CN104442267A - Oil gas suspension system, engineering vehicle and crane - Google Patents
Oil gas suspension system, engineering vehicle and crane Download PDFInfo
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- CN104442267A CN104442267A CN201410627375.0A CN201410627375A CN104442267A CN 104442267 A CN104442267 A CN 104442267A CN 201410627375 A CN201410627375 A CN 201410627375A CN 104442267 A CN104442267 A CN 104442267A
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Abstract
The invention relates to the technical field of oil gas suspensions, in particular to an oil gas suspension system, an engineering vehicle and a crane. The oil gas suspension system comprises a suspension cylinder, an energy storage, a switching adjusting valve, a pedal braking valve and a power source. The switching adjusting valve is arranged on an oil in-out way of the energy storage. The switching adjusting valve has a communication state and a throttling state which are switchable. The communication mode is an initial state. An inlet of the pedal braking valve is connected to an outlet of the power source. An outlet of the pedal braking valve is connected to a control end of the switching adjusting valve. Under the normal running state of the vehicle, normal adjusting of the suspension performance cannot be affected, during vehicle emergency braking, the braking nose diving amount can be effectively lowered, so that operation stability, passing capacity and comfort during emergency braking of the vehicle are improved, and potential safety hazards are lowered.
Description
Technical field
The present invention relates to hydro pneumatic suspension technical field, particularly a kind of hydro-pneumatic suspension system, engineering truck and hoisting crane.
Background technology
Suspension (is also often called suspension, Suspension) be the general name of all force transmission connections between vehicle frame (or vehicle body) and vehicle bridge, its effect road surface is acted on the moment that the vertical reaction (supporting power) on wheel, longitudinal counter-force (tractive force and braking force) and lateral reaction and these counter-forces cause be delivered on vehicle frame by the object that people are predetermined, to ensure the normal traveling of vehicle.
Although the suspension of modern vehicle has various different version, generally all comprise the devices such as elastic element, shock absorber and guiding mechanism.Specifically, elastic element is used for making to do elasticity between vehicle frame and vehicle bridge (or wheel) and contacts, when wheel is subject to large impact, its kinetic transformation is that elastic potential energy stores by elastic element, and jump under wheel or discharge when recovering former motoring condition, thus at elastic element when playing a role, generation vibrated, the vibration continued easily makes passengers inside the car feel under the weather and tired.Bumper is used for playing damping of vibrations, and aforementioned vibration is decayed rapidly.Force and moment is transmitted in the effect of guiding mechanism, simultaneously doublely to play the guiding role, namely when wheel and vehicle frame are beated, guiding mechanism can make wheel beat relative to vehicle frame by certain track, in order to avoid affect some performance (especially road-holding property) of vehicle.
And the suspension of not all must arrange or comprise these independent devices above-mentioned certainly.Such as: in the suspension adopting steel spring to be formed, steel spring is except rising except buffer action as elastic element, when it longitudinally settles on vehicle, and when one end and vehicle frame are fixedly hinged, both transmission can have been afforded all each to force and moment, and determine the task of wheel trace, thus just without the need to arranging guiding mechanism separately.In addition, general steel spring is that multi-disc builds up, and namely itself has certain absorption capacity, thus when to vibration damping less demanding, in employing steel spring as in the suspension of elastic element, also can not fill shock absorber.
From the foregoing, no matter suspension adopts any scheme, all have the effect of suitable resilient mounting and vibration damping, thus the performance of suspension can be characterized by the characteristic comprising elastic stiffness (also referred to as suspension rate) and damping (speed corresponding to weakening) usually.
Wherein: the vehicle frame frequency of natural vibration (or claiming the natural frequency of vibrating system) that the quality (spring carried mass) 1, supported by suspension rate and suspension flexibility determines is one of suspension important performance indexes of the riding comfort affecting vehicle, the frequency that human body is accustomed to is the frequency of walking health up-and-down movement, is about 1 ~ 1.6Hz.Vehicle frame frequency of natural vibration should be in or as much as possible close to this frequency limit, according to mechanical analysis, if vehicle to be regarded as the quality that is made single-degree of freedom vibration on resilient suspension, then the frequency of natural vibration (natural frequency) of suspension system is:
in formula:
G is acceleration due to gravity;
F is suspension vertical deformation (amount of deflection);
M is suspension spring carried mass;
The vertical load on suspension is added on needed for the unit distance (even if suspension produces specific vertical compressive deformation) that K (=M/f) instigates wheel center relative frame to move up for suspension rate (needing not be equal to the rigidity of elastic element).
From above formula: (1) is vertical load one timing suffered by suspension, suspension rate is less, then vehicle frequency of natural vibration is lower, but suspension rate is less, suspension vertical deformation is just larger under certain loads, and this as lorry etc. for the large vehicle of spring carried mass, is structurally difficult to guarantee and reaches perfect condition, thus in fact the vehicle frame frequency of natural vibration of lorry is often higher, and substantially exceeds above-mentioned desirable frequency limit.(2) when suspension rate one timing, spring carried mass is larger, then suspension vertical deformation is larger, and frequency of natural vibration is lower, thus vehicle frame frequency of natural vibration when empty wagons travels is than high during fully loaded traveling, and spring carried mass variation range is larger, then frequency range is also larger.
