive antioxygenic property, simultaneously can so that whole car appearance regulates system weight loss of weight nearly 60%.System is provided with flow valve, is used for adjusting flow system flow and ensures system synchronized movement in the same direction, be simultaneously used for the speed of action of control system.
By adding inbuilt displacement sensor and obliquity sensor realizes the closed loop control of car appearance Altitude control, by oleo-pneumatic suspension pressure oil circuit and the main oil passage of system add pressure transducer carrying out wheel load monitoring and pressure closed loop controls often organizing.Car appearance controls to be positioned at before and after car body the height of the carbody relative data measured by the inbuilt displacement sensor of four suspensions mainly through controlling system acquisition, it is positioned at the car body levelness absolute data measured by car body barycenter place obliquity sensor, two compare, by the control algolithm of system, ensure whether car appearance height meets design requirement, it is achieved the accurate control to vehicle body attitude.Inbuilt displacement sensor adopts magnetostriction type inbuilt displacement sensor, the feature that it has precision height, measurement scope is big, and disclosure satisfy that the vehicle particular/special requirement to Electro Magnetic Compatibility and environmental suitability etc. by the raising of degree of protection.Wheel load monitoring and pressure closed loop control to be come acquisition system actual working pressure and different oleo-pneumatic suspension load pressure by five pressure transducers being arranged in hydraulic system, judging whether each wheel load meets instructions for use by control system, whether system is working properly.
Accompanying drawing explanation
Fig. 1 is dosing pump main pressure control valve group composition and schematic diagram；
Fig. 2 is single-acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram；
Fig. 3 is that single group quantitative pump truck appearance of single-acting cylinder regulates system theory of constitution figure；
Fig. 4 adopts the quantitative pump truck appearance of single-acting cylinder oleo-pneumatic suspension to regulate system theory of constitution figure；
Fig. 5 is double acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram；
Fig. 6 is that single group quantitative pump truck appearance of double acting cylinder regulates system theory of constitution figure；
Fig. 7 adopts the quantitative pump truck appearance of double acting cylinder oleo-pneumatic suspension to regulate system theory of constitution figure；
Fig. 8 adopts the variable pump truck appearance of single-acting cylinder oleo-pneumatic suspension to regulate system theory of constitution figure；
Fig. 9 is that the accumulator damper valve group with blocking function forms and schematic diagram；
The high-power damper valve of Figure 10 and defibrillation valve arrangement principle；
Figure 11 system main-control logic；
Figure 12 working-flow.
nullIn figure: 1-fuel tank，2-oil return is filtered，3-system dynamic source，4-dosing pump main pressure control valve group，5-the first from left single-acting cylinder load-sensitive proportional throttle valve group，6-the first from left is with the accumulator damper valve group of blocking function，7-the first from left accumulator，8-the first from left inbuilt displacement sensor，9-the first from left oleo-pneumatic suspension，10-the second from left is with the accumulator damper valve group of blocking function，11-the second from left accumulator，12-the second from left inbuilt displacement sensor，13-the second from left oleo-pneumatic suspension，The 14-right side one is with the accumulator damper valve group of blocking function，The right accumulator of 15-，The right inbuilt displacement sensor of 16-，The right oleo-pneumatic suspension of 17-，The 18-right side two is with the accumulator damper valve group of blocking function，Right two accumulators of 19-，Right two inbuilt displacement sensors of 20-，Right two oleo-pneumatic suspensions of 21-，Right two shuttle valves of 22-，The right two single-acting cylinders load-sensitive proportional throttle valve group of 23-，The right shuttle valve of 24-，The right single-acting cylinder load-sensitive proportional throttle valve group of 25-，26-the second from left shuttle valve，27-the second from left single-acting cylinder load-sensitive proportional throttle valve group，28-the first from left shuttle valve，The main oil filter of 29-，30-dosing pump，31-the first from left double acting cylinder load-sensitive proportional throttle valve group，The right two double acting cylinders load-sensitive proportional throttle valve group of 32-，The right double acting cylinder load-sensitive proportional throttle valve group of 33-，34-the second from left double acting cylinder load-sensitive proportional throttle valve group，35-defibrillation valve，36-two-bit triplet flow control valve，37-overflow valve，38-oil return constant pressure difference control valve，39-oil return proportional throttle valve，40-oil-feed constant pressure difference control valve，41-oil-feed proportional throttle valve，42-oil-feed locking-valve，43-oil return locking-valve，44-constant pressure difference control valve，45-proportional throttle valve，46-three position four-way directional control valve，47-annular chamber locking-valve，The main oil pocket locking-valve of 48-，49-constant pressure variable displacement pump，50-variable pump main pressure control valve group，The high-power damper valve of 51-，52-rigid locking valve.
