CN105398304A - Semi-active both-way energy-feedback oil gas suspension system of truck - Google Patents
Semi-active both-way energy-feedback oil gas suspension system of truck Download PDFInfo
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- CN105398304A CN105398304A CN201410387589.5A CN201410387589A CN105398304A CN 105398304 A CN105398304 A CN 105398304A CN 201410387589 A CN201410387589 A CN 201410387589A CN 105398304 A CN105398304 A CN 105398304A
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Abstract
The invention discloses a semi-active both-way energy-feedback oil gas suspension system of a truck. The semi-active both-way energy-feedback oil gas suspension system mainly comprises a steel plate spring, a lifting lug, an oil cylinder connecting rod, a first oil cylinder, a second oil cylinder, an air cylinder, an oil-water separator, an air supercharger and an air storage tank which are sequentially connected. In the traveling process of the truck, oil liquid is driven by rotation motion of the lifting lug to flow from the first oil cylinder to the second oil cylinder, the second oil cylinder is further driven to compress gas of the air cylinder, and therefore air inflation to the air storage tank is achieved. By means of the semi-active both-way energy-feedback oil gas suspension system of the truck, the using reliability, the overall vehicle comfort and the energy recycling efficiency can be greatly improved.
Description
Technical field
The invention belongs to load-carrying vehicle energy regenerating field, be specifically related to a kind of load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system.
Background technology
Economy and traveling comfort are the important indicators evaluating automotive performance.At present, each car production producer is all in the low oil consumption of pursuit, and energy regenerating is reduce oil consumption raising economy to open new effective way.Under the overall situation of international economy crisis and domestic fuel oil transforming administrative fees into taxes, carry out the recovery of Vehicular vibration energy, for dissipative system, improve fuel economy significant.Along with the develop rapidly with auto trade that improves constantly of living standard, people have higher requirement to car load traveling comfort, and suspension system directly affects the traveling comfort of car load.When Car design, car load economy and traveling comfort are organically combined significant.Therefore, suspension design and vibration energy regeneration are organically combined, design and vehicle riding comfort can be made best and vibration energy regeneration efficiency is high suspension system has important practical is worth.
At present, compressor cylinder energy regenerative mainly contains two kinds: one adopts the unidirectional energy regenerative of cylinder; Another kind adopts the unidirectional energy regenerative of oil cylinder.These two kinds of energy regenerative methods all belong to unidirectional energy regenerative, and therefore energy recovery efficiency is lower, and does not give enough considerations to car load traveling comfort while recuperated energy.
Existing truck vibration energy recovery system is generally arranged between vehicle frame and vehicle bridge, mainly contain two kinds of specific implementation forms: one is direct vertical placement energy regenerative compressor cylinder, if can the cylinder of stored energy or oil cylinder etc. when compressing, this mode because of in the actual use procedure of load-carrying vehicle suspension dynamic deflection less, energy recovery efficiency is very low, practicality is very poor, and accessory is more complicated simultaneously, and cost is higher; Another kind of way of realization is that energy regenerative compressor cylinder is placed along vehicle frame longitudinal direction, the conversion of mode of motion is realized by the pinion and rack be arranged between vehicle frame and vehicle bridge, because in actual application, vehicle bridge has the motion of six degree of freedom, often there is the fault fractureed in rack-and-gear, cause energy-recuperation system to lose efficacy, this way of realization reliability is poor.
And existing truck vibration energy recovery system, vibration for the little amplitude of high frequency is difficult to reclaim, and the vibration of large amplitude is less, cause energy recovery efficiency low, still can not reach the requirement that vibrational energy high efficiency reclaims, can not improve car load traveling comfort preferably and be also degrading traveling comfort under some operating mode, thus existing truck vibration energy recovery system is difficult to promote.In addition, also not yet there is the ripe energy regenerative suspension system taking into account car load traveling comfort and vibration energy regeneration efficiency in load-carrying vehicle field at present.
Therefore, how install on load-carrying vehicle can improve that car load traveling comfort, structure are simple, dependable performance and the high vibration energy regeneration system of organic efficiency becomes problem demanding prompt solution.
Summary of the invention
For above-mentioned technical matters, the object of this invention is to provide that a kind of structure is simple, cost is low, dependable performance, can more effective recovery vehicle vibrational energy, improve fuel economy, and improve the load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system of the traveling comfort of goods carrying vehicle.
The technical solution used in the present invention is as follows:
A kind of load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that, comprising: the steel spring connected successively, hanger, oil cylinder connecting rod, the first oil cylinder, the second oil cylinder, cylinder, oil water separator, air pressurizing unit and storage tank;
Described steel spring one end is connected on vehicle frame, and the other end is connected on described hanger;
Described hanger one end is connected on vehicle frame by revolute, and the other end is connected with described oil cylinder connecting rod by revolute;
The rodless cavity of described first oil cylinder is connected with described oil cylinder connecting rod, and the rod chamber of described first oil cylinder is connected on described vehicle frame via piston rod by revolute;
Be connected with the second oil pipe by the first oil pipe between described first oil cylinder and described second oil cylinder;
Described cylinder is connected with described oil water separator with described second oil cylinder;
Wherein, in the driving process of load-carrying vehicle, by the rotary motion of described hanger, drive fluid from described first oil cylinder to described second oil cylinder flowing, and then drive described second oil cylinder to compress the gas of described cylinder, to inflate described storage tank.