2, the damping of vibration damping is larger, and vibration is cut down faster, for the decay of frame weaving, contributes to the comfort level improved ride of vehicle and improve passengers inside the car.
The elastic stiffness of early stage suspension system and damping are generally determined by the method for experience or optimal design, according to the suspension frame structure (suspension formed by steel spring exemplified as aforementioned) of these parameter designing, in vehicle traveling process, its performance is constant, also be difficult to regulate, vehicle riding comfort and travelling comfort are under some influence.Therefore usually traditional suspension system is called passive suspension system.If the rigidity of suspension system and damping force characteristics can carry out dynamic self-adapting adjustment according to the motoring condition of vehicle (state of kinematic motion and condition of road surface etc. as vehicle), make suspension system be in better or best elastic damping state all the time, be then called active suspension system.
The design original intention of active suspension system can be released from aforementioned " 1 " and " 2 " 2 amplification, that is: in order to make vehicle frame frequency of natural vibration spring carried mass be equivalent to vehicle from zero load to fully loaded scope in change time, remain unchanged or change very little, with regard to needing, the rigidity Design of suspension is become variable, namely during empty wagons, suspension rate is little, and during load increase, the rigidity of suspension increases thereupon; In addition, the dumping force of shock absorber is larger, vibration is cut down faster, but the effect of elastic element in parallel can not be given full play to, simultaneously, excessive dumping force also may cause shock absorber union piece and vehicle frame to damage, thus, desirable state is, in suspension compresses stroke (stroke that vehicle bridge and vehicle frame shift near mutually), the dumping force of shock absorber should be little, to make full use of the elasticity of elastic element, to relax impact, in suspension extension stroke in (vehicle bridge and vehicle frame mutually away from stroke), the dumping force of shock absorber should be large, in the hope of rapid vibration damping.
Whether active suspension system comprises propulsion source by it can be divided into full active suspension (active active suspension) and the large class of semi-active suspension (passive active suspension) system two.Certainly, in some documents, strictly do not distinguish the boundary of semi-active suspension system and full active suspension system, as long as but think to have extra power to change dynamic characteristic, this suspension system is just referred to as " initiatively ".
Full active suspension system can according to the state of kinematic motion of vehicle and pavement state, and in time the rigidity of adjustable suspension and damping, make it be in best elasticity and vibration damping state.It is the device of an additional controlled application force in the passive suspension of tradition (elastic element, shock absorber, guide piece) system, this device usually by actuating unit, measuring system, feedback control system and energy resource system four part form.The effect of actuating unit is the instruction of executive control system, is generally producer or torque generator (hydraulic actuating cylinder, cylinder, servomotor torque constant, electromagnet etc.).The effect of measuring system is the various state of measuring system, for control system provides foundation, comprises various sensor.The effect of control system is processing data and sends various control command, and its core component is automatic computer.The effect of energy resource system is for above each several part provides energy.
Semi-active suspension system can regulate the characteristic of in elastic stiffness and damping usually, but, owing to changing damping characteristic, comparatively to change elastic stiffness easier, so for a long time, the research of semi-active suspension system mainly concentrates on the damping coefficient aspect regulating shock absorber, i.e. the spring of this semi-active suspension system primarily of immutable rigidity and the shock absorber composition of adaptive damping.In addition, because the complex structure of full active suspension system, manufacture and maintenance cost are high, and semi-active suspension system on Control platform close to full active suspension system and structure is simple, energy consumption is little, thus extensive application.
At present, hydro-pneumatic suspension system is comparatively common a kind of suspension system, hydro-pneumatic suspension system is similar to passive suspension system in design, but has the version of semi-active suspension system, and has the partial function and performance that only have semi-active suspension system to realize.So-called hydro-pneumatic suspension system refers to that its elastic element is energy storage, and damping element is then the cutoff port, check valve etc. of suspension cylinder inside using fluid transmission of pressure, with a kind of suspension of unreactable gas (being generally nitrogen) as elastic medium.At present, hydro-pneumatic suspension system has been widely used in special vehicle and full size vehicle (as full Terrain Cranes).