Detailed description of the invention
Below in conjunction with accompanying drawing, car appearance is regulated system to be described in detail:
Described car appearance regulates system 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 composition, be connected by high pressure hard tube (or flexible pipe) between hydraulic system each several part and between hydraulic system and oleo-pneumatic suspension, electric control gear is connected with hydraulic system electromagnetic valve group by cable, it is provided that control signal.Hydraulic system in the present invention is different according to applicable oleo-pneumatic suspension model of action, it is divided into single-acting cylinder load-sensitive proportional throttle valve group and double acting cylinder load-sensitive proportional throttle valve group, different according to the hydraulic pump function adopted, main pressure control valve group form is also slightly different.Load-sensitive proportional throttle valve group according to the quantity increase and decrease of corresponding actuator, can be generally 4-12 set for general vehicle.Those skilled in the art can the multiple integrated control valve of combination in any according to actual needs, it is achieved the adjustment to car appearance.
Fig. 1 is that dosing pump main pressure control valve group 4 forms and schematic diagram, mainly comprises defibrillation valve 35, two-bit triplet flow control valve 36, overflow valve 37.Overflow valve 37, two-bit triplet flow control valve 36 are all connected in parallel between pump oil-feed oil circuit and system oil return road, and defibrillation valve 35 is connected on the oil circuit control of two-bit triplet flow control valve 36.By setting up the pressure of overflow valve 37, limit system maximum working pressure, set safety margins and prevent superpressure, protect system.Defibrillation valve 35 is arranged in two-bit triplet flow control valve 36 first and controls on the oil circuit of end K1, first controls end K1 is connected with the control end Kp mouth of dosing pump main pressure control valve group 4 simultaneously, make system highest load pressure can enter defibrillation valve 35 through Kp mouth, control end K1 by damping throttling by the first of stable pressure signal transmission to two-bit triplet flow control valve 36；The first back pressure spring controlling end K1 and two-bit triplet flow control valve 36 spool is in the same side, the second of two-bit triplet flow control valve 36 controls end K2 and connects with system in-line, its pressure is to consistently equal to two-bit triplet flow control valve 36 back pressure spring force and first and controls the pressure sum of end K1, pressure produced by the back pressure spring force of usual spool is about 0.6Mpa～0.9Mpa, namely after adopting this structure, system in-line pressure is higher 0.6Mpa～0.9Mpa than load pressure all the time, compared with constant-voltage system, it is to avoid the loss of excessive power.Fig. 6 is the schematic diagram of defibrillation valve 35, and it is mainly made up of forward check valve 351, choke valve 352 and reverse 353 3 element in parallel of check valve, reaches bidirectional throttle, reduces hydraulic shock and the purpose of surge wave concussion, to improve the operating accuracy of system.
Fig. 2 is single-acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram.The first from left single-acting cylinder is by load-sensitive proportional throttle valve group 5 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 proportional throttle valve 41, and oil-feed locking-valve 42, oil return locking-valve 43 forms.nullOil-feed constant pressure difference control valve 40 on oleo-pneumatic suspension oil-feed oil circuit、Oil-feed proportional throttle valve 41、Oil-feed locking-valve 42 is from system to oleo-pneumatic suspension direction sequential series，Oil-feed constant pressure difference control valve first controls end K3 and is connected with the oil inlet end of oil-feed proportional throttle valve 41，Oil-feed constant pressure difference control valve second controls end K4 and is connected with the oil outlet end of oil-feed proportional throttle valve 41，Oil-feed constant pressure difference control valve second controls the back pressure spring of end K4 and oil-feed constant pressure difference control valve 40 and is in the same side，Namely oil-feed constant pressure difference control valve first controls the pressure (the oil inlet end pressure of oil-feed proportional throttle valve 41) of end K3 and is to consistently equal to oil-feed constant pressure difference control valve 40 back pressure spring force and oil-feed constant pressure difference control valve second controls pressure (the oil outlet end pressure of the oil-feed proportional throttle valve 41) sum of end K4，Namely the oil inlet and outlet pressure reduction of oil-feed constant pressure difference control valve 40 is to consistently equal to the force value of its internal back pressure spring，Reach the purpose that the flow of oil-feed proportional throttle valve 41 linearly changes with aperture；nullOil 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 is from oleo-pneumatic suspension to system oil return direction sequential series，Oil return constant pressure difference control valve first controls end