Preferably, when described load-carrying vehicle is in the first state, described hanger clickwise, make, between the piston rod of described first oil cylinder and described first oil cylinder, compression movement occurs, and then driving described second oil cylinder to compress the gas of described cylinder, compressed gas is inflated along the first gas circuit described storage tank; When load-carrying vehicle is in the second state, described hanger left-hand revolution, make, between the piston rod of described first oil cylinder and described first oil cylinder, restoring movement occurs, and then driving described second oil cylinder to compress the gas of described cylinder, compressed gas is inflated along the second gas circuit described storage tank.
Preferably, the energy storage being provided with the first check valve, the second check valve, the 3rd check valve, the 4th check valve between described first oil cylinder with described second oil cylinder and being connected with the second check valve with described first check valve, wherein, described first check valve, the second check valve, the 3rd check valve, the 4th check valve are all in closed condition when described first state and described second state.
Preferably, when described first state, if described second oil cylinder is in the first end position, the fluid that the rod chamber of described first oil cylinder needs is compensated by the 4th check valve, and the unnecessary fluid caused because of the piston rod of described first oil cylinder, flow through described first check valve, stored by described energy storage; And when described second state, if described second oil cylinder is in the second end position, the part of the fluid required for rodless cavity of described first oil cylinder is compensated by the 3rd check valve, the demand fluid that another part causes because of the piston rod of described first oil cylinder is flowed out by described energy storage, compensates through described second check valve.
Preferably, the airfilter be connected with described cylinder is also comprised; Wherein, between the rod chamber of described cylinder and described airfilter, be provided with the 5th check valve, between the rodless cavity of described cylinder and described airfilter, be provided with the 6th check valve; Be provided with the 7th check valve between the rodless cavity of described cylinder and described oil water separator, between the rod chamber of described cylinder and described oil water separator, be provided with the 8th check valve.
Preferably, also comprise be arranged on pressure sensor on described storage tank and with described gas storage tank connected driving engine air pressure part flow system, and the electronic control unit communicated to connect with described pressure sensor and described driving engine air pressure part flow system respectively, and pressure energy consumption systems gentle to the tank connected by pass valve of described gas storage.
Preferably, when described pressure sensor records the force value p < p of described storage tank
atime, described driving engine air pressure part flow system is in opening; When described pressure sensor records the force value p>=p of described storage tank
atime, described driving engine air pressure part flow system is in closed condition; Wherein, Pa is the bottom threshold value of the force value of the storage tank of setting.
Preferably, when described driving engine air pressure part flow system is in closed condition, described load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system is in the first state and second state of energy regenerating, wherein, in said first condition, if the force value p > p of described storage tank
b, then by described by pass valve, Partial shrinkage air is discharged into the atmosphere, and now the 8th closed check valve, described 5th one-way valve opens; And in said second condition, if the force value p > p of described storage tank
b, then by described by pass valve, Partial shrinkage air is discharged into the atmosphere, and now the 7th closed check valve, described 6th one-way valve opens, wherein, p
bfor the upper threshold value of the force value of the storage tank of setting.
Preferably, described first gas circuit comprises the gas passage that the rodless cavity of the cylinder connected successively, the 7th check valve, oil water separator and storage tank are formed; Described second gas circuit comprises the gas passage that the rod chamber of the cylinder connected successively, the 8th check valve, oil water separator and storage tank are formed.
Preferably, also comprise:
(1) the operating air pressure p required for air pressure energy consumption systems
eand the rate of supercharging η of blwr, calculate the maximum working pressure (MWP) p of system
max=p
e/ η;
(2) according to the intensity of hanger material, the trouble free service power F that hanger can be born can be obtained;
(3) the trouble free service power F that can bear according to hanger and the maximum working pressure (MWP) p of system
max, utilize formula
can be calculated the cylinder barrel inside radius R of the first oil cylinder
u; According to the intensity of trouble free service power F and cylinder piston rod, the radius of the piston rod of the first oil cylinder is selected to be R
g;
(4) installing space on vehicle frame according to the second oil cylinder and cylinder, selects the forced stroke ratio beta of the second oil cylinder and the first oil cylinder
2;
(5) according to the cylinder barrel inside radius R of the first oil cylinder
uand the second forced stroke ratio beta of oil cylinder and the first oil cylinder
2, can be calculated the cylinder barrel inside radius r of the second oil cylinder
u=R
u/ β;
(6) record the pivot angle range Theta of hanger under unloaded and full load conditions according to test, the length x of hanger, utilizes L=2x θ can obtain the piston stroke L of the first oil cylinder;
(7) fluid of discharging according to the first oil cylinder flows into the second oil cylinder completely, and the requirement that the fluid that the second oil cylinder is discharged flows into the first oil cylinder completely determines that the radius of the piston rod of the second oil cylinder is r
g=R
g/ β
(8) according to arrangement space, the piston rod radius selecting cylinder is r
g, forced stroke is l;
(9) obtain the optimum damping ratio ξ of suspension system traveling comfort according to vehicle parameter by emulation or theory calculate, steel spring bears load m, steel spring stiffness K; Utilize formula
can be calculated the optimum damping value C of suspension system;
(10) according to the optimum damping value C of suspension system, select the diameter of tracheae and oil pipe, and carry out piping layout.