In periodical " construction machinery and equipment " 11 phases in 2003 the 7th page, " feature of hydro pneumatic suspension and structural principle analysis thereof " literary composition describes structure and the groundwork of hydro-pneumatic suspension system in detail, can learn from this article, the principal character of hydro-pneumatic suspension system is as follows: 1. non-linear rigidity, traditional suspension is mostly linear because of the rigidity of elastic element and its stiffness characteristics is remained unchanged substantially, and in hydro pneumatic suspension, the rigidity of elastic element has non-linear, the feature of cumulative (subtracting), this just can realize vehicle and travel smooth-going in flat road surface, road surface inferior make it keep certain moving velocity because suspension absorbs more impact energy, 2. non-linear damping, can suppress rapidly the vibration of vehicle frame, has damping preferably, 3. chassis frame height free adjustment, by regulating while suspension cylinder or separately, chassis frame height can oscilaltion, front and back lifting or left and right lifting, this to improve vehicle by performance and rideability very important, 4. rigid locking, by the connection oil circuit of cutting-off liquid cylinder pressure and energy storage and other Hydraulic Elements, utilizes the feature that oil compressibility is less, hydro pneumatic suspension can be made to be in rigid state, and vehicle can bear larger load and can slowly movement under these conditions.5. improve vehicle movement performance, the difference crisscross by suspension connects, and can improve some exercise performance (as roll motion, luffing etc.) of vehicle, suitably alleviates the phenomenon etc. of nodding when vehicle launch and brake.6. unit stored energy ratio is large, and this feature is advantageous particularly to heavy-duty vehicle, effectively can alleviate quality and the scantling of structure of suspension.
Therefore, a kind of hydro-pneumatic suspension system for hoisting crane propons exemplified in aforementioned " feature of hydro pneumatic suspension and structural principle analysis thereof " literary composition can realize several functions, as rigid suspension, resilient suspension, car load lifting, one-sided lifting, car load leveling etc.
In addition, in the prior art, as number of patent application be 200820005216.7,201010597697.7,201210578734.9,201220070120.5,201310247101.4, hydro pneumatic suspension (suspension) system disclosed in the Chinese patent literature such as 201320776004.X and 201410151307.1 or device can realize aforementioned 1. to the function that 6. at least one feature is corresponding respectively.
Wherein, be in the document of 200820005216.7 at number of patent application, on the basis of traditional hydro-pneumatic suspension system, the damper being integrated in suspension cylinder is separated, on energy storage connecting line between energy storage and suspension cylinder, arrange independently damping flow regulating valve, and arrange heat abstractor on the valve body of this damping flow regulating valve, the heat energy produced when flowing through damper to make fluid is quickly released.
Be in the document of 201010597697.7 at number of patent application, in hydraulic control circuit, adopt two three position four-way directional control valves respectively with the connection of left suspension oil cylinder and right suspension oil cylinder, by controlling the position of change-over valve, vehicle bridge can be realized and initiatively promote, instead of making the passive retraction of oil cylinder by car weight, like this, after hoisting crane accomplishes fluently supporting leg, by oil pressure, vehicle bridge can be mentioned, improve chassis maintainability.In addition, left and right suspension oil cylinder can realize the elevating control function of both sides suspension oil cylinder by corresponding change-over valve and displacement pickup, thus realizes vehicle body attitude adjustment; Left and right suspension oil cylinder both can carry out one-sided separate connection, also can carry out intersection to be communicated with, can also connect completely, simultaneously, left and right suspension oil cylinder rigid locking is realized by the connection cutting off energy storage and oil cylinder, therefore, at least four kinds of road driving patterns can be realized, like this, adopt multiple on-off valve can realize intersecting connection respectively, be communicated with completely, one-sided separate connection also has rigid locking four kinds of road driving patterns, thus improves road adaptive capacity.
Be in the document of 201210578734.9 at number of patent application, in hydraulic control circuit, by the state of control both direction control cock and/or the state of two electric proportional valves, to enable its road-driving mode (suspension cylinder is communicated with+meter out control with energy storage), non-blocking mode (suspension cylinder and energy storage disconnect) or elevating control pattern (external control is oil-filled); In addition, in one implementation, the damping arrangement in its hydraulic control circuit can comprise a check valve, two damping holes in parallel and a directional control valve, makes damping realize having level adjustable.
Be in the document of 201220070120.5 at number of patent application, be that a kind of scheme in the document of 201210578734.9 is similar with number of patent application, in hydraulic control circuit, at the rod chamber of suspension cylinder or be arranged in parallel damping hole, check valve and electrohydraulic servo valve between rodless cavity with corresponding energy storage, there is level adjustable to realize damping.
Be in the document of 201310247101.4 at number of patent application, in hydraulic control circuit, between each suspension cylinder and between suspension cylinder and corresponding energy storage, adopt multiple change-over valve and valve group of intersecting, the various states of vehicle bridge can be realized, and lock-out state and load equalization can be realized.
Be in the document of 201320776004.X at number of patent application, in hydraulic control circuit, between each suspension cylinder and between suspension cylinder and corresponding energy storage, adopt multiple solenoid directional control valve, the active that can realize suspension cylinder is stretched, and then realizes the function of vehicle bridge active lifting.
Be in the document of 201410151307.1 at number of patent application, provide a kind of hydro pneumatic suspension, hydro pneumatic suspension for hoisting crane in this hydro pneumatic suspension and aforementioned " feature of hydro pneumatic suspension and structural principle analysis thereof " is similar, can avoid causing vehicle bridge progressively downward trend because energy storage pressure is not enough or a certain vehicle bridge is overweight in hydro pneumatic suspension.