K5 and is connected with the oil inlet end of oil return proportional throttle valve 39，Oil return constant pressure difference control valve second controls end K6 and is connected with the oil outlet end of oil return proportional throttle valve 39，Oil return constant pressure difference control valve second controls the back pressure spring of end K6 and oil return constant pressure difference control valve 38 and is in the same side，Namely oil return constant pressure difference control valve first controls the pressure (the oil inlet end pressure of oil return proportional throttle valve 39) of end K5 and is to consistently equal to oil return constant pressure difference control valve 38 back pressure spring force and oil return constant pressure difference control valve second controls pressure (the oil outlet end pressure of the oil return proportional throttle valve 39) sum of end K6，Namely the oil inlet and outlet pressure reduction of oil return constant pressure difference control valve 38 is to consistently equal to the force value of its internal back pressure spring，Reach the purpose that the flow of oil return proportional throttle valve 39 linearly changes with aperture.Oil-feed proportional throttle valve 41 exit controls end K mouth with the pressure feedback of the first from left single-acting cylinder load-sensitive proportional throttle valve group 5 simultaneously and is connected, extraction system pressure feedback control signal.
Fig. 3 is that single group quantitative pump truck appearance of single-acting cylinder regulates system theory of constitution figure, wherein dosing pump by main pressure control valve group 4 and the first from left single-acting cylinder load-sensitive proportional throttle valve group 5 sequential series between dosing pump 30 and the first from left oleo-pneumatic suspension 9, the first from left single-acting cylinder controls end K mouth by the pressure feedback of load-sensitive proportional throttle valve group 5 and is connected with the control end Kp mouth of dosing pump main pressure control valve group 4, make the first of two-bit triplet flow control valve 36 control end K1 pressure and be equal to load pressure, reach the purpose of system in-line pressure 0.6Mpa～0.9Mpa higher than load pressure all the time.
Being illustrated in figure 4 and adopt the quantitative pump truck appearance of single-acting cylinder oleo-pneumatic suspension to regulate system theory of constitution figure, the end Kp mouth that controls of supporting dosing pump main pressure control valve group 4 is connected with load feedback oil circuit (the first of two-bit triplet flow control valve 36 controls end K1) through defibrillation valve 35 noise reduction；The first of right two shuttle valves 22 controls end K1 and is connected with the pressure feedback control end K mouth of right two single-acting cylinder load-sensitive proportional throttle valve groups 23, and second controls end K2 connects fuel tank 1；The oil return of right two shuttle valves 22 controls end and is connected with the second control end K2 of a right shuttle valve 24, and the first of a right shuttle valve 24 controls end K1 and be connected with the pressure feedback control end K mouth of a right single-acting cylinder load-sensitive proportional throttle valve group 25；The oil return of a right shuttle valve 24 controls end and is connected with the second control end K2 of the second from left shuttle valve 26, and the first of the second from left shuttle valve 26 controls end K1 and be connected with the pressure feedback control end K mouth of the second from left single-acting cylinder load-sensitive proportional throttle valve group 27；The oil return of the second from left shuttle valve 26 controls end and is connected with the second control end K2 of the first from left shuttle valve 28, the first of the first from left shuttle valve 28 controls end K1 and is connected with the pressure feedback control end K mouth of the first from left single-acting cylinder load-sensitive proportional throttle valve group 5, the first from left shuttle valve 28 oil return controls end and is connected with the Kp of dosing pump main pressure control valve group 4, so that in the system of multi load effect, the first of two-bit triplet flow control valve 36 control the load pressure signal that feeds back of end K1 be each oleo-pneumatic suspension correspondence load through shuttle valve relatively after maximum, set up system actual working pressure on this basis.Each oleo-pneumatic suspension and the corresponding accumulator damper valve group with blocking function, load-sensitive proportional throttle valve group and corresponding shuttle valve form one group, the electric control gear that system is subsidiary can be passed through, each electromagnetic valve is carried out logic control, realize rising, decline, lean forward, layback, arbitrarily set the concrete actions such as ride-height, the final purpose realizing changing car appearance state, simultaneously because have employed Ioad-sensing control principle, can so that regulate height process in, car body rise and fall speed is not affected by load, only relevant to proportional flow valve opening, realize height of the carbody steadily accurately to regulate, ensure the safety of heavy duty equipment simultaneously.