A kind of load-carrying vehicle provided by the invention half initiatively two-way energy regenerative hydro-pneumatic suspension system, its beneficial effect is, utilize hanger lever when oil cylinder cylinder diameter than amplify forced stroke, leverage is relevant with ear length and structure, and cylinder diameter is than the inner cylinder tube radius ratio β being exactly two oil cylinders; The path of motion utilizing hanger unique and connecting rod mechanism realize mode of motion conversion, improve reliability of service, avoid vertical low, the baroque problem of energy recovery efficiency of placing energy regenerative cylinder formula, turn avoid the problem of longitudinal placement energy regenerative cylinder formula poor reliability.In addition, be provided with check valve and energy storage between two oil cylinders, under impact operating mode, the improvement ability of traveling comfort is larger, and low amplitude vibrations energy regenerating ability is higher.
Second oil cylinder is connected with cylinder by the present invention, constitute not only have elastic component but also have damping element can the vibration insulating system of recuperated energy, this system can be stored using pressurized air again vibrational energy being converted into air pressure while elastic element.The dumping force of this system is provided by fluid throttling, and elastic force is provided by pressurized air, and groundwork is identical with hydro pneumatic suspension, and oil cylinder is when both direction is moved, can feedback energy, thus utilize cylinder to reclaim, realize two-way energy regenerative, therefore, this system parenchyma is a two-way energy regenerative hydro-pneumatic suspension system, and air and hydraulic oil provide dumping force jointly, dumping force setting range is larger, and gas, fluid cylinder linkage work, two-way recovery ability, energy regenerating ability can be high.The present invention is aided with again electronic control unit ECU and controls to improve vehicle ride comfort, improves car load traveling comfort and energy recovery efficiency.
Accompanying drawing explanation
Fig. 1 is the integral structure schematic diagram of an embodiment of the invention.
(description of reference numerals)
1. electronic control unit ECU; 2. air pressurizing unit; 3. storage tank; 4. pressure sensor;
5. driving engine air pressure part flow system; 6. vehicle frame; 7. the first cylinder piston rod;
8. the first oil cylinder; 9. oil cylinder connecting rod; 10. hanger;
11. steel springs; 12. energy storages; 13. vehicle bridge;
14. equivalent tires; 15. first check valves; 16. second check valves;
17. the 3rd check valves; 18. the 4th check valves; 19. second oil cylinders;
20. second cylinder piston rods; 21. coupler; 22. the 5th check valves;
23. cylinder piston rods; 24. airfilters; 25. the 6th check valves;
26. cylinders; 27. the 7th check valves; 28. the 8th check valves;
29. by pass valves; 30. air pressure energy consumption systems; 31. oil water separators
Detailed description of the invention
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described in detail.
As shown in Figure 1, the load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system of present embodiment, comprises the steel spring 11, hanger 10, oil cylinder connecting rod 9, first oil cylinder 8, second oil cylinder 19, cylinder 26, oil water separator 31, blwr 2, the storage tank 3 that connect successively.
In the present invention, the structure of the conventional hanger that hanger and current vehicle use is different, which employs lever ratio, increase the length of conventional hanger, and lower end is connected with oil cylinder connecting rod 9 by revolute.In actual design process, can decide according to the intensity of the ear length of different vehicle, hanger material and installing space, generally hanger is enlarged into original 1.5 ~ 2 times.
Wherein, steel spring 11 one end is connected on vehicle frame 6, and the other end is connected on hanger 10; Hanger 10 one end is connected on vehicle frame 6 by revolute, and the other end is connected by revolute with oil cylinder connecting rod 9; Oil cylinder connecting rod 9 is connected by fixed joint with the first oil cylinder 8; The piston rod 7 of the first oil cylinder 8 is connected on vehicle frame 6 by revolute; Be connected with the second oil pipe by the first oil pipe between first oil cylinder 8 and the second oil cylinder 19.The oil pipe that first oil pipe first oil pipe and the second oil pipe are respectively the oil pipe between the rod chamber of connection first oil cylinder 8 and the rod chamber of the second oil cylinder 9 and connect between the rodless cavity of the first oil cylinder 8 and the rodless cavity of the second oil cylinder 9.