As previously mentioned, due to many merits and the performance of hydro-pneumatic suspension system, be thus widely used in hoisting crane or engineering truck, smooth-going to make vehicle travel on road surface, be conducive to the exercise performance improving vehicle, and the phenomenon of nodding when suitably can alleviate vehicle brake.But present inventor is realizing finding in process of the present invention: in prior art, when the slow braking brake of vehicle, the braking nose dive amount that hydro-pneumatic suspension system produces is in certain limit, may can not have a strong impact on operational stability and the traveling comfort of vehicle, but, if vehicle meet with emergency case and emergency braking brake time, in the process that this is extremely short, the transfer rapidly of vehicle antero posterior axis load, be there is conversion obvious and rapidly in the adhesive ability causing vehicle antero posterior axis in longitudinal direction and side direction, the head of vehicle is sunk rapidly, afterbody lifts rapidly, cause braking nose dive amount excessive, have a strong impact on road-holding property and the comfort level of vehicle, in addition, braking nose dive amount is crossed conference and is caused the dynamic ground Clearance of vehicle obviously to reduce, thus affect the crossing ability of vehicle, consider that engineering truck or hoisting crane etc. are trudged often in field, under the rugged environments such as mountains and rivers, the excessive braking nose dive amount that this emergency brake produces substantially increases potential safety hazard, in addition, although the hydro-pneumatic suspension system of prior art (if number of patent application is the scheme disclosed in the document of 201210578734.9 and 201220070120.5) also may have the function of the multistage adjustment of damping, in normal driving process, damping can regulate in higher level by chaufeur or corresponding mechanism, to adapt to the change of road conditions, but chaufeur or corresponding mechanism are difficult to predict emergency case, and when vehicle meets with emergency case, emergency braking brakes, within the extremely short time, chaufeur or corresponding mechanism also have little time damping to regulate in higher level, thus braking nose dive amount cannot be reduced in time.
Therefore, how to improve for this deficiency, effectively reducing the braking nose dive amount of vehicle when emergency brake, is the direction of present inventor's effort always.
Summary of the invention
In view of this, the present invention aims to provide a kind of hydro-pneumatic suspension system, a kind of engineering truck and a kind of hoisting crane, make vehicle at normal motoring condition time can not disturb the normal regulating of its suspension property, and the braking nose dive amount of vehicle effectively can be reduced during emergency brake of vehicle, thus improve the road-holding property of vehicle when emergency braking, crossing ability and traveling comfort, reduce potential safety hazard.
Particularly, this hydro-pneumatic suspension system comprises suspension cylinder and energy storage, also comprise and switch control cock, pedal brake valve and propulsion source, wherein: described switching control cock is arranged on the inlet and outlet of fuel channel of described energy storage, described switching control cock has switchable connected state and throttle, and described connected state is initial condition; The import of described pedal brake valve is connected to the outlet of described propulsion source, and the outlet of described pedal brake valve is connected to the control end of described switching control cock.
Further, described pedal brake valve is proportional pressure-reducing valve, and the throttle of described switching control cock is ratio throttle.
Further, described propulsion source is source of the gas.
Further, described source of the gas is air receiver or air pump
In addition, this project vehicle comprises chassis, described chassis comprises vehicle bridge, vehicle frame and brake pedal, the hydro-pneumatic suspension system described in above-mentioned any one is provided with between described vehicle bridge and described vehicle frame, wherein, the cylinder barrel of described suspension cylinder is connected to described vehicle bridge, and the piston rod of described suspension cylinder is connected to described vehicle frame, and the control end of described pedal brake valve is connected with described brake pedal.
Further, described chassis is equipped with Pneumatic brake system, and when described propulsion source is source of the gas, described source of the gas comes from described Pneumatic brake system.
Further, the number of described suspension cylinder is at least one pair of, and suspension cylinder described at least one pair of is arranged between vehicle bridge before described engineering truck center of gravity and vehicle frame, or between the vehicle bridge be arranged at after described engineering machinery vehicle center of gravity and vehicle frame.
Further, described vehicle bridge comprises and turns to vehicle bridge, turns between vehicle bridge and described vehicle frame described in suspension cylinder described at least one pair of is arranged at.
In addition, this hoisting crane comprises the engineering truck described in above-mentioned any one and is arranged at the device of boarding of this project vehicle.
Further, described hoisting crane is full Terrain Cranes.
Present inventor is obtaining aforementioned various scheme after further investigation.After adopting either a program of the present invention, when vehicle is during road surface normally travels, chaufeur loosen the brake, pedal brake valve is not operating, propulsion source is not to the switching control cock pipage control energy be positioned on energy storage inlet and outlet of fuel channel, switch control cock and be in initial condition, energy storage can freely with between hydraulic control circuit or suspension cylinder be coordinated, to realize the adjustment of suspension property under normal motoring condition, if meet with emergency case in the process of moving, chaufeur emergency braking, pedal brake pedal, the meanwhile rapid action of pedal brake valve, the power that propulsion source is exported acts on the control end to switching control cock immediately, switch control cock and switch to throttle immediately, energy storage can not freely with between hydraulic control circuit or suspension cylinder be coordinated, and then the degree of freedom making energy storage pass in and out fluid is restricted, resistance to shock and/or the elastic stiffness of suspension system can be improved so largely, thus effectively reduce the braking nose dive amount of vehicle, improve the road-holding property of vehicle when emergency braking, crossing ability and traveling comfort, reduce potential safety hazard.In addition, suspension system of the present invention crosses multiple component without the need to additional configuration, and structure is simple, realizes cost low.