Additionally the concrete connected mode of other modules is: system dynamic source 3 drive dosing pump 30 connect after main oil filter 29 with the oil inlet P of dosing pump main pressure control valve group 40It is connected；After the first from left single-acting cylinder load-sensitive proportional throttle valve group 5, the second from left single-acting cylinder load-sensitive proportional throttle valve group 27, a right single-acting cylinder load-sensitive proportional throttle valve group 25, right two single-acting cylinder load-sensitive proportional throttle valve group 23 parallel connections, the oil-out P of respective oil inlet P and dosing pump main pressure control valve group 41Being connected, respective oil return opening is connected with the oil return opening of dosing pump main pressure control valve group 4；After dosing pump is connected with oil return filter 2 with the oil return opening of main pressure control valve group 4, fluid unloads oil sump tank 1.The first from left oleo-pneumatic suspension 9 inbuilt displacement sensor 8, its oil-filled mouth is connected with the first from left single-acting cylinder load-sensitive proportional throttle valve group 5 oil-in A, and the first from left is connected between the first from left accumulator 7 and the first from left oleo-pneumatic suspension 9 with the accumulator damper valve group 6 of blocking function；The second from left oleo-pneumatic suspension 13 inbuilt displacement sensor 12, its oil-filled mouth is connected with the second from left single-acting cylinder load-sensitive proportional throttle valve group 27 oil-in A, and the second from left is connected between the second from left accumulator 11 and the second from left oleo-pneumatic suspension 13 with the accumulator damper valve group 10 of blocking function；Right oleo-pneumatic suspension 17 inbuilt displacement sensor 16, its oil-filled mouth is connected with a right single-acting cylinder load-sensitive proportional throttle valve group 25 oil-in A, and the right side one is connected between a right accumulator 15 and a right oleo-pneumatic suspension 17 with the accumulator damper valve group 14 of blocking function；Right two oleo-pneumatic suspension 21 inbuilt displacement sensors 20, its oil-filled mouth is connected with right two single-acting cylinder load-sensitive proportional throttle valve group 23 oil-in A, and the right side two is connected between right two accumulators 19 and right two oleo-pneumatic suspensions 21 with the accumulator damper valve group 18 of blocking function.
Fig. 5 is double acting cylinder load-sensitive proportional throttle valve group composition and schematic diagram.Double acting cylinder is by load-sensitive proportional throttle valve group 31 by constant pressure difference control valve 44, proportional throttle valve 45, three position four-way directional control valve 46, annular chamber locking-valve 47, and main oil pocket locking-valve 48 forms.Annular chamber locking-valve 47 is connected with a end of the annular chamber of oleo-pneumatic suspension and main oil pocket and three position four-way directional control valve 46 and b end respectively with main oil pocket locking-valve 48, the oil return opening connection system oil return circuit of three position four-way directional control valve 46, the oil-in of three position four-way directional control valve 46 respectively with proportional throttle valve 45, be connected to system oil-feed oil circuit after constant pressure difference control valve 44 sequential series.Constant pressure difference control valve first controls end K7 and is connected with the oil inlet end of proportional throttle valve 45, constant pressure difference control valve second controls end K8 and is connected with the oil outlet end of proportional throttle valve 45, wherein constant pressure difference control valve second controls the back pressure spring of end K8 and constant pressure difference control valve 44 and is in the same side, namely constant pressure difference control valve first controls the pressure (the oil inlet end pressure of proportional throttle valve 45) of end K7 and is to consistently equal to constant pressure difference control valve 44 back pressure spring force and constant pressure difference control valve second controls pressure (the oil outlet end pressure of the proportional throttle valve 45) sum of end K8, namely the oil inlet and outlet pressure reduction of constant pressure difference control valve 44 is to consistently equal to the force value of its internal back pressure spring, reach the purpose that the flow of proportional throttle valve 45 linearly changes with aperture.Additionally proportional throttle valve 45 oil outlet end is connected with the pressure feedback control end K mouth of double acting cylinder load-sensitive proportional throttle valve group 31 simultaneously, extraction system pressure feedback control signal.
