CN101074713A - Hydraulic shock absorber - Google Patents
Hydraulic shock absorber Download PDFInfo
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- CN101074713A CN101074713A CN 200710107044 CN200710107044A CN101074713A CN 101074713 A CN101074713 A CN 101074713A CN 200710107044 CN200710107044 CN 200710107044 CN 200710107044 A CN200710107044 A CN 200710107044A CN 101074713 A CN101074713 A CN 101074713A
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- hydraulic damper
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- incline section
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Abstract
The invention provides a hydraulic shock absorber comprising a cylinder body, a rod and a piston. The cylinder body is cylindrical with open foreside and forms the shape of the hydraulic shock absorber. The rod has a back end inserting into the cylinder body and a front end protruding from the cylinder body. The rod move forward and back selectively according to the contact with the collide object. The piston is set in the cylinder body and installed on the back end of rod, and moves with the rod together forward and back. The cylinder body includes a sloping portion that forms on the circumference in it. The sloping portion slopes in order to make the inside diameter of the cylinder body to decrease along the backward direction. The area of the hole which is used as the flow path of oil changes according to the forward and backward moving of the piston.
Description
Technical field
The present invention relates to a kind of hydraulic damper, and relate in particular to following hydraulic damper, having incline section and piston on the inner circumference of its cylinder body can wherein be positioned at the oil mass of the hole control flows of piston outside through this hole optionally near the incline section setting.
Background technique
Hydraulic damper is a kind of vibration damper that uses the turbulent drag (with square proportional resistance of speed) of fluid as damping force.Fluid uses working fluid usually.Fluid resistance should be used for the hole (being limited to the through hole of dividing plate) of fluid or the area of passage from activated valve control by means of producing from activated valve.
Such hydraulic damper can be divided into straight line type vibration damper and level type (lever-type) vibration damper, and wherein the straight line type vibration damper is configured to piston, and the level type vibration damper constitutes pivotable flap or cylinder configuration.Automobile absorber and pillar all are the forms of hydraulic damper, and the straight line type vibration damper is generally used for this application.Hydraulic damper also is used for railway vehicle, the undercarriage of aircraft, the pipeline damping and be used to open the door damping.
Fig. 1 is the stereogram according to the hydraulic damper of prior art, and Fig. 2 is the sectional view that illustrates according to the internal structure of the hydraulic damper of prior art.With reference to Fig. 1 and 2, hydraulic damper has the cylinder body 10 that forms its external shape, and is filled in cylinder body 10 inside as the oily O of working fluid.
Center portion's formation within it of piston 12 is passed in hole 14.Hole 14 forms with predetermined diameter from the front portion of piston 12 to the rear portion, for the motion of oily O provides passage.
Piston ring 20 further around the excircle setting of piston 12 controlling the flow of oily O, and the pressure spring 22 that is used for that piston 12 is pushed away forward is arranged on piston 12 rear portions (hereinafter on right side that Fig. 2 observes).
The rod guidance 24 that is used for strut 16 is arranged on the place ahead of cylinder body 10 inside, is used to prevent that the oil sealing 26 of oily O leakage further is installed in the front of rod guidance 24.
Description is according to the operational instruction of the hydraulic damper of the said structure of prior art now.
When external force was applied to bar 16 anterior, piston 12 moved backward.Here, be filled in oily O pressurized in the compartment at piston 12 rear portions.Yet, because oily O is an incompressible fluid, so flow through hole 14 of oil O arrives the compartment of pistons 12 fronts when piston 12 is compressed.
Move through hole 14 and arrive the size Control of anterior oily O amount by hole 14.Therefore, the resistance of oily O is used to absorb the collision energy of external impact by hydraulic damper.
Hydraulic damper is designed to change the viscosity of the size in volume, hole 14 of cylinder body 10 and oily O to obtain the damping of q.s.And, be designed to keep hole 14 sizes of being scheduled to and the hydraulic damper of oil viscosity to have the proportional cushioning ability of the striking force a certain amount of and external impact that causes body.