Wherein, the energy storage 12 being provided with the first check valve 15, second check valve 16, the 3rd check valve 17, the 4th check valve 18 between first oil cylinder 8 with the second oil cylinder 19 and being connected with the second check valve 16 with the first check valve 15, as shown in Figure 1, the first check valve 15, second check valve 16 is all connected with the first oil pipe; Three, the 4th check valve 17,18 is arranged between the first oil pipe and the second oil pipe; The piston rod 20 of the second oil cylinder 19 is connected by coupler 21 with the piston rod 23 of cylinder 26; The 7th check valve 27 is provided with between the rodless cavity of cylinder 26 and oil water separator 31; The 8th check valve 28 is provided with between the rod chamber of cylinder 26 and oil water separator 31; The 5th check valve 22 is provided with between the rod chamber of cylinder 26 and airfilter 24; The 6th check valve 25 is provided with between the rodless cavity of cylinder 26 and airfilter 24.
In addition, as shown in Figure 1, system also comprises the pressure sensor 4 be arranged on storage tank 3 and the driving engine air pressure part flow system 5 be connected with storage tank 3, and the electronic control unit ECU1 communicated to connect with pressure sensor 4 and driving engine air pressure part flow system 5 respectively, and the gentle pressure energy consumption systems 30 of by pass valve 29 be connected with storage tank 4 respectively.
When pressure sensor 4 records the force value p < p of storage tank 3
a(wherein p
abottom threshold value for setting) time, driving engine air pressure part flow system 5 is in opening.When pressure sensor 4 records the force value p>=p of storage tank 3
atime, driving engine air pressure part flow system 5 is in closed condition.
Below the two-way energy regenerative hydro-pneumatic suspension system of load-carrying vehicle of the present invention half active is introduced in the situation of different operating state.
In vehicle traveling process, vehicle frame 6 is vibrated because of Uneven road, but tire is not subject to severe impact, compression and restoring movement can be there is in steel spring 11, cause hanger 10 to rotate around its point on fixed support, drive fluid to flow to the second oil cylinder 19 from the first oil cylinder 8, and then drive the gas of the second oil cylinder 19 compression cylinder 26, to inflate storage tank 3, thus carry out the recovery of the energy vibrational energy of load-carrying vehicle.
When pressure sensor 4 records the force value p>=p of storage tank 3
atime, driving engine air pressure part flow system 5 is in closed condition.Now, system is in energy regenerating mode of operation.Energy regenerating mode of operation can be divided into the first state and the second state.The first state in the present invention and the second state determine based on the relative motion between vehicle frame 6 and vehicle bridge 13, when vehicle frame 6 and vehicle bridge 13 close to each other time, be referred to as the first state, when vehicle frame 6 and vehicle bridge 13 mutually away from time, be referred to as the second state.
When load-carrying vehicle is in the first state, can compression movement be there is in steel spring 11, hanger 10 makes clockwise rotation around its point on fixed support, make, between the first oil cylinder 8 and the piston rod 7 of the first oil cylinder, compression movement occurs, and then the gas in drive the second oil cylinder 19 compression cylinder 26, compressed gas is inflated along the first gas circuit storage tank 3; When load-carrying vehicle is in the second state, hanger 10 makes counter-clockwise rotary motion around its point on fixed support, make, between the piston rod 7 of the first oil cylinder 8 and described first oil cylinder, restoring movement occurs, and then driving the gas of the second oil cylinder 19 compression cylinder 26, compressed gas is inflated along the second gas circuit storage tank 3.
Below the first state of the present invention and the second state are described in detail.
(1) first state
When in the first state, namely when vehicle frame 6 is close to each other with vehicle bridge 13 (it is connected with equivalent tire 14), there is compression movement in steel spring 11, hanger 10 makes clockwise rotation around its point on fixed support, be the compression movement between the first oil cylinder 8 and its piston rod 7 by hanger 10 and oil cylinder connecting rod 9 convert rotational motion, the fluid that first cylinder piston rod 7 promotes the first oil cylinder 8 rodless cavity enters the second oil cylinder 19 rodless cavity, thus the piston rod 20 promoting the second oil cylinder 19 moves to left, and makes its rod chamber fluid enter the rod chamber of the first oil cylinder 8.Meanwhile, drive the second oil cylinder 19 to compress the gas of described cylinder, compressed gas is inflated along the first gas circuit described storage tank, particularly, second oil cylinder 19 is moved to left by the piston rod 23 of piston rod 20 with dynamic air cylinder 26, rodless cavity gas is compressed, and pressure raises, and closes the 6th check valve 25, open the 7th check valve 27, pressure gas enters blwr 2 through the 7th check valve 27 and oil water separator 31, enters storage tank 3 after supercharging, completes energy regenerating action.
In a state in which, if record the force value p > p of storage tank 3
b(p
bupper threshold value for setting) time, by by pass valve 29, Partial shrinkage air is discharged into the atmosphere.Meanwhile, because piston moves to left, air pressure reduces cylinder 26 rod chamber gas, and the 8th check valve 28 is closed, and air pushes the 5th check valve 22 open through airfilter 24, enters the rod chamber of cylinder 26, completes aspiratory action.In whole process, the first check valve 15, second check valve 16, the 3rd check valve 16, the 4th check valve 17 are all in closed condition.