Accompanying drawing explanation
The accompanying drawing forming a part of the present invention is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
The principle schematic of a kind of hydro-pneumatic suspension system that Fig. 1 provides for the embodiment of the present invention;
Fig. 2 is the structural representation of pedal brake valve in hydro-pneumatic suspension system shown in Fig. 1;
Fig. 3 is for switching the structural representation of control cock in hydro-pneumatic suspension system shown in Fig. 1.
Major label description in figure:
1 suspension cylinder
2 energy storages
3 inlet and outlet of fuel channel
4 switch control cock
5 pedal brake valves
6 propulsions source
7 hydraulic control circuits
41 connected states
42 throttles
Detailed description of the invention
To it should be pointed out that in this part to the description of concrete structure and description order it is only explanation to specific embodiment, should not be considered as there is any restriction to protection scope of the present invention.In addition, when not conflicting, the embodiment in this part and the feature in embodiment can combine mutually.
Please also refer to Fig. 1, Fig. 2 and Fig. 3, below the hydro-pneumatic suspension system of accompanying drawing to the embodiment of the present invention is elaborated.
Shown in composition graphs 1, the hydro-pneumatic suspension system of this embodiment can comprise at least one pair of suspension cylinder 1 (shown in figure be two to), energy storage 2, switch control cock 4, pedal brake valve 5, propulsion source 6 and hydraulic control circuit 7.
Wherein, be connected by hydraulic control circuit 7 between each suspension cylinder 1 or between suspension cylinder 1 with energy storage 2, hydraulic control circuit 7 can have multiple implementation, specifically can with reference to associated description of the prior art, such as can with reference to the hydraulic control circuit various of the prior art mentioned in background technology part, hydraulic control circuit can comprise some hydraulic tubings, or some hydraulic tubings and some change-over valves can be comprised, or some hydraulic tubings can be comprised, some change-over valves and some damping arrangements, in the present invention this is not construed as limiting, suspension cylinder 1, engagement process between hydraulic control circuit 7 and energy storage 2 and hydraulic control circuit 7 can see the related description of prior art with the annexation of Hydraulic Station, this part is not the emphasis of the embodiment of the present invention, thus do not launch to describe.
Switching control cock 4 is arranged on the inlet and outlet of fuel channel 3 of energy storage 2, and shown in composition graphs 3, switch control cock 4 and have switchable connected state 41 and throttle 42, wherein, connected state 41 is initial condition.The import of pedal brake valve 5 is connected to the outlet of (being communicated in) propulsion source 6, the outlet of pedal brake valve 5 is connected to the control end that (being communicated in) switches control cock 4, shown in composition graphs 2, the operating state of pedal brake valve 5 can be corresponding with the state of brake pedal on vehicle, when brake pedal is trampled to desired location, pedal brake valve 5 action, when brake pedal is released, pedal brake valve 5 is not operating.In addition, pedal brake valve 5 can be communicated with the outlet of propulsion source 6 and switch the control end of control cock 4 when action, when not operating, can cut off the outlet of propulsion source 6 and being communicated with between the control end switching control cock 4.
Be applied to vehicle for above-mentioned hydro-pneumatic suspension system below and the principle of work of this hydro-pneumatic suspension system is described in conjunction with concrete scene: when vehicle is during road surface normally travels, chaufeur loosen the brake, pedal brake valve 5 is not operating, propulsion source 6 is not to the switching control cock 4 pipage control energy be positioned on energy storage 2 inlet and outlet of fuel channel 3, switch control cock 4 and be in initial condition, energy storage 2 can freely with between hydraulic control circuit 7 or suspension cylinder 1 be coordinated, to realize the normal regulating of suspension property under normal motoring condition.If meet with emergency case in the process of moving, chaufeur emergency braking, pedal brake pedal, meanwhile pedal brake valve 5 action rapidly, the power that propulsion source 6 is exported acts on the control end to switching control cock 4 immediately, switch control cock 4 and switch to throttle immediately, and then energy storage 2 can not freely with between hydraulic control circuit 7 or suspension cylinder 1 be coordinated, resistance to shock and/or the elastic stiffness of suspension system can be improved so largely, thus effectively reduce the braking nose dive amount of vehicle, improve the road-holding property of vehicle when emergency braking, crossing ability and traveling comfort, reduce potential safety hazard.In addition, from the foregoing, hydro-pneumatic suspension system of the present invention, on the basis of traditional hydro-pneumatic suspension system, crosses multiple component without the need to additional configuration, and structure is simple, realizes cost low.After emergency brake terminates, chaufeur loosen the brake, pedal brake valve 5 returns to not operating state, and then makes switching control cock 4 return to initial condition, thus can not interfere with vehicles continuation travel.