Therefore, the striking speed of external impact object high more (perhaps collision energy is high more), then the corresponding reaction damping of hydraulic damper is big more.This self regulating charactoristic of vibration damper is it in order to provide big damping force corresponding to big collision energy to make the nature of appropriate reaction.
Be described below variation, as shown in FIG. 3 according to the cushioning ability of the oil bumper of prior art.
Fig. 3 is the plotted curve that illustrates according to the damping force of the hydraulic damper of prior art.The x axle is represented the stroke S of piston, and the y axle is represented damping force.As shown in FIG. 3, when door or other collision object and hydraulic damper collision, striking speed is in the moment maximum of bump, and at this moment hydraulic damper produces its maximum damping force F
D
Here, when increasing, striking speed is in peaked damping force F
DBecome bigger, so big damping force F
DReduce the travelling speed of collision object rapidly.Therefore, in the damping that on the stroke of stroke S, takes place, when beginning, applied maximum damping force F
DAfterwards, damping force F
DReduce suddenly.
Yet, in above-mentioned hydraulic damper, have following point according to prior art.
In the hydraulic damper according to prior art, damping force is determined by the speed of piston 12 (or collision object), the size in hole 14, the cross sectional area of cylinder body 10 and the viscosity of oily O.In these variablees, the viscosity of the size in hole 14, the cross sectional area of cylinder body and oily O is that wherein they are adjusted to the level that is suitable for the employed expection environment of vibration damper at fixing variable of design phase.
Because the door or the striking speed of other collision object can change the processing of object or other environmental factor according to the user, so object does not always act on the hydraulic damper in an identical manner.
Therefore, if the striking speed of collision object is faster than the design striking speed of vibration damper, thereby the kinergety of collision object will become bigger with damping force bigger and that provided when bump begins by hydraulic damper so.
Therefore, although hydraulic damper can absorb the kinergety of collision object with shock absorbing, the big shock-absorbing power that applies when the bump beginning may produce noise.In this case, not only damaged one of them major function (noise reduces) of hydraulic damper, and noise can evoke the discontented of user.
Equally, owing to producing big shock-absorbing power when initial,, damage hydraulic damper, and other problem may occur so may damage door or other collision object with the bump of collision object.
Summary of the invention
Therefore, the present invention proposes a kind of hydraulic damper, and it has been eliminated basically because the limitation of prior art and one or more problems that shortcoming causes.
The purpose of this invention is to provide a kind of hydraulic damper, this hydraulic damper has incline section and the optionally close incline section setting of piston on the inner circumference of cylinder body, wherein be positioned at the oil mass of the hole control flows of piston outside through this hole.
Additional advantage of the present invention, purpose and characteristic will be discussed in the following description, and part will be significantly to those of ordinary skill in the art when studying hereinafter or can learn from the practice of the present invention.The objectives and other advantages of the present invention can realize by the structure that particularly points out in the specification of writing and its claim and accompanying drawing and obtain.
For the advantage that realizes these purposes and other and according to the intent of the present invention, as implement in this article and broadly described, a kind of hydraulic damper is provided, comprising: cylinder body, it forms the cylindrical shape that has open front, and forms the profile of hydraulic damper; Bar, it has rear end that is inserted in the cylinder body and the front end of giving prominence to from cylinder body, and described pole-footing is according to moving forward and backward with contacting optionally of collision object; And piston, it is arranged in the described cylinder body and is installed to the rear end of described bar, be used for moving forward and backward with described bar, wherein said cylinder body comprises the incline section that is formed on its inner circumference, described incline section tilts for making the internal diameter of cylinder body reduce gradually along backward direction, and as the area in the hole of the flow channel of oil according to described piston forward and motion backward change.
Therefore, because be formed on according to the hole of hydraulic damper of the present invention between the excircle of the inner circumference of cylinder body and piston, can make more simply so be used to form the structure in this hole, so whole manufacture cost reduces and output increases.
And, being provided with gradient by the incline section that will form this hole, the size in this hole reduces when piston is advanced backward, so damping force can increase.
Therefore, under the situation of high striking speed,, therefore can reduce to collide the shock-absorbing power when initial, so the damping process proceeds to the part that the area in hole reduces because when incline section was anterior, the area in hole was bigger.Therefore, the process of damping has prolonged.