(2) second states
When in the second state, namely vehicle frame 6 and vehicle bridge 13 (it is connected with equivalent tire 14) mutually away from time, there is restoring movement in steel spring 11, hanger 10 makes counter-clockwise rotary motion around its point on fixed support, be the restoring movement between the first oil cylinder 8 and its piston rod 7 by hanger 10 and oil cylinder connecting rod 9 convert rotational motion, the fluid that first cylinder piston rod 7 promotes the first oil cylinder 8 rod chamber enters the rod chamber of the second oil cylinder 19, thus the piston rod 20 promoting the second oil cylinder 19 moves to right, and makes its rodless cavity fluid enter the rodless cavity of the first oil cylinder 8.Meanwhile, drive the second oil cylinder 19 to compress the gas of described cylinder, compressed gas is inflated along the second gas circuit described storage tank, particularly, second oil cylinder 19 is moved to right by the piston rod 23 of piston rod 20 with dynamic air cylinder 26, rod chamber gas is compressed, and pressure raises, and closes the 5th check valve 22, open the 8th check valve 28, pressure gas enters blwr 2 through the 8th check valve 28 and oil water separator 31, enters storage tank 3 after supercharging, completes energy regenerating action.
In a state in which, if the force value p > p of the storage tank recorded 3
b(p
bupper threshold value for setting) time, by by pass valve 29, Partial shrinkage air is discharged into the atmosphere.Meanwhile, because piston moves to right, air pressure reduces the gas of cylinder 26 rodless cavity, and the 7th check valve 27 is closed, and air pushes the 6th check valve 25 open through airfilter 24, enters the rodless cavity of cylinder 26, completes aspiratory action.In whole process, the first check valve 15, second check valve 16, the 3rd check valve 16, the 4th check valve 17 are all in closed condition.
When pressure sensor 4 records the force value p < p of storage tank 3
a(wherein p
abottom threshold value for setting) time, by ECU12 start the engine air pressure part flow system 5, be that storage tank 3 is inflated by the Air compressor on driving engine.In other situation, driving engine air pressure part flow system 5 is in closed condition, so avoids engine air compressor and is in the fuel oil consumption caused for gaseity.The pressure threshold lower limit of the storage tank of current conventional vehicles, roughly between 8bar ~ 10bar, when determining Pa, can design according to the purposes of the energy of vehicle and collection, being approximately located at about 85% of conventional vehicles value.
In vehicle traveling process, tire is subject to severe impact, if when the second oil cylinder 19 reaches the first end position because the first oil cylinder 8 compression stroke displacement is excessive, now the piston of the second oil cylinder 19 is positioned at the high order end of its rod chamber: the fluid required for the first oil cylinder 8 rod chamber, compensate through the 4th check valve 18, because of the unnecessary fluid that piston rod 7 causes, namely due to fluid part that the movement of piston rod 7 is discharged, flow through the first check valve 15, stored by energy storage 12, and when the first oil cylinder 8 restores stroke, the fluid that energy storage 12 stores flows to the rodless cavity of the first oil cylinder 8 through the second check valve 16, if the second oil cylinder 19 because of the first oil cylinder 8 restore travel displacement excessive and reach the second end position time, now the piston of the second oil cylinder 19 is positioned at the low order end of rodless cavity: the fluid required for the first oil cylinder 8 rodless cavity, a part compensates through the 3rd check valve 17, the demand fluid that another part causes because of piston rod 7, namely due to the movement of piston rod 7, make the volume fractiion shared by original piston rod 7 be available and need fluid to fill caused demand fluid to be flowed out by energy storage 12, compensate through the second check valve 16.
In the present invention, the parameters of system is selected by following:
(1) the operating air pressure p required for air pressure energy consumption systems 30
eand the rate of supercharging η of blwr 2, calculate the maximum working pressure (MWP) p of system
max=p
e/ η;
(2) according to the leading dimensions of hanger 10 material, structure and strength of material, the trouble free service power F utilizing mechanical knowledge can obtain hanger can to bear;
(3) the trouble free service power F that can bear according to the hanger 10 and maximum working pressure (MWP) p of system
max, utilize formula
can be calculated the cylinder barrel inside radius R of the first oil cylinder 8
u; According to the intensity of trouble free service power F and cylinder piston rod, the radius of the piston rod 7 of the first oil cylinder 8 is selected to be R
g;
(4) installing space on vehicle frame according to the second oil cylinder 19 and cylinder 26, selects the forced stroke ratio beta of the second oil cylinder 19 and the first oil cylinder 8
2; In practice, forced stroke ratio beta can be determined in the actual installation space on vehicle frame according to the second oil cylinder 19 and cylinder 26
2.