As shown in Figure 6, system theory of constitution figure is regulated for single group quantitative pump truck appearance of double acting cylinder, wherein dosing pump by main pressure control valve group 4 and double acting cylinder load-sensitive proportional throttle valve group 31 sequential series between dosing pump 30 and the first from left oleo-pneumatic suspension 9, double acting cylinder controls end K mouth by the pressure feedback of load-sensitive proportional throttle valve group 31 and is connected with the control end Kp mouth of dosing pump main pressure control valve group 4, make the first of two-bit triplet flow control valve 36 control end K1 pressure and be equal to load pressure, reach the purpose of system in-line pressure 0.6Mpa～0.9Mpa higher than load pressure all the time；Double acting cylinder load-sensitive proportional throttle valve group 31 oil charging-discharging A mouth and B mouth connect main oil pocket and the annular chamber of the first from left oleo-pneumatic suspension 9 respectively.
Fig. 7 show and adopts the quantitative pump truck appearance of double acting cylinder oleo-pneumatic suspension to regulate system theory of constitution.The car appearance adopting double acting cylinder regulates the stretching speed of system operationally oleo-pneumatic suspension piston rod and depends on that (oil-filled chamber refers to the oil pocket of hydraulic oil effect when system works to the oil-filled speed of oil-filled chamber, namely when piston rod stretches out, oil-filled chamber is main oil pocket, when piston rod is regained, oil-filled chamber is annular chamber), what the load-sensitive proportional throttle valve group therefore used and single-acting oleo-pneumatic suspension adopted is slightly different, on oil-filled oil circuit, only have employed flow-control, and realize the checker of oil-filled chamber by increasing three-position four-way valve.In like manner, the end Kp mouth that controls of supporting dosing pump main pressure control valve group 4 is connected with load feedback oil circuit (the first of two-bit triplet flow control valve 36 controls end K1) through defibrillation valve 35 noise reduction；The first of right two shuttle valves 22 controls end K1 and is connected with the pressure feedback control end K mouth of right two double acting cylinder load-sensitive proportional throttle valve groups 32, and second controls end K2 connects fuel tank 1；The oil return of right two shuttle valves 22 controls end and is connected with the second control end K2 of a right shuttle valve 24, and the first of a right shuttle valve 24 controls end K1 and be connected with the pressure feedback control end K mouth of a right double acting cylinder load-sensitive proportional throttle valve group 33；The oil return of a right shuttle valve 24 controls end and is connected with the second control end K2 of the second from left shuttle valve 26, and the first of the second from left shuttle valve 26 controls end K1 and be connected with the pressure feedback control end K mouth of the second from left double acting cylinder load-sensitive proportional throttle valve group 34；The oil return of the second from left shuttle valve 26 controls end and is connected with the second control end K2 of the first from left shuttle valve 28, the first of the first from left shuttle valve 28 controls end K1 and is connected with the pressure feedback control end K mouth of the first from left double acting cylinder load-sensitive proportional throttle valve group 31, the first from left shuttle valve 28 oil return controls end and is connected with the Kp of dosing pump main pressure control valve group 4, so that in the system of multi load effect, the first of two-bit triplet flow control valve 36 control the load pressure signal that feeds back of end K1 be each oleo-pneumatic suspension correspondence load through shuttle valve relatively after maximum, set up system actual working pressure on this basis.Each oleo-pneumatic suspension and the corresponding accumulator damper valve group with blocking function, load-sensitive proportional throttle valve group and corresponding shuttle valve form one group, the electric control gear that system is subsidiary can be passed through, each electromagnetic valve is carried out logic control, realize rising, decline, lean forward, layback, arbitrarily set the concrete actions such as ride-height, the final purpose realizing changing car appearance state, simultaneously because have employed Ioad-sensing control principle, can so that regulate height process in, car body rise and fall speed is not affected by load, only relevant to proportional flow valve opening, realize height of the carbody steadily accurately to regulate, ensure the safety of heavy duty equipment simultaneously.