Therefore,, also can prevent noise, and the speed of door and other collision object can be controlled by the continuous absorption of vibrations by the collision generation even under the striking speed condition with higher of collision object.
Therefore, the object that has different striking speeies that caused by the various factors in the user environment can be reduced to identical speed to produce identical cushioning effect during damping.In a word, hydraulic damper can be handled the striking speed that various user environments cause effectively.
And, by preventing noise, can prevent because the user that undue noise causes is discontented by the collision generation of high speed object.
Should be understood that aforesaid general description of the present invention and following detailed description are exemplary and indicative and are intended to provide the further explanation of claimed invention.
Description of drawings
Comprise with thinking and the invention provides further understanding and be merged in and the accompanying drawing that constitutes this application part illustrates embodiments of the present invention, and be used from specification one and explain principle of the present invention.In the accompanying drawings:
Fig. 1 is the stereogram according to the hydraulic damper of prior art;
Fig. 2 is the sectional view that illustrates according to the internal structure of the hydraulic damper of prior art;
Fig. 3 is the plotted curve that illustrates according to the damping force of the hydraulic damper of prior art;
Fig. 4 is the exploded perspective view of hydraulic damper according to the preferred embodiment of the present invention;
Fig. 5 illustrates the sectional view of the internal structure of hydraulic damper according to the preferred embodiment of the present invention;
Fig. 6 illustrates according to the preferred embodiment of the present invention the internal structure that is applied with the hydraulic damper of external force on it;
Fig. 7 and 8 is amplification views of hydraulic damper according to the preferred embodiment of the present invention, the flowing of oil in it when being illustrated in external force and being applied on the hydraulic damper;
Fig. 9 is when external force sectional view of hydraulic damper according to the preferred embodiment of the present invention when hydraulic damper is removed;
Figure 10 is the amplification view of hydraulic damper according to the preferred embodiment of the present invention, is illustrated in external force the flowing of oil in it when hydraulic damper is removed;
Figure 11 illustrates the plotted curve of the damping force variation of hydraulic damper according to the preferred embodiment of the present invention; And
Figure 12 is the sectional view that the internal structure of the hydraulic damper of another mode of execution according to the present invention is shown.
Embodiment
In detail with reference to preferred implementation of the present invention, its example is shown in the drawings now.Yet the present invention can should not be construed with different ways enforcement and the present invention and be limited to mode of execution as herein described.
Fig. 4 is the exploded perspective view of hydraulic damper according to the preferred embodiment of the present invention, and Fig. 5 illustrates the sectional view of the internal structure of hydraulic damper according to the preferred embodiment of the present invention.
With reference to Fig. 4 and Fig. 5, hydraulic damper has the outside that is formed by cylinder body 100, and this cylinder body is (referring to the Figure 4 and 5) that open wide in its front portion.The inside of cylinder body 100 is provided with (they will describe in detail below) such as piston 200, bar 300, rod guidance 600.When these parts moved around in cylinder body 100, the inside of cylinder body 100 was filled with the oily O as working fluid.
And incline section 120 can be formed with single inclined-plane or a plurality of tilting zone 122 and 124 as required.Here, each tilting zone 122 and 124 can form has different slopes, and can design in every way according to the shock-absorbing characteristic of hydraulic damper.
Therefore, the area in the hole 140 that forms between the outer surface of the internal surface of incline section 120 and piston 200 reduces on each tilting zone 122 and 124 stage by stage, so according to the inclination of corresponding tilting zone 122 and 124, the area in hole 140 reduces towards the rear portion.
Form is the front portion of opening wide that the cylindrical bar 300 of predetermined length is inserted into cylinder body 100.According to treat contacting of damping object, bar 300 can optionally move into or shift out cylinder body 100.
The front end of bar 300 is by outstanding exposure the from the front portion of cylinder body 100, and the front surface that opens wide that cylinder body 100 is passed in the rear end of bar 300 is inserted in the cylinder body 100.Therefore, when treating the front end of damping object contact lever 300, bar 300 moves backward and is inserted in the cylinder body 100.