In specific implementation process, the hydro-pneumatic suspension system of above-described embodiment can also adopt some prioritization schemes, such as, pedal brake valve 5 can adoption rate reducing valve, correspondingly, the throttle 42 switching control cock 4 can be ratio throttle, the operating state of such pedal brake valve 5 can be corresponding by the angle of trampling with brake pedal, and then make the delivery pressure of pedal brake valve 5 also be in predetermined state, after this delivery pressure effect to the control end of switching control cock 4, throttle 42 is also in corresponding throttle degree, effective control of braking nose dive amount when emergency braking brakes can be improved so further, and the operational stability of vehicle when emergency braking brakes can be improved further, crossing ability and traveling comfort.
And for example, propulsion source 6 can adopt source of the gas, and correspondingly, pedal brake valve 5 is pneumatic valve, switching control cock 4 is Pneumatical hydraulic value, and on this basis, source of the gas can be air receiver or air pump, when adopting air receiver, air receiver can arrange safety valve, to ensure the pressure security of air receiver.
It should be noted that, in the prior art, such as, " feature of hydro pneumatic suspension and structural principle analysis thereof " described in background technology part, 200820005216.7, 201010597697.7, 201210578734.9, 201220070120.5, 201310247101.4, 201320776004.X with in 201410151307.1 documents such as grade, what have annexation with the inlet and outlet of fuel channel of energy storage can be switch valve, one-way throttle valve or one-way throttling device, damping arrangement or unidirectionally have grade damping adjustment device etc., these parts otherwise be in order to cut off suspension cylinder and energy storage contact realize the additional functions such as rigid locking, for coordinating with energy storage to realize the normal regulating of suspension property under normal motoring condition, and the technical scheme of these prior aries is all difficult to effectively reduce the nod amount of vehicle when emergency braking brakes, but, in the invention described above embodiment, the effect switching control cock 4 is not identical or equivalent with the effect of these parts above-mentioned, reason is: switch control cock 4 and pedal brake valve 5, propulsion source 6 etc. combines, energy storage and coordinating between hydraulic control circuit or suspension cylinder can not be disturbed when normal vehicle operation, namely the adjustment of suspension property under normal motoring condition can not be disturbed, and can when vehicle meets with emergency case emergency brake, the degree of freedom making energy storage pass in and out fluid is restricted, resistance to shock and/or the elastic stiffness of suspension system can be improved so largely, thus effectively reduce the braking nose dive amount of vehicle.In other words, hydraulic control circuit 7 part of the hydro-pneumatic suspension system of the embodiment of the present invention also can adopt the hydraulic connecting scheme in arbitrary prior art between suspension cylinder and energy storage, and the setting switching control cock 4 and pedal brake valve 5, propulsion source 6 etc. can not affect hydraulic control circuit 7 and play a role under non-emergent braking state.
The present invention other the first embodiment still provides a kind of engineering truck, this project vehicle comprises chassis, this chassis comprises vehicle bridge, vehicle frame and brake pedal, this project machinery also comprises the hydro-pneumatic suspension system of above-described embodiment, this hydro-pneumatic suspension system is arranged between this vehicle bridge and this vehicle frame, wherein, the cylinder barrel of suspension cylinder 1 is connected to this vehicle bridge, and the external part of the piston rod of suspension cylinder 1 is connected to vehicle frame.
On this basis, this project vehicle can also comprise the Pneumatic brake system be provided on chassis, correspondingly, propulsion source 6 can adopt the source of the gas coming from this Pneumatic brake system, like this when this project car sudden stop, the master cylinder gas circuit of Pneumatic brake system simultaneously for the air operated control of aerodynamic brake and suspension petroleum system provides power, can improve the conformability of control, and contribute to simplifying and arrange and structure, reduce extra cost.
During concrete enforcement, at least one pair of suspension cylinder 1 can be arranged between vehicle bridge (propons) before engineering truck center of gravity and vehicle frame correspondence position, also can be arranged between vehicle bridge (back axle) after this center and vehicle frame correspondence position.In addition, at least one pair of suspension cylinder 1 can be arranged at turn to vehicle bridge corresponding with vehicle frame position between.
In addition, during concrete enforcement, in order to ensure the state of pedal brake valve 5 and brake pedal to trample angle corresponding, mechanicalness can be adopted between the control end of pedal brake valve 5 and brake pedal to connect, such as can adopt connecting rod connection mode, make when brake pedal is trampled predetermined angular, under the transmission of connecting rod, occur in the control end of pedal brake valve 5 that corresponding position adjusts, thus under making pedal brake valve 5 be in corresponding state.
Because above-mentioned hydro-pneumatic suspension system has above-mentioned technique effect, therefore, this project vehicle effectively can improve exercise performance, safety performance and carrying capacity during emergency brake, the specific implementation process of its appropriate section and the hydro-pneumatic suspension system of above-described embodiment similar, the specific implementation process of other parts see the associated description of prior art, hereby can not repeat.
Other the second embodiments of the present invention also provide a kind of hoisting crane, and as full Terrain Cranes, this hoisting crane comprises other engineering trucks described in the first embodiment above-mentioned and the device of boarding be arranged on this project vehicle.
