CN101070889A - Combined piston of gas-oil spring - Google Patents
Combined piston of gas-oil spring Download PDFInfo
- Publication number
- CN101070889A CN101070889A CN 200710118958 CN200710118958A CN101070889A CN 101070889 A CN101070889 A CN 101070889A CN 200710118958 CN200710118958 CN 200710118958 CN 200710118958 A CN200710118958 A CN 200710118958A CN 101070889 A CN101070889 A CN 101070889A
- Authority
- CN
- China
- Prior art keywords
- throttle valve
- piston
- valve plate
- plate group
- hydro
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Landscapes
- Fluid-Damping Devices (AREA)
Abstract
The present invention is a combination of oil and gas piston spring, including Piston Rings , Cover, bearing cap, ring-group throttle and adjustment ring gasket. Bearing cap with the thread through the rod attached to the throttle-group and the adjustment for gasket sets in the back end of the Detroit Piston Ring Cover and connected through the thread. The invention of on the basis the original oil and gas in the spring can change resistance in order to achieve different requirements of the traffic movement. In the absence of the destruction of the cylinder seal, this enables oil and gas spring by the substantial increase in common. Attenuation of the invention can be used body vibration, enhancing vehicle safety, ride comfort and off-road speed.
Description
Technical field
The present invention relates to a kind of hydro-pneumatic spring built-up piston that is used for.Belong to hydraulic machinery and road vehicle application field.
Background technique
Suspension is the general name of all power transmission connection sets between vehicle frame (or monocoque body) and the vehicle bridge (or wheel).From conversational implication, suspension system is made up of elastic element, damping member and guiding device etc.Certainly, on concrete structure realized, above-mentioned each element may not be all with independently form appearance.
In the prior art, remove hydro-pneumatic spring, the employed elastic element kind of vehicle suspension system mainly also has: leaf spring, helical spring, torsion bar spring, rubber spring and gas spring.The unit mass energy storage of leaf spring, helical spring and torsion bar spring is smaller, and it is very limited to absorb vibrational energy in the vehicle driving process, and quality is bigger; Simultaneously spring rate all is linear performance, can not change on the different brackets road surface according to vehicle driving, thereby can't realize the optimization of vehicle ride comfort.Rubber spring then is to utilize the elasticity of rubber itself to absorb vibrational energy, but the life-span is shorter, is easy to wear out, so application area is less.Gas spring generally be with inert gas (nitrogen) as Elastic medium, stiffness curve presents good nonlinear characteristics; Its energy storage is bigger than very simultaneously, but itself can only absorb the impact that car body is produced with the release portion road excitation, consume most of vibrational energy, satisfy travelling of vehicle and require also need add vibration damping equipment, and gas spring itself does not have leading role yet.
In the last few years, the development of hydro-pneumatic spring had had significant progress, all used to some extent on some engineering vehicles and military vehicle, compared with above several form of springs, and hydro-pneumatic spring generally has following characteristics:
(1) nonlinear variable-stiffness characteristic
Because hydro-pneumatic spring uses high-pressure inert gas (nitrogen) to serve as traditional elastic element, has typical nonlinear rigidity and cumulative property characteristics, so can satisfy vehicle ride comfort and stability requirement to greatest extent.When vehicle when flat road surface is travelled, the relative extending amount of hydro-pneumatic spring is less, the rigidity that inert gas produced is also less, can fully satisfy occupant's travelling comfort requirement; When vehicle when rough ground travels, moving stroke increases, and makes hydro-pneumatic spring rigidity become big, can absorb more impact energy, thereby guarantee occupant's Security.In addition, at the bigger vehicle of load change, the change stiffness characteristics of hydro-pneumatic spring can make the vehicle body natural frequency remain on a metastable scope, so that improve the smoothness of vehicle.
(2) non-linear change damping characteristic
By the orifice valve that different throttle style is formed, be installed on the hydro-pneumatic spring, also have the nonlinear dampling characteristic, the damping force of generation and damping constant all change along with the variation of vehicle frame and vehicle bridge relative velocity.So after installing orifice valve additional, hydro-pneumatic spring has played the effect of vibration damper simultaneously.
(3) car appearance regulatory function
Hydro-pneumatic spring can also be realized the lifting of car body by the additional one appearance regulating system of harnessing an animal to a cart, and front and back pitching and tilting is so that the passing ability of raising vehicle.Regulatory function for the car appearance only could realize in Active Suspension usually, thereby embodies the superiority and the bright development prospect of oleo-pneumatic suspension.