Piston 200 is installed on the rear end of bar 300.Piston 200 (shape is approximately cylindrical) moves forward and backward in cylinder body 100 with bar 300.Pass the flow of the oily O in the hole 140 that forms between the outer surface of the internal surface of cylinder body 100 and piston 200 for control optionally, the internal surface of cylinder body 100 can optionally be divided into different sizes.
Correspondingly, the inside of cylinder body 100 is divided into the front space F that is positioned at piston 200 fronts by piston 200 and is positioned at piston 200 back space B afterwards, and wherein the volume separately of front space F and back space B is variable according to the motion of piston 200.
Excircle around piston 200 about centre is equipped with piston ring 242, carrying out small motion with respect to piston 200.Piston ring 242 forms the ring that external diameter is slightly less than cylinder body 100 internal diameters.
Correspondingly, the outer surface of piston ring 242 forms the outmost part of piston 200, so hole 140 is formed on the excircle of piston ring 242 and the inner circumference of cylinder body 100 is between the incline section 120, so the motion control that flows through the hole of oily O during the seesawing of piston 200.
The ring mounting portion 240 that is used for ring installation 242 is formed on the central authorities of the excircle of piston 200 (piston ring 242 is with mounted thereto).Ring mounting portion 240 is recessed into predetermined depth in the piston 200 can hold piston ring 242 and to be recessed into the degree of depth that can realize micro-gap with the internal surface of piston ring 242, and ring mounting portion 240 also is formed with the width above piston ring 242 width, when piston 200 moved forward and backward, piston ring 242 can move in ring mounting portion 240 according to the resistance of oil like this.
The support plate 260 that is used to support pressure spring 400 (will be described below) front end is formed on the back of ring mounting portion 240.Support plate 260 forms from the excircle of piston 200 vertical outwards outstanding, and radially forms a plurality of around the excircle of piston 200 with predetermined interval.Therefore, support plate 260 supports the pressure of pressure spring 400 as described below, forms the passage that allows oily O to flow through the space between the corresponding support plate 260 simultaneously.
The spring insertion portion 280 that is used to be inserted on the spring 400 forms from the rear portion of support plate 260 outstanding backward.The excircle of spring insertion portion 280 can form the inner circumference less than pressure spring 400, so that pressure spring 400 is inserted on the spring insertion portion 280.
The pressure spring 400 that is inserted on the spring insertion portion 280 is used for providing compression during piston 200 moves forward and backward, and pressure spring 400 forms has predetermined length, and be compression helical spring, this compression helical spring is subjected to along the compressive force of the central direction of its coil when power is applied on it.
The front end of pressure spring 400 is inserted in and forms from the outstanding spring insertion portion 280 in the rear portion of piston 200, and the rear end of pressure spring is mounted to the internal surface of cylinder body 100 and contacts, so pressure spring 400 can optionally compress according to the motion of piston 200.
The front surface that opens wide of cylinder body 100 is by covering 500 sealings.The middle body of lid 500 limits the lid hole 520 of passing bar 300.And oil sealing 540 is arranged on and covers 500 back and cover 500 rear surface with contact.
Oil sealing 540 is used to prevent that oily O from leaking into cylinder body 100 outsides, and has traditional oil seal structure.Oil sealing hole 542 is formed on about centre of oil sealing 540 in order to pass through bar 300.
The member mounting portion 642 that is used to install balance component 640 is recessed in the excircle of rod guidance 600, makes balance component 640 to remain on wherein.Locking plate 660 forms in the rear end of rod guidance 600 vertical outwards outstanding.
Throw off to prevent balance component 640 rear end of locking plate 660 balance support members 640, is formed for compressing the flow channel of the oily O of balance component 640 simultaneously.Excircle around rod guidance 600 radially is formed with a plurality of locking plates 660 with predetermined interval.
Operation according to the hydraulic damper of said structure of the present invention is described with reference to the accompanying drawings.