Because above-mentioned engineering truck has above-mentioned technique effect, therefore, the transport performance of this hoisting crane and safety performance obtain effective raising, the specific implementation process of its appropriate section is similar to the above embodiments, the specific implementation process of other parts see the associated description of prior art, hereby can not repeat.
The foregoing is only preferred embodiment of the present invention, not in order to limit the present invention, within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (10)
1. a hydro-pneumatic suspension system, comprises suspension cylinder (1) and energy storage (2), it is characterized in that, also comprises and switches control cock (4), pedal brake valve (5) and propulsion source (6), wherein:
Described switching control cock (4) is arranged on the inlet and outlet of fuel channel (3) of described energy storage (2), described switching control cock (4) has switchable connected state (41) and throttle (42), and described connected state (41) is initial condition;
The import of described pedal brake valve (5) is connected to the outlet of described propulsion source (6), and the outlet of described pedal brake valve (5) is connected to the control end of described switching control cock (4).
2. hydro-pneumatic suspension system as claimed in claim 1, it is characterized in that, described pedal brake valve (5) is proportional pressure-reducing valve, and the throttle (42) of described switching control cock (4) is ratio throttle.
3. hydro-pneumatic suspension system as claimed in claim 1 or 2, it is characterized in that, described propulsion source (6) is source of the gas.
4. hydro-pneumatic suspension system as claimed in claim 3, it is characterized in that, described source of the gas is air receiver or air pump.
5. an engineering truck, comprise chassis, described chassis comprises vehicle bridge, vehicle frame and brake pedal, it is characterized in that, be provided with the hydro-pneumatic suspension system described in any one of Claims 1-4 between described vehicle bridge and described vehicle frame, wherein, the cylinder barrel of described suspension cylinder (1) is connected to described vehicle bridge, the piston rod of described suspension cylinder (1) is connected to described vehicle frame, and the control end of described pedal brake valve (5) is connected with described brake pedal.
6. engineering truck as claimed in claim 5, it is characterized in that, described chassis is equipped with Pneumatic brake system, described propulsion source (6) for source of the gas when, described source of the gas comes from described Pneumatic brake system.
7. engineering truck as claimed in claim 5, it is characterized in that, the number of described suspension cylinder (1) is at least one pair of, suspension cylinder described at least one pair of (1) is arranged between vehicle bridge before described engineering truck center of gravity and vehicle frame, or between the vehicle bridge be arranged at after described engineering machinery vehicle center of gravity and vehicle frame.
8. engineering truck as claimed in claim 7, is characterized in that, described vehicle bridge comprises and turns to vehicle bridge, turns between vehicle bridge and described vehicle frame described in suspension cylinder described at least one pair of (1) is arranged at.
9. a hoisting crane, is characterized in that, described hoisting crane comprises the engineering truck described in any one of claim 5 to 8 and is arranged at the device of boarding of this project vehicle.
10. hoisting crane as claimed in claim 9, it is characterized in that, described hoisting crane is full Terrain Cranes.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201410627375.0A CN104442267A (en) | 2014-11-10 | 2014-11-10 | Oil gas suspension system, engineering vehicle and crane |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410627375.0A CN104442267A (en) | 2014-11-10 | 2014-11-10 | Oil gas suspension system, engineering vehicle and crane |
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| CN104442267A true CN104442267A (en) | 2015-03-25 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410627375.0A Pending CN104442267A (en) | 2014-11-10 | 2014-11-10 | Oil gas suspension system, engineering vehicle and crane |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105946831A (en) * | 2016-06-13 | 2016-09-21 | 朱明德 | Auxiliary braking device of vehicle |
| CN106004841A (en) * | 2016-06-13 | 2016-10-12 | 朱明德 | Braking method for vehicle boost baking device |
| CN107031330A (en) * | 2016-12-05 | 2017-08-11 | 安徽江淮汽车集团股份有限公司 | Automobile anti-nod control system and control method, damper |
| CN108162709A (en) * | 2017-12-15 | 2018-06-15 | 江苏理工学院 | A kind of electronic controlled suspension and ABS cooperative control devices |