(5) according to the cylinder barrel inside radius R of the first oil cylinder 8
uand the second forced stroke ratio beta of oil cylinder 19 and the first oil cylinder 8
2, can be calculated the cylinder barrel inside radius r of the second oil cylinder 19
u=R
u/ β;
(6) record the pivot angle range Theta of hanger under unloaded and full load conditions according to test, the length x of hanger 2, utilizes L=2x θ can obtain the piston stroke L of the first oil cylinder 8;
(7) fluid of discharging according to the first oil cylinder 8 flows into the second oil cylinder 19 completely, and the fluid that the second oil cylinder 19 is discharged flows into the requirement of the first oil cylinder 8 completely, determines that the radius of the piston rod 20 of the second oil cylinder 19 is r
g=R
g/ β;
(8) according to arrangement space, piston rod 23 radius selecting cylinder 26 is r
g, forced stroke is l;
(9) obtained the optimum damping ratio ξ of suspension system traveling comfort by emulation or theory calculate according to vehicle parameter, steel spring bears load m; Steel spring stiffness K; Utilize formula
can be calculated the optimum damping value C of suspension system;
Such as can set up whole vehicle model optimal damping parameter by ADAMS/Car many bodies software, obtain traveling comfort optimum damping ratio ξ; Also theory of oscillation can be utilized to set up car load oscillatory differential equation group optimal damping parameter, obtain traveling comfort optimum damping ratio ξ.
(10) according to the optimum damping value C of suspension system, select the diameter of tracheae and oil pipe, and carry out piping layout.
Piping layout refers to that system is arranged between each element, and between each element as shown in Figure 1, the length of oil pipe and tracheae and the circuit walked, by selecting their length, bending route, can make the equivalent damping produced equal C; First substantially determine pipeline diameter according to C, then arrange.The length that concrete layout refers to oil pipe and tracheae and the circuit walked, this makes industry general knowledge, and oil pipe and tracheae are exactly the connection pipe shown in figure, by selecting their length, bending route, the equivalent damping produced can be made to equal C; First substantially determine pipeline diameter according to C, then arrange; The C that the pipeline of different-diameter produces is different.
Embodiment
Next, certain Medium Truck produced using certain car company as sample car, thus is described further truck vibration energy recovery system of the present invention.
The truck vibration energy recovery system integral structure structure of sample car as above.Wherein, the length of the storage tank 30 in sample car is 500mm, and diameter is 250mm.
For solving existing truck vibration energy recovery system, high frequency small amplitude motion is difficult to the problem reclaiming vibrational energy, and the present invention adopts the oil cylinder of different cylinder diameter and forced stroke to connect, thus realizes amplifying the stroke of high frequency small amplitude motion; For improving car load traveling comfort, avoiding severe road conditions to cause system failure to tire severe impact, devise the protection bypass under limiting condition, comprise the first check valve 15, second check valve 16, the 3rd check valve 16, the 4th check valve 17 and energy storage 12.The original hanger of steel spring (length 110mm) is redesigned simultaneously, according to intensity and the installing space of hanger material, original ear length is amplified twice, length becomes 220mm, i.e. hanger 10, namely lever ratio is adopted, the length of conventional hanger is increased, and lower end is connected with oil cylinder connecting rod 9 by revolute, though make the vehicle situation bad due to road conditions in the process of moving cause the distance between vehicle frame and vehicle bridge to be changed within the scope of-3mm ~ 3mm small amplitude motion stroke amplify further.
For solving the problem of longitudinal placement energy regenerative cylinder formula poor reliability, the present invention utilizes unique path of motion of hanger 2 to realize mode of motion conversion, namely hanger 10 can only rotate around its point on fixed support, be the compression movement of the first oil cylinder 8 and its piston rod 7 convert rotational motion by oil cylinder connecting rod 9, improve reliability.In order to avoid the first oil cylinder 8 is subject to excessive side force, the piston rod 7 of the first oil cylinder 8 is connected with vehicle frame 6 by revolute.
For providing energy recovery efficiency, and make vehicle reach traveling comfort optimum regime, system component parameter chooses employing following steps:
(1) the operating air pressure p required for air pressure energy consumption systems 30
erate of supercharging η=2 of=8e+005Pa and blwr 2, calculate the maximum working pressure (MWP) p of system
max=p
e/ η=4e+005Pa;
(2) according to the intensity of hanger 10 material, the trouble free service power F=3000N that hanger can be born can be obtained.
(3) the trouble free service power F that can bear according to hanger and the maximum working pressure (MWP) p of system
max=4e+005Pa, utilizes formula
can be calculated the cylinder barrel inside radius R of the first oil cylinder 8
u=50mm; According to the intensity of trouble free service power F=3000N and cylinder piston rod, the radius of the piston rod 7 of the first oil cylinder 8 is selected to be R
g=10;
(4) installing space on vehicle frame according to the second oil cylinder 19 and cylinder 26, selects the forced stroke ratio beta of the second oil cylinder 19 and the first oil cylinder 8
2=4;
(5) according to the cylinder barrel inside radius R of the first oil cylinder 8
uthe forced stroke ratio beta of=50mm and the second oil cylinder 19 and the first oil cylinder 8
2=4, half r in the cylinder barrel that can be calculated the second oil cylinder 19
u=R
u/ β=25mm;
(6) recording the pivot angle scope of hanger under unloaded and full load conditions according to test is-10 ° ~ 10 °, and ear length x=120mm, utilizes L=2x θ can obtain the first oil cylinder piston stroke L=80mm.