The deficiency of existing hydro-pneumatic spring:
In order to ensure compact structure, usually orifice valve is installed on the piston, in case assembling is finished, find the orifice valve cisco unity malfunction by test, maybe need to adjust the valve group and change damping force when reaching the entrucking requirement, dismantle again, changing valve group component difficulty can be very big, and the dismounting after the hydro-pneumatic spring Sealing often need integral replacing, cause unnecessary waste; This hydro-pneumatic spring can only be applicable to the needs of certain vehicle, is difficult to change the requirement that valve block structure satisfies other vehicles on the original basis, and versatility is bad.
Summary of the invention
The objective of the invention is to overcome the deficiency of above-mentioned prior art, a kind of hydro-pneumatic spring built-up piston is provided, the piston rod of hydro-pneumatic spring is sleeved in the cylinder barrel, and built-up piston comprises piston ring, piston end cap, load lid, annular throttle valve plate group and annular adjustment pad.The load lid links to each other with piston rod by screw thread, and the piston ring that will play supporting and leading role compresses, throttle valve plate group and adjustment pad are sleeved on load and cover end, the piston end cap links to each other with piston ring by screw thread, and with load lid together with the inner ring of throttle valve plate group with adjust pad and compress, lock the load lid simultaneously, prevent that the screw thread between load lid and the piston rod from unscrewing.
Piston ring circumferentially is processed with the knuckle oil-through hole, is communicated with cylinder barrel annular oil cavity and cylinder barrel oil pocket.
The piston end cap circumferentially is processed with the assembling oil-through hole of being convenient to dismounting and playing the oil effect, center position is processed with the last center hole that is communicated with cylinder barrel oil pocket and piston rod oil pocket, be processed with towards throttle valve plate group one side restriction throttle valve plate group maximum deformation quantity on the annular stop piece, being processed into the wall shape, be used to change throttle chink width and damping force with the throttle valve plate group outward edge amount of deformation place of matching.
The load lid is processed with the throttle valve film trap of suit throttle valve plate group, be processed with the following annular stop piece that is used to limit throttle valve plate group maximum deformation quantity towards throttle valve plate group one side, being processed into the wall shape, be used to change throttle chink width and damping force with the throttle valve plate group outward edge amount of deformation place of matching.
The throttle valve film trap that annular is adjusted in pad inside/outside diameter size and the load lid is consistent, to play the effect that compresses the throttle valve plate group and adjust throttle valve plate group maximum deformation quantity and maximum damping force.
The throttle valve plate group is formed by annular throttle valve plate stack combinations, and the valve block of both sides is more smaller than the external diameter of center position valve block, and the wall shape of covering with load when guaranteeing distortion does not interfere.
It is all detachable that the present invention is used to produce the core component of damping force, so just can change Resistance Value easily on the basis of original hydro-pneumatic spring, to reach the requirement of travelling of different vehicle.Owing to do not destroy the Sealing in the cylinder, thereby the versatility of hydro-pneumatic spring is largely increased.Adopt the present invention's body vibrations of can decaying, improve Security, smoothness and the cross-country speed of vehicle.
Description of drawings
Fig. 1 is the assembly structure chart of hydro-pneumatic spring;
Fig. 2 is a damping device structural drawing on the hydro-pneumatic spring;
Fig. 3 is a damping device structural drawing under the hydro-pneumatic spring;
Fig. 4 is a hydro-pneumatic spring upper connection assembly structure chart;
Fig. 5 is a hydro-pneumatic spring lower contact assembly structure chart;
Fig. 6 is a hydro-pneumatic spring lower contact assembly sleeve end face structural drawing;
Fig. 7 is a connecting cover plan view under the hydro-pneumatic spring lower contact assembly;
Fig. 8 is a connecting cover left view under the hydro-pneumatic spring lower contact assembly;
Fig. 9 is a hydro-pneumatic spring built-up piston structural drawing;
Figure 10 is a hydro-pneumatic spring built-up piston partial enlarged drawing;
Figure 11 is a hydro-pneumatic spring piston end cap plan view;
Figure 12 is a hydro-pneumatic spring piston end cap plan view;
Figure 13 is hydro-pneumatic spring load lid plan view;
Figure 14 covers A to view for the hydro-pneumatic spring load;
Figure 15 is the stressed schematic representation of research on throttle valve plate of oil-pneumatic spring;