Additionally the concrete connected mode of other modules is: system dynamic source 3 drive dosing pump 30 connect after main oil filter 29 with the oil inlet P of dosing pump main pressure control valve group 40It is connected；After the first from left double acting cylinder load-sensitive proportional throttle valve group 31, the second from left double acting cylinder load-sensitive proportional throttle valve group 34, a right double acting cylinder load-sensitive proportional throttle valve group 33, right two double acting cylinder load-sensitive proportional throttle valve group 32 parallel connections, the oil-out P of respective oil inlet P and dosing pump main pressure control valve group 41Being connected, respective oil return opening is connected with the oil return opening of dosing pump main pressure control valve group 4；After dosing pump is connected with oil return filter 2 with the oil return opening of main pressure control valve group 4, fluid unloads oil sump tank 1.The first from left oleo-pneumatic suspension 9 inbuilt displacement sensor 8, its main oil pocket and annular chamber connect oil charging-discharging A mouth and the B mouth of the first from left double acting cylinder load-sensitive proportional throttle valve group 31 respectively, and the first from left is connected between the first from left accumulator 7 and the first from left oleo-pneumatic suspension 9 with the accumulator damper valve group 6 of blocking function；The second from left oleo-pneumatic suspension 13 inbuilt displacement sensor 12, its main oil pocket and annular chamber connect oil charging-discharging A mouth and the B mouth of the second from left double acting cylinder load-sensitive proportional throttle valve group 34 respectively, and the second from left is connected between the second from left accumulator 11 and the second from left oleo-pneumatic suspension 13 with the accumulator damper valve group 10 of blocking function；Right oleo-pneumatic suspension 17 inbuilt displacement sensor 16, its main oil pocket and annular chamber connect oil charging-discharging A mouth and the B mouth of a right double acting cylinder load-sensitive proportional throttle valve group 33 respectively, and the right side one is connected between a right accumulator 15 and a right oleo-pneumatic suspension 17 with the accumulator damper valve group 14 of blocking function；Right two oleo-pneumatic suspension 21 inbuilt displacement sensors 20, its main oil pocket and annular chamber connect oil charging-discharging A mouth and the B mouth of right two double acting cylinder load-sensitive proportional throttle valve groups 32 respectively, and the right side two is connected between right two accumulators 19 and right two oleo-pneumatic suspensions 21 with the accumulator damper valve group 18 of blocking function.
Fig. 8 is that the variable pump truck appearance adopting single-acting cylinder oleo-pneumatic suspension regulates system theory of constitution figure.This system adopts constant pressure variable displacement pump 49 to provide power, except variable pump main pressure control valve group 50 different from dosing pump main pressure control valve group 4 structural principle except, it is identical that all the other valve group functions and system connected mode regulate system with the quantitative pump truck appearance adopting single-acting cylinder oleo-pneumatic suspension.In like manner those skilled in the art can infer that the variable pump truck appearance of double acting cylinder oleo-pneumatic suspension regulates system theory of constitution figure easily.
Variable pump main pressure control valve group 50 mainly comprises overflow valve 37, by setting up the pressure of overflow valve 37, limits system maximum working pressure, sets safety margins and prevents superpressure, protects system.Variable pump controls end with the control end Kp mouth of main pressure control valve group 50 and variable pump and is connected so that system highest load pressure can entering variable pump control end through Kp mouth, in order to adjusted the parameter such as output pressure and flow of variable pump in real time by load pressure.
Fig. 9 is that the accumulator damper valve group with blocking function forms and schematic diagram.Accumulator damper valve group 6 with blocking function is connected between accumulator and pneumatic cylinder, plays buffering ground in the face of hanging the effect impacted.Accumulator damper valve group 6 with blocking function is composed in series by high-power damper valve 51 and open type 2/2-way rigid locking valve 52.High-power damper valve 51 is consistent with the structural principle of defibrillation valve 35, as shown in Figure 10, it is mainly made up of forward check valve 351, choke valve 352 and reverse 353 3 element in parallel of check valve, reaches bidirectional throttle vibration damping, reduces hydraulic shock and the purpose of surge wave concussion；After rigid locking valve 52 is energized locking, whole chassis forms rigid platfor, improves job stability.
Figure 11 is system logic principle.System provides high voltage power with motor (or electromotor), pump for power source, using oleo-pneumatic suspension as executive component, control oleo-pneumatic suspension oil charging-discharging by duty valve block and realize the change of car appearance, realized monitoring and the closed loop control of height, levelness and spring carried mass by sensing system.Control object using the position of wheel of born maximum load as system pressure and flow in system self-regulating process, the pressure in other position of wheels is monitored in real time by sensor and is compared with maximum load, realize each reasonable distribution taking turns bit traffic by linear ratio relation, reach the purpose of steadily lifting.