(7) fluid of discharging according to the first oil cylinder 8 flows into the second oil cylinder 19 completely, and the fluid that the second oil cylinder 19 is discharged flows into the requirement of the first oil cylinder 8 completely, determines that the radius of the piston rod 20 of the second oil cylinder 19 is r
g=R
g/ β=5mm;
(8) according to the strength of material of cylinder 26 piston rod 23, piston rod 23 radius selecting cylinder 26 is r
g=5mm is l=200mm according to arrangement space forced stroke;
(9) obtained optimum damping ratio ξ=0.2 of suspension system traveling comfort by emulation or theory calculate according to vehicle parameter, steel spring bears load m=5000kg; Steel spring stiffness K=970000N/m; Utilize formula
can be calculated the optimum damping value C=2.7857e+004Ns/m of suspension system;
Such as can set up whole vehicle model optimal damping parameter by ADAMS/Car many bodies software, obtain traveling comfort optimum damping ratio ξ; Also theory of oscillation can be utilized to set up car load oscillatory differential equation group optimal damping parameter, obtain traveling comfort optimum damping ratio ξ.
(10) according to the optimum damping value C=2.7857e+004Ns/m of suspension system, select the diameter of tracheae and oil pipe, and carry out piping layout, make system damping value be 2.7857e+004Ns/m.
For verifying traveling comfort and the energy recovery efficiency of sample car, the method adopting Simulation and test to combine, energy recovery rate being estimated, and contrast verification is carried out to travelling comfort:
Software ADAMS/Car and software EASY5 is utilized to set up associative simulation model.Test method(s) is utilized to record each part quality and rotor inertia in model, rubber bush six to rigidity, resistance of shock absorber, steel spring rigidity, tire stiffness.The speed of a motor vehicle is 60km/h, and it is 15 tons that spring carries, and road surface input adopts GB7031-86 standard road spectrum grade A, B, C, D.
Table 1 energy regenerating evaluation table
Emulation shows, it is 15 tons that the spring of sample car carries, and the speed of a motor vehicle is 60km/h when travelling respectively on A, B, C, D level road surface, and energy recovery rate is followed successively by 2.30%, 5.60%, 10.22%, 18.27%.
Table 2 travelling comfort evaluation table
Emulation shows, it is 15 tons that sample car spring carries, and the speed of a motor vehicle is 60km/h when travelling respectively on A, B, C, D level road surface, and traveling comfort improves percentum and is followed successively by 8.06%, 18.82%, 20.0%, 21.69%.
To sum up, load-carrying vehicle of the present invention half initiatively two-way energy regenerative hydro-pneumatic suspension system has not only reclaimed the vibrational energy of load-carrying vehicle, turn avoid and only has engine air compressor to be in the fuel oil consumption caused for gaseity, save the fuel oil consumption of driving engine.The present invention connects the second oil cylinder with cylinder, constitute not only have elastic component but also have damping element can the vibration insulating system of recuperated energy, the dumping force of this system is provided by fluid throttling, and elastic force is provided by pressurized air, groundwork is identical with hydro pneumatic suspension, and two-way energy regenerative.The present invention is aided with again electronic control unit ECU and controls to improve car load traveling comfort.
Claims (10)
1. a load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that, comprising: the steel spring connected successively, hanger, oil cylinder connecting rod, the first oil cylinder, the second oil cylinder, cylinder, oil water separator, air pressurizing unit and storage tank;
Described steel spring one end is connected on vehicle frame, and the other end is connected on described hanger;
Described hanger one end is connected on vehicle frame by revolute, and the other end is connected with described oil cylinder connecting rod by revolute;
The rodless cavity of described first oil cylinder is connected with described oil cylinder connecting rod, and the rod chamber of described first oil cylinder is connected on described vehicle frame via piston rod by revolute;
Be connected with the second oil pipe by the first oil pipe between described first oil cylinder and described second oil cylinder;
Described cylinder is connected with described oil water separator with described second oil cylinder;
Wherein, in the driving process of load-carrying vehicle, by the rotary motion of described hanger, drive fluid from described first oil cylinder to described second oil cylinder flowing, and then drive described second oil cylinder to compress the gas of described cylinder, to inflate described storage tank.
2. load-carrying vehicle according to claim 1 half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that,
When described load-carrying vehicle is in the first state, described hanger clickwise, make, between the piston rod of described first oil cylinder and described first oil cylinder, compression movement occurs, and then driving described second oil cylinder to compress the gas of described cylinder, compressed gas is inflated along the first gas circuit described storage tank;
When load-carrying vehicle is in the second state, described hanger left-hand revolution, make, between the piston rod of described first oil cylinder and described first oil cylinder, restoring movement occurs, and then driving described second oil cylinder to compress the gas of described cylinder, compressed gas is inflated along the second gas circuit described storage tank.
3. load-carrying vehicle according to claim 2 half initiatively two-way energy regenerative hydro-pneumatic suspension system, it is characterized in that, the energy storage being provided with the first check valve, the second check valve, the 3rd check valve, the 4th check valve between described first oil cylinder with described second oil cylinder and being connected with the second check valve with described first check valve
Wherein, described first check valve, the second check valve, the 3rd check valve, the 4th check valve are all in closed condition when described first state and described second state.
4. load-carrying vehicle according to claim 2 half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that,
When described first state, if described second oil cylinder is in the first end position, the fluid that the rod chamber of described first oil cylinder needs is compensated by the 4th check valve, and the unnecessary fluid caused because of the piston rod of described first oil cylinder, flow through described first check valve, stored by described energy storage; And
When described second state, if described second oil cylinder is in the second end position, the part of the fluid required for rodless cavity of described first oil cylinder is compensated by the 3rd check valve, the demand fluid that another part causes because of the piston rod of described first oil cylinder is flowed out by described energy storage, compensates through described second check valve.
5. load-carrying vehicle according to claim 4 half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that, also comprise the airfilter be connected with described cylinder;
Wherein, between the rod chamber of described cylinder and described airfilter, be provided with the 5th check valve, between the rodless cavity of described cylinder and described airfilter, be provided with the 6th check valve; Be provided with the 7th check valve between the rodless cavity of described cylinder and described oil water separator, between the rod chamber of described cylinder and described oil water separator, be provided with the 8th check valve.
6. load-carrying vehicle according to claim 5 half initiatively two-way energy regenerative hydro-pneumatic suspension system, it is characterized in that, also comprise be arranged on pressure sensor on described storage tank and with described gas storage tank connected driving engine air pressure part flow system, and the electronic control unit communicated to connect with described pressure sensor and described driving engine air pressure part flow system respectively, and pressure energy consumption systems gentle to the tank connected by pass valve of described gas storage.
7. load-carrying vehicle according to claim 6 half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that,
When described pressure sensor records the force value p < p of described storage tank
atime, described driving engine air pressure part flow system is in opening;
When described pressure sensor records the force value p>=p of described storage tank
atime, described driving engine air pressure part flow system is in closed condition;
Wherein, Pa is the bottom threshold value of the force value of the storage tank of setting.
8. load-carrying vehicle according to claim 7 half initiatively two-way energy regenerative hydro-pneumatic suspension system, it is characterized in that, when described driving engine air pressure part flow system is in closed condition, described load-carrying vehicle half initiatively two-way energy regenerative hydro-pneumatic suspension system is in the first state and second state of energy regenerating
Wherein, in said first condition, if the force value p > p of described storage tank
b, then by described by pass valve, Partial shrinkage air is discharged into the atmosphere, and now the 8th closed check valve, described 5th one-way valve opens; And
In said second condition, if the force value p > p of described storage tank
b, then by described by pass valve, Partial shrinkage air is discharged into the atmosphere, and now the 7th closed check valve, described 6th one-way valve opens,
Wherein, p
bfor the upper threshold value of the force value of the storage tank of setting.
9. load-carrying vehicle according to claim 5 half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that, described first gas circuit comprises the gas passage that the rodless cavity of the cylinder connected successively, the 7th check valve, oil water separator and storage tank are formed; Described second gas circuit comprises the gas passage that the rod chamber of the cylinder connected successively, the 8th check valve, oil water separator and storage tank are formed.
10. the load-carrying vehicle according to any one of claim 6 to 9 half initiatively two-way energy regenerative hydro-pneumatic suspension system, is characterized in that, also comprise:
(1) the operating air pressure p required for air pressure energy consumption systems
eand the rate of supercharging η of blwr, calculate the maximum working pressure (MWP) p of system
max=p
e/ η;
(2) according to the intensity of hanger material, the trouble free service power F that hanger can be born can be obtained;
(3) the trouble free service power F that can bear according to hanger and the maximum working pressure (MWP) p of system
max, utilize formula
can be calculated the cylinder barrel inside radius R of the first oil cylinder
u; According to the intensity of trouble free service power F and cylinder piston rod, the radius of the piston rod of the first oil cylinder is selected to be R
g;
(4) installing space on vehicle frame according to the second oil cylinder and cylinder, selects the forced stroke ratio beta of the second oil cylinder and the first oil cylinder
2;
(5) according to the cylinder barrel inside radius R of the first oil cylinder
uand the second forced stroke ratio beta of oil cylinder and the first oil cylinder
2, can be calculated the cylinder barrel inside radius r of the second oil cylinder
u=R
u/ β;
(6) record the pivot angle range Theta of hanger under unloaded and full load conditions according to test, the length x of hanger, utilizes L=2x θ can obtain the piston stroke L of the first oil cylinder;
(7) fluid of discharging according to the first oil cylinder flows into the second oil cylinder completely, and the requirement that the fluid that the second oil cylinder is discharged flows into the first oil cylinder completely determines that the radius of the piston rod of the second oil cylinder is r
g=R
g/ β
(8) according to arrangement space, the piston rod radius selecting cylinder is r
g, forced stroke is l;
(9) obtain the optimum damping ratio ξ of suspension system traveling comfort according to vehicle parameter by emulation or theory calculate, steel spring bears load m, steel spring stiffness K; Utilize formula
can be calculated the optimum damping value C of suspension system;
(10) according to the optimum damping value C of suspension system, select the diameter of tracheae and oil pipe, and carry out piping layout.
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