Among the figure: 1-piston rod, 2-cylinder barrel, 3-lower support locking nut, the 4-lower end cap, 5-lower support assembly, 6-lower contact locking nut, the 7-lower cover, 8-lower contact assembly, 9-lower contact Sealing, 10-lower support Sealing, damping device under the 11-, the 12-floating piston, the 13-built-up piston, 14-upper connection Sealing, 15-upper connection assembly, 16-upper press cover, the last damping device of 17-, 18-upper connection locking nut, 19-sleeve, 20-end cap assembly, the big Sealing of 21-end cap, the little Sealing of 22-end cap, the 23-threaded fastener, connecting cover under the 24-, 25-lower support pilot hole, 26-lower contact pilot hole, 27-upper connection pilot hole, the last buffer stopper of 28-, the 29-upper guard board, the little dome of 30-, the big dome end face of 31-, 32-sleeve fitting recess, the 33-tapped hole, buffer stopper under the 34-, backplate under the 35-, the 36-unthreaded hole, the 37-projection, 38-piston ring, 39-piston end cap, 40-load lid, 41-knuckle oil-through hole, 42-assembles oil-through hole, the last circular groove of 43-, the 44-wall, 45-throttle valve plate group, 46-adjusts pad, the last annular stop piece of 47-, circular groove under the 48-, 49-throttle valve film trap, annular stop piece under the 50-, center hole under the 51-
A-piston rod oil pocket, B-piston rod air cavity, C-cylinder barrel annular oil cavity, D-cylinder barrel oil pocket, E-sleeve air cavity, F-vehicle bridge steering equipment
Embodiment
Below in conjunction with accompanying drawing the hydro-pneumatic spring damping device is done detailed description:
The piston rod 1 of hollow is sleeved in the cylinder barrel 2, and built-up piston 13 is equipped with in the upper end of piston rod 1, and by being threaded onto together, the lower end is equipped with lower contact assembly 8, forms the end sealing, so that link to each other by the link arm of link and vehicle bridge.Piston rod cavity is equipped with floating piston 12, and piston rod cavity is divided into two chambers, and wherein upper chamber is full of fluid, is called piston rod oil pocket A, and lower chambers charges into corresponding high-pressure inert gas according to the vehicle static load, is called piston rod air cavity B.Cylinder barrel 2 upper ends are equipped with upper connection assembly 15, and form the end sealing, so that link to each other by the link arm of link with compartment or vehicle frame; Lower support assembly 5 is equipped with in cylinder barrel 2 lower ends, mainly piston rod 1 is played the effect of guiding and supporting, so just between piston rod 1 and cylinder barrel 2, form cylinder barrel annular oil cavity C, between cylinder barrel 2, upper connection assembly 15 and built-up piston 13, formed cylinder barrel oil pocket D.As can be seen from the figure, cylinder barrel oil pocket D is communicated with piston rod oil pocket A by the center hole of built-up piston 13; In the hydro-pneumatic spring working procedure, because built-up piston 13 center holes are enough big, the local pressure loss that is produced can be ignored, thus cylinder barrel oil pocket D equate with the pressure of piston rod oil pocket A, also equal the gas pressure of piston rod air cavity B simultaneously.
Figure 2 shows that the erection drawing of damping device 17, wherein go up buffer stopper 28 and form that upper guard board 29 can be made by hard material, bonds together by sulfuration or gluing mode and last buffer stopper 28 by the materials processing that rubber etc. has elastic property.
Figure 3 shows that down the erection drawing of damping device 11, wherein descend buffer stopper 34 to be formed by the materials processing that rubber etc. has elastic property, following backplate 35 can be made by hard material, bonds together with following buffer stopper 34 by sulfuration or gluing mode.
Go up the upper and lower end parts that damping device 17 and following damping device 11 are installed at cylinder barrel 2 inner chambers respectively as shown in Figure 1.Assemble at present that damping device 11 directly is sleeved on the piston rod 1, following backplate 35 1 sides should be towards built-up piston 13.After the hydro-pneumatic spring entrucking, following damping device 11 can rely on self gravitation to remain on cylinder barrel 2 lower ends, and contacts with lower support assembly 5, so do not need to adopt special fixation, has reduced assembly process; In addition, because last damping device 17 is in the upper end of hydro-pneumatic spring inner cavity chamber, in the hydro-pneumatic spring working procedure, for preventing that it from relying on self gravitation or being subjected to other external force to influence landing to cylinder barrel oil pocket D, interfere the to-and-fro motion of built-up piston 13, hydro-pneumatic spring itself is produced unnecessary destruction, so it is sleeved on the little dome 30 of upper connection assembly 15, as shown in Figure 4, upper guard board 29 1 sides also should will bond together going up the contact segment of buffer stopper 28 with upper connection assembly 15 simultaneously towards built-up piston 13.
When vehicle is run at high speed under abominable road conditions, if the limiting stopper on the car body lost efficacy, to probably cause the overtravel motion of built-up piston 13, thereby produce fierce collision with upper connection assembly 15 and lower support assembly 5, this will be easy to cause the leakage of hydro-pneumatic spring until breaking-up.After in hydro-pneumatic spring, installing upper and lower damping device 17 and 11 additional; the upper and lower buffer stopper 28 and 34 impacts that will fully absorb of making by elastic material from built-up piston 13; the upper and lower backplate 29 of hard and 35 of its outer end bonding then can play necessary protective action to upper and lower buffer stopper 28 and 34, prevents that its formula piston 13 that is combined from breaking.To improve the shock proof reliability of hydro-pneumatic spring effectively like this.