Figure 12 is working-flow.System control mode is divided into Non-follow control and automatically controls both of which.Under automatic control state, as long as driver operates corresponding car appearance Action Button, system according to program setting, by collecting vehicle appearance position signalling, will reach program state set in advance.When being under Non-follow control state, driver determines the time length of oleo-pneumatic suspension oil charging-discharging by controlling the time length of car appearance Action Button, thus reaching to control the effect of car appearance height；System is by being arranged in inbuilt displacement sensor within oleo-pneumatic suspension and being arranged in the obliquity sensor of body gravity position and carry out the control of car appearance vertical ground direction Bit andits control and car body load-carrying plane levelness, meeting and alarm when stroke transfinites；Axle load monitoring and pressure closed loop control, meeting and alarm when pressure limit is carried out by adding pressure transducer.
It should be noted that, skilled person can easily appreciate that, the adjustable oil gas suspended device of car appearance involved in the present invention can be arranged on different types of vehicle in the above described manner, and when without departing from the spirit and scope of the present invention being defined by the following claims, it is possible to the present invention is carried out various multi-form change and change.
Claims (1)
1. the accumulator damper valve group with blocking function, it is composed in series by high-power damper valve and open type 2/2-way rigid locking valve, and it is connected between accumulator and pneumatic cylinder, high-power damper valve is made up of forward check valve, choke valve and reverse three element in parallel of check valve, reaches bidirectional throttle vibration damping, reduces hydraulic shock and the purpose of surge wave concussion；After rigid locking valve is energized locking, whole chassis forms rigid platfor, improves job stability.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610171844.1A CN105751848B (en) | 2016-03-24 | 2016-03-24 | Accumulator vibration damping valve group with blocking function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610171844.1A CN105751848B (en) | 2016-03-24 | 2016-03-24 | Accumulator vibration damping valve group with blocking function |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105751848A true CN105751848A (en) | 2016-07-13 |
| CN105751848B CN105751848B (en) | 2018-08-21 |
Family
ID=56346268
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610171844.1A Active CN105751848B (en) | 2016-03-24 | 2016-03-24 | Accumulator vibration damping valve group with blocking function |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105751848B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106089834A (en) * | 2016-08-08 | 2016-11-09 | 湖北航天技术研究院特种车辆技术中心 | A kind of integrated control valve group |
| CN107791774A (en) * | 2017-09-21 | 2018-03-13 | 湖北航天技术研究院特种车辆技术中心 | A kind of vehicle suspension system |
| CN109606054A (en) * | 2018-11-29 | 2019-04-12 | 湖北航天技术研究院特种车辆技术中心 | A kind of damping adjustment device |
| JP2022159209A (en) * | 2021-03-31 | 2022-10-17 | ベイジンウェスト・インダストリーズ・カンパニー・リミテッド | Suspension hydraulic lift actuator for axle trim height control |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62198508A (en) * | 1986-02-25 | 1987-09-02 | Fuji Heavy Ind Ltd | Suspension cylinder control device for heavy load carrying vehicle |
| CN2454171Y (en) * | 2000-12-07 | 2001-10-17 | 郑州郑工机械集团有限责任公司 | Oil-gas suspension mechanism |
| CN201049576Y (en) * | 2007-06-14 | 2008-04-23 | 吉林大学 | Double one-way valve connecting type oil-gas suspension system |
| CN203093658U (en) * | 2013-01-22 | 2013-07-31 | 蔡言龙 | Novel oil gas suspension system |
| CN103398038A (en) * | 2013-08-14 | 2013-11-20 | 徐州徐工液压件有限公司 | Multifunctional three-way flow control valve and hydraulic system of construction machinery |
| CN104608574A (en) * | 2014-12-03 | 2015-05-13 | 中国北方车辆研究所 | Vehicle side-turn-prevention suspension device |
-
2016
- 2016-03-24 CN CN201610171844.1A patent/CN105751848B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62198508A (en) * | 1986-02-25 | 1987-09-02 | Fuji Heavy Ind Ltd | Suspension cylinder control device for heavy load carrying vehicle |
| CN2454171Y (en) * | 2000-12-07 | 2001-10-17 | 郑州郑工机械集团有限责任公司 | Oil-gas suspension mechanism |