| CN108216166A (en) * | 2017-12-15 | 2018-06-29 | 江苏理工学院 | A kind of electronic controlled suspension and ABS coordinated control systems |
| CN110450592A (en) * | 2019-08-07 | 2019-11-15 | 三一重型装备有限公司 | Oil gas suspended device and engineering truck |
| CN111301086A (en) * | 2019-11-29 | 2020-06-19 | 徐工集团工程机械股份有限公司 | Engineering truck, hydro-pneumatic suspension system and control method of hydro-pneumatic suspension system |
| CN112172440A (en) * | 2020-10-19 | 2021-01-05 | 合肥工业大学 | Active control device for resisting front pitching of car during braking |
| CN113525009A (en) * | 2021-06-04 | 2021-10-22 | 湖北优软汽车科技有限公司 | Two-stage pressure type single swing arm structure oil gas suspension system |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59102610A (en) * | 1982-12-02 | 1984-06-13 | Isuzu Motors Ltd | Air-spring type suspension apparatus |
| US4856813A (en) * | 1987-10-15 | 1989-08-15 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Vehicle suspension apparatus |
| US5150917A (en) * | 1990-05-31 | 1992-09-29 | Nissan Motor Company, Limited | Active suspension system with control to change variation in pressure of working fluid cylinder between increase and decrease thereof |
| US5239471A (en) * | 1990-03-06 | 1993-08-24 | Nissan Motor Co., Ltd. | Actively controlled suspension system for automotive vehicles |
| CN1880114A (en) * | 2005-02-23 | 2006-12-20 | 哈尔德克斯制动器公司 | Air suspension system with supply air restriction valve |
| CN201193191Y (en) * | 2008-03-13 | 2009-02-11 | 广东力士通机械股份有限公司 | Tire crane |
| CN202507887U (en) * | 2012-02-29 | 2012-10-31 | 三一汽车起重机械有限公司 | Variable damping oil gas suspension system and crane |
| CN102837694A (en) * | 2012-09-17 | 2012-12-26 | 三一重通机械有限公司 | Electrical control brake system of bulldozer and bulldozer |
-
2014
- 2014-11-10 CN CN201410627375.0A patent/CN104442267A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59102610A (en) * | 1982-12-02 | 1984-06-13 | Isuzu Motors Ltd | Air-spring type suspension apparatus |
| US4856813A (en) * | 1987-10-15 | 1989-08-15 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Vehicle suspension apparatus |
| US5239471A (en) * | 1990-03-06 | 1993-08-24 | Nissan Motor Co., Ltd. | Actively controlled suspension system for automotive vehicles |
| US5150917A (en) * | 1990-05-31 | 1992-09-29 | Nissan Motor Company, Limited | Active suspension system with control to change variation in pressure of working fluid cylinder between increase and decrease thereof |
| CN1880114A (en) * | 2005-02-23 | 2006-12-20 | 哈尔德克斯制动器公司 | Air suspension system with supply air restriction valve |
| CN201193191Y (en) * | 2008-03-13 | 2009-02-11 | 广东力士通机械股份有限公司 | Tire crane |
| CN202507887U (en) * | 2012-02-29 | 2012-10-31 | 三一汽车起重机械有限公司 | Variable damping oil gas suspension system and crane |
| CN102837694A (en) * | 2012-09-17 | 2012-12-26 | 三一重通机械有限公司 | Electrical control brake system of bulldozer and bulldozer |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106004841B (en) * | 2016-06-13 | 2018-06-29 | 陈雅婷 | A kind of braking method of vehicle booster brake apparatus |
| CN106004841A (en) * | 2016-06-13 | 2016-10-12 | 朱明德 | Braking method for vehicle boost baking device |
| CN105946831A (en) * | 2016-06-13 | 2016-09-21 | 朱明德 | Auxiliary braking device of vehicle |
| CN105946831B (en) * | 2016-06-13 | 2018-06-29 | 青岛华瑞丰机械有限公司 | Vehicle booster brake apparatus |
| CN107031330A (en) * | 2016-12-05 | 2017-08-11 | 安徽江淮汽车集团股份有限公司 | Automobile anti-nod control system and control method, damper |
| CN108216166A (en) * | 2017-12-15 | 2018-06-29 | 江苏理工学院 | A kind of electronic controlled suspension and ABS coordinated control systems |
| CN108162709A (en) * | 2017-12-15 | 2018-06-15 | 江苏理工学院 | A kind of electronic controlled suspension and ABS cooperative control devices |
| CN108162709B (en) * | 2017-12-15 | 2020-05-22 | 江苏理工学院 | Coordination control device for electric control suspension and ABS |
| CN108216166B (en) * | 2017-12-15 | 2020-08-25 | 江苏理工学院 | Electronic control suspension and ABS (anti-lock brake system) linkage control system |
| CN110450592A (en) * | 2019-08-07 | 2019-11-15 | 三一重型装备有限公司 | Oil gas suspended device and engineering truck |
| CN110450592B (en) * | 2019-08-07 | 2024-04-05 | 三一重型装备有限公司 | Hydro-pneumatic suspension device and engineering vehicle |
| CN111301086A (en) * | 2019-11-29 | 2020-06-19 | 徐工集团工程机械股份有限公司 | Engineering truck, hydro-pneumatic suspension system and control method of hydro-pneumatic suspension system |
| CN111301086B (en) * | 2019-11-29 | 2024-03-08 | 徐工集团工程机械股份有限公司 | Engineering truck, hydro-pneumatic suspension system and control method of hydro-pneumatic suspension system |
| CN112172440A (en) * | 2020-10-19 | 2021-01-05 | 合肥工业大学 | Active control device for resisting front pitching of car during braking |
| CN113525009A (en) * | 2021-06-04 | 2021-10-22 | 湖北优软汽车科技有限公司 | Two-stage pressure type single swing arm structure oil gas suspension system |
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Application publication date: 20150325 |