Shown in Fig. 1,4, the fit of upper connection assembly 15 places first sealing combination device is as follows:
The part that upper connection assembly 15 is had upper connection Sealing 14 is pressed in the cylinder barrel 2, upper press cover 16 is linked to each other with cylinder barrel 2 by screw thread again; Be processed with the circumferential upper connection pilot hole 27 that is used for dismounting on the upper press cover 16, so that the big dome end face 31 of upper connection assembly 15 and the end face of cylinder barrel 2 are compressed, then use upper connection locking nut 18 that upper press cover 16 is axially locked, prevent that it from unscrewing in vibration processes; Upper connection Sealing 14 is used for preventing the leakage of fluid in the cylinder barrel oil pocket.
As shown in Figure 1, the fit of lower support assembly 5 places second sealing combination device is as follows:
The part that lower support assembly 5 is had lower support Sealing 10 is pressed in the cylinder barrel 2, again lower end cap 4 is linked to each other with cylinder barrel 2 by screw thread, be processed with the circumferential lower support pilot hole 25 that is used for dismounting on the lower end cap 4, so that the end face of lower support assembly 5 with cylinder barrel 2 compressed, then use lower support locking nut 3 that lower end cap 4 is axially locked, prevent that it from unscrewing in vibration processes; Lower support Sealing 10 is used for preventing the leakage of fluid in the cylinder barrel annular oil cavity.
As shown in Figure 1, the fit of lower contact assembly 8 places the 3rd sealing combination device is as follows:
The part that lower contact assembly 8 is had lower contact Sealing 9 is pressed in the piston rod 1, again lower cover 7 is linked to each other with piston rod 1 by screw thread, be processed with the circumferential lower contact pilot hole 26 that is used for dismounting on the lower cover 7, so that the end face of lower contact assembly 8 with piston rod 1 compressed, then use lower contact locking nut 6 that lower cover 7 is axially locked, prevent that it from unscrewing in vibration processes; Lower contact Sealing 9 is used for preventing the leakage of inert gas in the piston rod air cavity.
As shown in Figure 5, be the another embodiment of hydro-pneumatic spring lower contact Placement, be specially adapted to the steering structure of vehicle propons, thereby can satisfy the requirement of full chassis hydro-pneumatic spring vehicle.Wherein the fit of end cap assembly 20 places the 4th sealing combination device is as follows:
An end that end cap assembly 20 is had the little Sealing 22 of end cap is by being pressed into shown in the figure in the piston rod 1, to link to each other with piston rod 1 by screw thread with the sleeve 19 that the F of vehicle bridge steering equipment (among the figure shown in the double dot dash line) matches again, be processed with the circumferential sleeve fitting recess 32 that is used for dismounting on the sleeve 19, so that the end face of end cap assembly 20 with piston rod 1 compressed, then use lower contact locking nut 6 that sleeve 19 is axially locked, prevent that it from unscrewing in the Vehicular turn process; The little Sealing 22 of end cap is used for preventing the leakage of inert gas in the piston rod air cavity B.Because sleeve air cavity E is communicated with piston rod air cavity B, is filled with high-pressure inert gas,, be used for preventing that the inert gas among the sleeve air cavity E from producing leakage so on end cap assembly 20, also need to install the big Sealing 21 of end cap at least again additional one.
Shown in Fig. 5,6,7 and 8, at first sleeve 19 is packed among the F of vehicle bridge steering equipment, again the projection 37 on the following connecting cover 24 is buckled in the groove of the F of vehicle bridge steering equipment corresponding with it, then by corresponding circumferential tapped hole 33 in unthreaded hole 36 circumferential in the following connecting cover 24 and the sleeve 19, with threaded fastener 23 they are fastened to together, the quantity of hole and threaded fastener is not limited to 4 shown in the present embodiment, can decide as the case may be.Like this, the lower contact of piston rod 1 just connects together with the steering equipment of vehicle, and when Vehicular turn, piston rod 1 can be with steering equipment along rotational, thereby has satisfied the requirement of vehicle propons assembly lube air spring.