| CN201049576Y (en) * | 2007-06-14 | 2008-04-23 | 吉林大学 | Double one-way valve connecting type oil-gas suspension system |
| CN203093658U (en) * | 2013-01-22 | 2013-07-31 | 蔡言龙 | Novel oil gas suspension system |
| CN103398038A (en) * | 2013-08-14 | 2013-11-20 | 徐州徐工液压件有限公司 | Multifunctional three-way flow control valve and hydraulic system of construction machinery |
| CN104608574A (en) * | 2014-12-03 | 2015-05-13 | 中国北方车辆研究所 | Vehicle side-turn-prevention suspension device |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106089834A (en) * | 2016-08-08 | 2016-11-09 | 湖北航天技术研究院特种车辆技术中心 | A kind of integrated control valve group |
| CN106089834B (en) * | 2016-08-08 | 2018-01-02 | 湖北航天技术研究院特种车辆技术中心 | A kind of integrated control valve group |
| CN107791774A (en) * | 2017-09-21 | 2018-03-13 | 湖北航天技术研究院特种车辆技术中心 | A kind of vehicle suspension system |
| CN109606054A (en) * | 2018-11-29 | 2019-04-12 | 湖北航天技术研究院特种车辆技术中心 | A kind of damping adjustment device |
| JP2022159209A (en) * | 2021-03-31 | 2022-10-17 | ベイジンウェスト・インダストリーズ・カンパニー・リミテッド | Suspension hydraulic lift actuator for axle trim height control |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105751848B (en) | 2018-08-21 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105782140A (en) | Double-acting-cylinder fixed displacement pump truck pose adjustment system | |
| CN105757017A (en) | Load-sensitive proportional throttle valve for double-acting cylinders | |
| CN105774460A (en) | Work procedure for vehicle posture adjusting system | |
| CN103042893B (en) | Hydro-pneumatic suspension system and engineering truck | |
| CN102673340B (en) | Oil gas hanging unwheeling appearance regulating system | |
| CN103057374B (en) | Hydro-pneumatic suspension system and engineering truck | |
| CN105751848A (en) | Energy accumulator vibration attenuation valve group with locking function | |
| CN105736488A (en) | Single-set dual-function cylinder constant delivery pump vehicle posture adjusting system | |
| CN105799443A (en) | Single-unit single-acting-cylinder metering pump car posture regulating system | |
| CN205349893U (en) | Hydro -pneumatic suspension system with synchronous lift and accent appearance function | |
| CN105805062A (en) | Quantitative pump truck posture adjustment system with single acting cylinder | |
| CN208778564U (en) | A kind of liquid gas support damping device and the vehicle using this liquid gas support damping device | |
| CN105882346B (en) | Constant displacement pump main pressure control valve group | |
| US11584187B2 (en) | Vehicle suspension system | |
| CN112895832B (en) | Vehicle posture and damping adjustment control method | |
| CN205298378U (en) | Half initiative oil gas suspension of binary channels lateral rigidity | |
| CN107116986A (en) | A kind of big stroke adjustment system of bodywork height for multi-axle heavy type vehicle | |
| CN105818635A (en) | Main pressure control valve set for variable pump | |
| CN105835650B (en) | Vehicle appearance regulating system control method | |
| CN102700380B (en) | suspension system control combination device | |
| CN106704440A (en) | Two-channel lateral rigidity semi-active hydropneumatic suspension | |
| CN105857005B (en) | Single-acting cylinder load-sensitive proportional throttle valve group | |
| CN113027975A (en) | Damping adjustable vibration reduction valve group | |
| CN106640816B (en) | Hang valve module, suspension system and engineering truck | |
| CN112895831B (en) | Multi-axle vehicle posture adjusting system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB03 | Change of inventor or designer information |
Inventor after: Chen Diejie Inventor after: Ju Haijie Inventor after: Wang Yajun Inventor after: Han Xiaoling Inventor after: Du Fu Inventor after: Xu Mengyan Inventor after: Ning Dan Inventor after: Gao Xiaodong Inventor after: Wan Yiqiang Inventor after: Mao Ming Inventor after: Zheng Guanhui Inventor after: Hou Maoxin Inventor after: Wang Hongying Inventor after: Wang Lu Inventor after: Li Biao Inventor after: Zhang Xu Inventor after: Zhang Yafeng Inventor before: Chen Diejie Inventor before: Wang Yajun Inventor before: Han Xiaoling Inventor before: Du Fu Inventor before: Xu Mengyan Inventor before: Ning Dan Inventor before: Gao Xiaodong Inventor before: Wan Yiqiang Inventor before: Zheng Guanhui Inventor before: Hou Maoxin Inventor before: Wang Hongying Inventor before: Wang Lu Inventor before: Li Biao Inventor before: Zhang Xu Inventor before: Zhang Yafeng Inventor before: Ju Haijie |
|
| CB03 | Change of inventor or designer information | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |