CN201747842U - Single barrel type oil and gas spring - Google Patents
Single barrel type oil and gas spring Download PDFInfo
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- CN201747842U CN201747842U CN2010202696645U CN201020269664U CN201747842U CN 201747842 U CN201747842 U CN 201747842U CN 2010202696645 U CN2010202696645 U CN 2010202696645U CN 201020269664 U CN201020269664 U CN 201020269664U CN 201747842 U CN201747842 U CN 201747842U
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Abstract
The utility model provides a single barrel type oil and gas spring which comprises a cylinder barrel, a piston rod, a piston and a floating piston, wherein the hollow piston rod is sheathed in the cylinder barrel; the piston is installed at the upper end of the piston rod; the piston rod and the piston are connected together through threads; the floating piston is installed in the inner cavity of the piston rod; the floating piston divides the inner cavity of the piston rod into two cavities, wherein the upper cavity is filled with oil; and the lower cavity is filled with high-pressure inert gas according to vehicle dead load. After the single barrel type oil and gas spring is adopted, vehicle does not need a single damper any more, the structure is simpler, and the system has small volume and light weight and is convenient to disassemble.
Description
Technical field
The utility model relates to a kind of monotubular formula hydro-pneumatic spring.Belong to hydraulic machinery and road vehicle application field, be mainly used in the decay body vibrations, improve Security, smoothness and the cross-country speed of vehicle.
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 model utility content
The purpose of this utility model is to provide a kind of monotubular formula hydro-pneumatic spring, the piston rod of hydro-pneumatic spring is sleeved in the cylinder barrel, the piston rod upper end links to each other with piston, piston has orifice valve, described orifice valve produces the slit by the throttle valve plate distortion of various combination mode, and fluid is carried out throttling and forms damping force.
Monotubular formula hydro-pneumatic spring of the present utility model, comprise cylinder barrel, piston rod, piston and floating piston, wherein, the piston rod of hollow is sleeved in the cylinder barrel, and piston is equipped with in the upper end of piston rod, and both are by being threaded onto together, piston rod cavity is equipped with floating piston, this floating piston is divided into two chambers with piston rod cavity, and wherein upper chamber is full of fluid, and lower chambers charges into corresponding high-pressure inert gas according to the vehicle static load.
Further, between piston rod and cylinder barrel, form annular oil cavity, between cylinder barrel and piston, formed the cylinder barrel oil pocket.
Further, the cylinder barrel oil pocket is communicated with the piston rod oil pocket by the center hole of piston.
Further, in piston, be equipped with the orifice valve of throttle valve plate, spacing back-up ring be installed, between throttle valve plate and spacing back-up ring, annular gasket is installed in the piston outside.
Vehicle no longer needs independent vibration damper after adopting the utility model, easier on the structure, usually air chamber is located in the piston rod, by floating piston with Oil-gas Separation, to adapt to a heavy-duty off-road vehicle big characteristic of moving stroke, overcome the moving little shortcoming of stroke of the isolated hydro-pneumatic spring of diaphragm.This cover system volume is little, in light weight simultaneously, is convenient to dismounting.
Description of drawings
Fig. 1 is the assembly structure chart of monotubular formula hydro-pneumatic spring.
Embodiment
Below in conjunction with accompanying drawing monotubular formula hydro-pneumatic spring is done detailed description:
As shown in Figure 1, the piston rod 2 of hollow is sleeved in the cylinder barrel 1, piston 4 is equipped with in the upper end of piston rod 2, and by being threaded onto together, piston rod 2 inner chambers are equipped with floating piston 3, piston rod 2 inner chambers are divided into two chambers, and wherein upper chamber is full of fluid, and lower chambers charges into corresponding high-pressure inert gas according to the vehicle static load.Between piston rod 2 and cylinder barrel 1, form annular oil cavity C, between cylinder barrel 1 and piston 4, 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 piston 4; In the hydro-pneumatic spring working procedure, because piston 4 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.
As shown in Figure 1, in piston 4, be equipped with the orifice valve of throttle valve plate 5, in piston 4 outsides spacing back-up ring 7 is installed, be used to control the maximum deformation quantity of throttle valve plate 5, prevent the excessive generation phenomenon of rupture of amount of deformation, quantity and thickness that annular gasket 9 is used to adjust throttle valve plate 5 are installed between throttle valve plate 5 and spacing back-up ring 7, are the power value to change valve, and 6 on nut is used for realizing the axially locating to piston 4.
Be described in detail below in conjunction with the working principle of accompanying drawing hydro-pneumatic spring.
When piston rod 2 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 center hole of piston 4, and promote inert gas among the floating piston 3 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 5 two ends will produce pressure reduction, and be out of shape to annular oil cavity C one side, just formed the annulus between throttle valve plate 5 and the piston 4 like this, another part fluid of cylinder barrel oil pocket will flow into cylinder barrel annular oil cavity C by throttle valve plate 5, 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; It is the same to restore the stroke principle.
Although shown in the accompanying drawing is monotubular formula hydro-pneumatic spring, but those skilled in the art can easily understand, the related content of the utility model 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 utility model that are defined by the following claims, can carry out various change and change to the utility model.
Claims (4)
1. monotubular formula hydro-pneumatic spring, comprise cylinder barrel, piston rod, piston and floating piston, it is characterized in that: the piston rod of hollow is sleeved in the cylinder barrel, piston is equipped with in the upper end of piston rod, both are by being threaded onto together, and piston rod cavity is equipped with floating piston, and this floating piston is divided into two chambers with piston rod cavity, wherein upper chamber is full of fluid, and lower chambers charges into corresponding high-pressure inert gas according to the vehicle static load.
2. monotubular formula hydro-pneumatic spring according to claim 1 is characterized in that: formed annular oil cavity between piston rod and cylinder barrel, formed the cylinder barrel oil pocket between cylinder barrel and piston.
3. monotubular formula hydro-pneumatic spring according to claim 2 is characterized in that: the cylinder barrel oil pocket is communicated with the piston rod oil pocket by the center hole of piston.
4. according to any described monotubular formula hydro-pneumatic spring in the claim 1 to 3, it is characterized in that: in piston, be equipped with the orifice valve of throttle valve plate, spacing back-up ring be installed, between throttle valve plate and spacing back-up ring, annular gasket is installed in the piston outside.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202696645U CN201747842U (en) | 2010-07-26 | 2010-07-26 | Single barrel type oil and gas spring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202696645U CN201747842U (en) | 2010-07-26 | 2010-07-26 | Single barrel type oil and gas spring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201747842U true CN201747842U (en) | 2011-02-16 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010202696645U Expired - Fee Related CN201747842U (en) | 2010-07-26 | 2010-07-26 | Single barrel type oil and gas spring |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201747842U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103174788A (en) * | 2013-03-20 | 2013-06-26 | 安徽江淮汽车股份有限公司 | Damping control valve and damping adjusting structure of hydraulic absorber |
| CN103967992A (en) * | 2013-01-30 | 2014-08-06 | 爱思恩梯大宇汽车部件(昆山)有限公司 | Automobile vibration damper piston valve |
| CN105020316A (en) * | 2014-04-29 | 2015-11-04 | 哈尔滨飞机工业集团有限责任公司 | Undercarriage buffer |
| CN105134855A (en) * | 2015-10-16 | 2015-12-09 | 厦门铠睿智能科技有限公司 | Novel oil-gas damper |
| CN105179554A (en) * | 2015-10-16 | 2015-12-23 | 厦门铠睿智能科技有限公司 | Novel mixed connected type oil gas damping device with double gas chambers |
| CN107850162A (en) * | 2015-07-31 | 2018-03-27 | 宝马股份公司 | Fluid pressure type monotubular stretches damping shock absorber |
| CN108488297A (en) * | 2018-04-11 | 2018-09-04 | 华侨大学 | A kind of hydro-pneumatic spring |
| CN111156274A (en) * | 2019-11-29 | 2020-05-15 | 中国北方车辆研究所 | Single-cylinder annular cavity high-pressure hydro-pneumatic spring |
-
2010
- 2010-07-26 CN CN2010202696645U patent/CN201747842U/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103967992A (en) * | 2013-01-30 | 2014-08-06 | 爱思恩梯大宇汽车部件(昆山)有限公司 | Automobile vibration damper piston valve |
| CN103174788A (en) * | 2013-03-20 | 2013-06-26 | 安徽江淮汽车股份有限公司 | Damping control valve and damping adjusting structure of hydraulic absorber |
| CN105020316A (en) * | 2014-04-29 | 2015-11-04 | 哈尔滨飞机工业集团有限责任公司 | Undercarriage buffer |
| CN105020316B (en) * | 2014-04-29 | 2017-01-04 | 哈尔滨飞机工业集团有限责任公司 | A kind of undercarriage buffer |
| CN107850162A (en) * | 2015-07-31 | 2018-03-27 | 宝马股份公司 | Fluid pressure type monotubular stretches damping shock absorber |
| CN107850162B (en) * | 2015-07-31 | 2020-09-08 | 宝马股份公司 | Hydraulic single-cylinder telescopic damping shock absorber |
| CN105134855A (en) * | 2015-10-16 | 2015-12-09 | 厦门铠睿智能科技有限公司 | Novel oil-gas damper |
| CN105179554A (en) * | 2015-10-16 | 2015-12-23 | 厦门铠睿智能科技有限公司 | Novel mixed connected type oil gas damping device with double gas chambers |
| CN108488297A (en) * | 2018-04-11 | 2018-09-04 | 华侨大学 | A kind of hydro-pneumatic spring |
| CN111156274A (en) * | 2019-11-29 | 2020-05-15 | 中国北方车辆研究所 | Single-cylinder annular cavity high-pressure hydro-pneumatic spring |
| CN111156274B (en) * | 2019-11-29 | 2021-11-02 | 中国北方车辆研究所 | Single-cylinder annular cavity high-pressure hydro-pneumatic spring |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 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: 20110216 Termination date: 20110726 |