Shown in Fig. 1,5, be not difficult to find, more than the Placement of four kinds of sealing combination devices all be similar: the joint and the end assembly that have Sealing compress by compacting part respectively, and the locking nut that re-uses different inside/outside diameter sizes is axially locked with compacting part.The Placement of connector assembly and vehicle frame and vehicle bridge is not limited only to shown in the foregoing description about it is emphasized that, need be determined on a case-by-case basis.Because hydro-pneumatic spring its cavity pressure in the course of the work often will reach tens or even tens MPas, such high pressure is very harsh to the requirement of seal arrangement, the careless slightly leakage that will cause fluid and gas, especially at lower contact assembly 8 places of the upper connection assembly 15 and the piston rod 1 of cylinder barrel 2, all the time all bearing very big variation dynamic load again from vehicle frame and vehicle bridge, so also just become one of main leakage point of hydro-pneumatic spring, also be simultaneously a main bottleneck of restriction hydro-pneumatic spring development.And adopt above-mentioned sealing combination device, can fully reduce hydro-pneumatic spring and produce the possibility of leaking.From preventing test situation on the spot, vehicle at various road travelings nearly 20,000 kilometers, use the hydro-pneumatic spring of this sealing combination device the situation of any leakage of oil, gas leakage not occur, improved the anti-reliability of leaking of hydro-pneumatic spring greatly, guaranteed vehicle and occupant's driving safety; In addition, adopt such sealing combination device, reduced the weight and the difficulty of processing of single component, and improved assembly quality and efficient effectively.
Shown in Fig. 9,10, be the structural drawing of built-up piston 13.Wherein load lid 40 links to each other with piston rod 1 by screw thread, and piston ring 38 is compressed; Throttle valve plate group 45 is sleeved on the load lid 40; Piston end cap 39 links to each other with piston ring 38 by screw thread, and the inner ring of throttle valve plate group 45 is compressed, and has also played simultaneously the effect of locking load lid 40, prevents that screw thread unscrews between itself and the piston rod 1.
Shown in Figure 11,12, piston end cap 39 circumferentially has the assembling oil-through hole 42 of some.The quantity of assembling oil-through hole 42 is not limited only to shown in the present embodiment 6, needs decide as the case may be.The effect of assembling oil-through hole 42 mainly contains two, is that special assembly tool easy to use makes piston end cap 39 obtain enough impacting forces on the one hand; On the other hand, in the hydro-pneumatic spring working procedure, work the oil effect of being.Except assembling oil-through hole 42, also be processed with circular groove 43, and the two connection.In last circular groove 43, leave annular stop piece 47, be used for limiting the maximum deformation quantity of throttle valve plate group 45 among Figure 10, the protection valve block is no more than ultimate strength and ruptures; The last center hole of piston end cap 39 is used for cylinder barrel oil pocket D and piston rod oil pocket A are communicated to together.
Shown in Figure 13,14, the topology view for load lid 40 has the throttle valve film trap 49 that is used for suit throttle valve plate group 45, and a following circular groove 48 that is communicated with throttle valve film trap 49; In following circular groove 48, leave down annular stop piece 50, be used for limiting the maximum deformation quantity of throttle valve plate group 45 among Figure 10, the protection valve block is no more than ultimate strength and ruptures.A in view as can be seen, the following center hole 51 of load lid 40 be a Hexagon so that use special assembly tool to obtain enough impacting forces by load lid 40, the while, this center hole also was communicated to cylinder barrel oil pocket and piston rod oil pocket together.
Shown in Fig. 9,13, piston ring 38 has circumferential knuckle oil-through hole 41.The quantity of knuckle oil-through hole 41 can be decided as the case may be, and is communicated with the following circular groove 48 of load lid 40; Piston ring 38 mainly plays the effect of supporting and guiding to piston rod 1.
As shown in figure 10, throttle valve plate group 45 is that the throttle valve plate by some is formed by stacking, wherein the valve block of both sides is more smaller than the external diameter of center position valve block, and the wall 44 of both sides valve block and load lid 40 interferes when throttle valve plate group 45 bulk deformations to avoid.The hydro-pneumatic spring of present embodiment mainly relies on the distortion of throttle valve plate group 45 outward edges, and throttling generation damping force is carried out to fluid in the formation annulus between load lid 40 and the piston end cap 39.1., can change Resistance Value by following dual mode: because the width of damping force and annulus has direct relation, so cover 40 and the physical dimension of piston end cap 39 walls 44 by changing the load match with throttle valve plate group 45, just can change damping force; 2., owing to throttle valve plate group 45 is in the upper and lower circular groove 43,48 of piston end cap 39 and load lid 40, so stressed uniform load that belongs to of throttle valve plate, as shown in figure 11, the throttle valve plate uniform load flexural function formula of deriving voluntarily by elastomechanics flexure of sheet theory:
Wherein: q---the suffered uniform load of throttle valve plate
E---throttle valve plate Young's modulus
The thickness of h---throttle valve plate
G
L---under the uniform load with throttle valve plate inside and outside gauge structure size r
a, r
bRelevant coefficient
W---throttle valve plate amount of deformation
After the inside/outside diameter size of throttle valve plate is determined, G
LCoefficient is a constant, and the thickness of the Young's modulus of the selected material of throttle valve plate and valve block itself directly affects the function relation between its pressure and the amount of deformation; That is to say, select for use identical in outer diameter parameters but have different materials or the throttle valve plate of thickness, can make orifice valve produce different damping forces.The concrete functional form that can also further derive stack throttle valve plate group under the uniform load by above-mentioned formula is as follows:
Wherein: i---the code name of every throttle valve plate
N---throttle valve plate sum
Δ p---total uniform load that the throttle valve plate group is suffered
By (2) formula as can be seen, in the present embodiment under the fit of throttle valve plate group 45, the valve block of different materials, different-thickness is superimposed the function relation between load and the amount of deflection is changed, and that is to say, will make hydro-pneumatic spring produce different damping forces.
Shown in Fig. 1,9,10,11,12,13 and 14, built-up piston 13 uniqueness structurally in the hydro-pneumatic spring as can be seen.After if the hydro-pneumatic spring assembling is finished, find that the structural type that orifice valve can't proper functioning maybe needs to adjust orifice valve reaches different dampings, can be earlier the inert gas of hydro-pneumatic spring air cavity be bled off, then piston rod 1 compression is advanced in the cylinder barrel 2, unscrew upper connection locking nut 18 and upper press cover 16 respectively, and upper press cover 16 is pulled down; Because upper connection Sealing 14 just is in the end position of cylinder barrel 2, so the mode of taking gently to drag just can be taken out upper connection assembly 15 from cylinder barrel 2, in order not damage upper connection Sealing 14 when the dismounting, the end of cylinder barrel 2 is processed with angle of deflection; After upper connection assembly 15 is pulled down, just can see piston end cap 39, use extracting tool it to be taken off, expose throttle valve plate group 45, just can reach the purpose of change damping force by the throttle valve plate stack combinations of changing and adjust above-mentioned different materials and thickness by assembling oil-through hole 42; Need to specify that the throttle valve film trap 49 on the load lid 40 can suitably be processed deeply, to enlarge regulation range; For guaranteeing that piston end cap 39 compresses throttle valve plate group 45 inward flanges, can be used with throttle valve plate group 45 by the adjustment pad 46 of varying number and thickness; The inside/outside diameter size of adjusting pad 46 should be identical with throttle valve film trap 49, so just can not influence the stress deformation of throttle valve plate group 45; In addition, can also use and adjust the relative position that pad 46 is adjusted upper and lower annular stop piece 47,50 in throttle valve plate group 45 both sides end faces and piston end cap 39 and the load lid 40, change the maximum deformation quantity of throttle valve plate group 45, thereby the maximum resistance value is changed; Use special assembly tool load lid 40 to be pulled down by following center hole 51, change piston end cap 39 and load covers the physical dimension of 40 walls 44 and the height and the position of upper and lower annular stop piece 47,50 in the mode of changing component, thereby change Resistance Value and maximum resistance value.
By the way, the core component that is used to produce damping force in the whole built-up piston 13 all disassembles, after corresponding component are adjusted and changed, can restore by above-mentioned assembly method; Piston ring 38 mainly plays the guiding of piston rod 1 and supporting role, so do not need dismounting generally speaking.So just can on the basis of original hydro-pneumatic spring, change Resistance Value easily, to reach the requirement of travelling of different vehicle.Owing to do not destroy the Sealing in the cylinder, thereby the versatility of hydro-pneumatic spring is largely increased.
Working principle below in conjunction with Fig. 1,9,10,11,12,13 and 14 pairs of hydro-pneumatic springs is described in detail.Upper connection assembly 15 links to each other with vehicle frame by link, and lower contact assembly 8 links to each other with vehicle bridge by link; Vehicle in the process of moving, wheel can be along with the uneven of road surface jumps up and down, thereby makes the reciprocal relative movement of generation between hydro-pneumatic spring piston rod 1 and the cylinder barrel 2.
When piston rod 1 is in compression stroke, cylinder barrel oil pocket D volume diminishes, cavity pressure increases, a part of fluid wherein will enter piston rod oil pocket A by the last center hole of piston end cap 39 and the following center hole 51 of load lid 40, and promote inert gas among the floating piston 12 compression piston bar air cavity B, increase spring rate and fully absorb impact energy to produce high pressure from ground.Simultaneously because the volume of cylinder barrel annular oil cavity C becomes big, cavity pressure reduces, so throttle valve plate group 45 two ends will produce pressure reduction, and cover 40 1 sides distortion to load, just formed the annulus between the wall 44 of throttle valve plate group 45 and load lid 40 like this, another part fluid of cylinder barrel oil pocket will be successively flows into cylinder barrel annular oil cavity C from assembling oil-through hole 42 and last circular groove 43, the annulus of throttle valve plate group 45, the following circular groove 48 of load lid 40 and the knuckle oil-through hole 41 of piston ring 38 of piston end cap 39, to replenish the volume of its increase.Because the annulus area is very little, can carry out throttling to the fluid that flows through, will produce compression damping power to consume the impact energy on ground; When piston rod 1 is in the recovery stroke, it is big that cylinder barrel oil pocket D volume becomes, cavity pressure reduces, high-pressure inert gas among the piston rod air cavity B will promote the fluid among the floating piston 12 compression piston bar oil pocket A, enter cylinder barrel oil pocket D by the following center hole 51 of load lid 40 and the last center hole of piston end cap 39, to replenish the volume of its increase.Volume owing to cylinder barrel annular oil cavity C diminishes simultaneously, cavity pressure increases, so throttle valve plate group 45 two ends will produce pressure reduction, and be out of shape to piston end cap 39 1 sides, throttle valve plate group 45 just successively and between the wall 44 of load lid 40 and piston end cap 39 has formed the annulus like this, and the part fluid of cylinder barrel annular oil cavity C will successively flow into cylinder barrel oil pocket D from the knuckle oil-through hole 41 of piston ring 38, the following circular groove 48 of load lid 40, the annulus of throttle valve plate group 45 and the last circular groove 43 and the assembling oil-through hole 42 of piston end cap 39.Because the annulus area is very little, and the fluid that flows through is carried out throttling, thereby will produce recovery damping force to consume the impact energy on ground.
Although shown in the accompanying drawing is single chamber hydragas spring, but those skilled in the art can easily understand, built-up piston involved in the present invention can be installed in the hydro-pneumatic spring of other type equally in the above described manner, and under the situation that does not break away from the spirit and scope of the present invention that are defined by the following claims, can carry out various change and change to the present invention.
Claims (6)
1, a kind of hydro-pneumatic spring built-up piston, comprise piston ring, the piston end cap, the load lid, annular throttle valve plate group and annular are adjusted pad, the piston rod of hydro-pneumatic spring is sleeved in the cylinder barrel, it is characterized in that: described load lid links to each other with piston rod by screw thread, and the piston ring that will play supporting and leading role compresses, throttle valve plate group and adjustment pad are sleeved on load and cover end, the piston end cap links to each other with piston ring by screw thread, and with load lid together with the inner ring of throttle valve plate group with adjust pad and compress, lock the load lid simultaneously, prevent that the screw thread between load lid and the piston rod from unscrewing.
2, hydro-pneumatic spring built-up piston according to claim 1, it is characterized in that: piston ring circumferentially is processed with the knuckle oil-through hole, is communicated with cylinder barrel annular oil cavity and cylinder barrel oil pocket.
3, hydro-pneumatic spring built-up piston according to claim 1, it is characterized in that: the piston end cap circumferentially is processed with the assembling oil-through hole of being convenient to dismounting and playing the oil effect, center position is processed with the last center hole that is communicated with cylinder barrel oil pocket and piston rod oil pocket, be processed with towards throttle valve plate group one side restriction throttle valve plate group maximum deformation quantity on the annular stop piece, being processed into the wall shape, be used to change throttle chink width and damping force with the throttle valve plate group outward edge amount of deformation place of matching.
4, hydro-pneumatic spring built-up piston according to claim 1, it is characterized in that: the load lid is processed with the throttle valve film trap of suit throttle valve plate group, be processed with the following annular stop piece that is used to limit throttle valve plate group maximum deformation quantity towards throttle valve plate group one side, being processed into the wall shape, be used to change throttle chink width and damping force with the throttle valve plate group outward edge amount of deformation place of matching.
5, hydro-pneumatic spring built-up piston according to claim 1, it is characterized in that: the throttle valve film trap that annular is adjusted in pad inside/outside diameter size and the load lid is consistent, to play the effect that compresses the throttle valve plate group and adjust throttle valve plate group maximum deformation quantity and maximum damping force.
6, hydro-pneumatic spring built-up piston according to claim 1, it is characterized in that: the throttle valve plate group is formed by annular throttle valve plate stack combinations, the valve block of both sides is more smaller than the external diameter of center position valve block, and the wall shape of covering with load when guaranteeing distortion does not interfere.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200710118958A CN100591943C (en) | 2007-06-15 | 2007-06-15 | Combined piston of gas-oil spring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN200710118958A CN100591943C (en) | 2007-06-15 | 2007-06-15 | Combined piston of gas-oil spring |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101070889A true CN101070889A (en) | 2007-11-14 |
| CN100591943C CN100591943C (en) | 2010-02-24 |
Family
ID=38898249
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200710118958A Expired - Fee Related CN100591943C (en) | 2007-06-15 | 2007-06-15 | Combined piston of gas-oil spring |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100591943C (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094927A (en) * | 2011-01-14 | 2011-06-15 | 北京理工大学 | Integral type pneumatic spring with controllable third-level damp and adaptive second-level stiffness |
| CN105673763A (en) * | 2016-03-23 | 2016-06-15 | 新乡市新华液压机械有限公司 | Inflatable type damper guider sealing structure |
| CN109667876A (en) * | 2017-10-16 | 2019-04-23 | 株洲中车时代电气股份有限公司 | A kind of oil-pressure damper piston and oil-pressure damper |
| CN111237377A (en) * | 2018-11-29 | 2020-06-05 | 蒂森克虏伯比尔斯坦有限公司 | Adjustable vibration damper and vehicle with same |
| CN113124083A (en) * | 2021-04-14 | 2021-07-16 | 北京科技大学 | Hydro-pneumatic spring and car |
| CN115929830A (en) * | 2022-12-23 | 2023-04-07 | 宁波鸿裕工业有限公司 | High bounce-back shock absorber and vehicle |
-
2007
- 2007-06-15 CN CN200710118958A patent/CN100591943C/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094927A (en) * | 2011-01-14 | 2011-06-15 | 北京理工大学 | Integral type pneumatic spring with controllable third-level damp and adaptive second-level stiffness |
| CN105673763A (en) * | 2016-03-23 | 2016-06-15 | 新乡市新华液压机械有限公司 | Inflatable type damper guider sealing structure |
| CN109667876A (en) * | 2017-10-16 | 2019-04-23 | 株洲中车时代电气股份有限公司 | A kind of oil-pressure damper piston and oil-pressure damper |
| CN109667876B (en) * | 2017-10-16 | 2020-03-27 | 株洲中车时代电气股份有限公司 | Oil pressure shock absorber piston and oil pressure shock absorber |
| CN111237377A (en) * | 2018-11-29 | 2020-06-05 | 蒂森克虏伯比尔斯坦有限公司 | Adjustable vibration damper and vehicle with same |
| US11391337B2 (en) | 2018-11-29 | 2022-07-19 | Thyssenkrupp Bilstein Gmbh | Adjustable vibration damper and vehicle having such a vibration damper |
| CN113124083A (en) * | 2021-04-14 | 2021-07-16 | 北京科技大学 | Hydro-pneumatic spring and car |
| CN113124083B (en) * | 2021-04-14 | 2022-09-16 | 北京科技大学 | Hydro-pneumatic spring and car |
| CN115929830A (en) * | 2022-12-23 | 2023-04-07 | 宁波鸿裕工业有限公司 | High bounce-back shock absorber and vehicle |
| CN115929830B (en) * | 2022-12-23 | 2023-08-15 | 宁波鸿裕工业有限公司 | High-rebound-force shock absorber and vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100591943C (en) | 2010-02-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100591943C (en) | Combined piston of gas-oil spring | |
| CN201083245Y (en) | Oil gas spring with control valve | |
| KR101218834B1 (en) | Body amplitude sensitive air spring | |
| EP0000287A1 (en) | A hydro-pneumatic spring suspension strut for motor vehicles | |
| CN201747842U (en) | Single barrel type oil and gas spring | |
| CN101070891A (en) | Throttling valve sheet group of oil-gas spring | |
| CN2547546Y (en) | Abrasion-free non-linear-damping combined vibration-damp locating spring | |
| CN103511536A (en) | Overload prevention hydraulic balance absorber | |
| CN203248591U (en) | Vibration damper for heavy-loaded truck | |
| EP0601014A1 (en) | Suspension system | |
| WO2019015604A1 (en) | Dual-spring damper assembly | |
| CN203348402U (en) | Anti-overloading hydraulic balance shock absorber | |
| CN201116581Y (en) | Sealing combination device for oil-gas spring | |
| CN203308997U (en) | Hydraulic balancing shock absorber | |
| CN201083248Y (en) | Cushioning device for oil gas spring | |
| CN101070892B (en) | Sealing combination device of oil-gas spring | |
| CN100381727C (en) | Spring shock absorber with rubber | |
| CN201116580Y (en) | Throttle valve sheet set for oil-gas spring | |
| CN110206843A (en) | A kind of twin-tub cylinder double chamber hydragas spring | |
| CN210661182U (en) | Electronic composite shock absorber | |
| CN106678260A (en) | Automobile damper | |
| CN209414495U (en) | A kind of air spring vibration damper assembly with lateral force buffer function | |
| KR100235446B1 (en) | Double cylinder type shock absorber | |
| CN2517642Y (en) | Anti-snake shape hydraulic shock damper | |
| CN2195001Y (en) | Hydraulic shock-absorber for automotive suspension |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100224 Termination date: 20100615 |