Fig. 6 is the sectional view that the internal structure of the hydraulic damper that is applied with external force on it is shown according to the preferred embodiment of the present invention, Fig. 7 and 8 is amplification views of hydraulic damper according to the preferred embodiment of the present invention, the flowing of oil in it when being illustrated in external force and being applied on the hydraulic damper.
With reference to Fig. 6 to 8, when collision object bumped against with predetermined striking speed and bar, bar 300 inwardly was inserted in the piston 200, and piston 200 moves backward simultaneously.
Because the motion backward of piston 200, the oily O that fills among the back space B is mobile along direction forward along the hole 140 that forms between incline section 120 and the piston ring 242.
When oily O moved forward, piston ring 242 was pressed against the front end that encircles mounting portion 240 by the resistance of oily O, and moves backward with piston 200.
Here, incline section 120 forms has predetermined gradient, and therefore when piston 200 was mobile backward, the distance between piston ring 242 and the incline section 120 reduced.Therefore, the cross sectional area in hole 140 reduces to make oily resistance to increase, thereby increases the amount of shock-absorbing power.
When piston ring 242 by first tilting zone 122 and when arriving second tilting zone 124, because the slope of second tilting zone 124 is bigger, so the size in hole 140 reduces suddenly when piston 200 moves, so damping force increases suddenly.
The motion backward of piston 200 causes pressure spring 400 to be compressed predetermined length.Therefore, be installed in balance component 640 on the rod guidance 600 and be compressed the quantity that piston 200 enters into cylinder body 100.Like this, balance component 640 can keep the volume unanimity in the cylinder body 100.
Describe another kind of mode below in detail, wherein can apply damping force and be used for differently slowing down the vibrations that the speed by collision object causes according to hydraulic damper of the present invention.
Bump starting point when collision object high-speed impact vibration damper, in the front portion of the incline section 120 that has bigger hole 140, piston 200 has applied little shock-absorbing power, so the piston 200 of high-speed travel slows down gradually and decays.
And when piston 200 continuation were mobile backward, because the gradient of incline section 120, the size in hole 140 reduced gradually.Therefore, the damping force that increases gradually is applied on the piston 200 to continue damping piston 200.
When piston 200 was finished it and moved backward in stroke S, piston ring 242 was in the position of the most close incline section rear end.At this moment, do not have further shock-absorbing power to be applied on the piston 200, therefore finish the impact damping.
Though do not describe in detail, be divided at incline section 120 under the situation of a plurality of tilting zones 122 and 124, the gradient in each tilting zone 122 and 124 provides the damping force that increases backward.As shown in the figure, when the gradient of second tilting zone 124 during greater than the gradient of first tilting zone 122, between first tilting zone 122 of incline section 120 and second tilting zone 124 reducing suddenly of damping force appearred.
Next, Fig. 9 is when external force sectional view of hydraulic damper according to the preferred embodiment of the present invention when hydraulic damper is removed, Figure 10 is the amplification view of hydraulic damper according to the preferred embodiment of the present invention, is illustrated in external force the flowing of oil in it when hydraulic damper is removed.
With reference to Fig. 9 and Figure 10, when the collision of collision object caused bar 300 to be inserted in the cylinder body 100 fully, piston 200 was positioned at its rearmost position.In this state, pressure spring 400 is compressed the biglyyest.
In this state, when the collision object of contact lever 300 was removed, the power that is pressed on the bar 300 was also removed, so bar 300 and piston 200 bias voltage by pressure spring 400 moves forward.
Here, when piston 200 moved forward, the oil among the front space F flowed to back space B.
In more detail, when piston 200 moved forward, the piston ring 242 that is installed on the piston 200 was pressed against the support plate 260 that encircles mounting portion 240 rear end.
Here, support plate 260 forms a plurality of at regular intervals, make oil flow through between a plurality of support plates 260 the space and after by piston ring 242, flow into front space F.
Certainly, moving forward of piston 200 realized in oily O also flow through the forward excircle of piston ring 242 and the hole 140 between the incline section 120 easily.
That is to say that because the space of the space that oily O flows through when more mobile backward than piston 200 is bigger, so flowing of oily O is freer, so piston 200 moves forward with less resistance.
Because bar 300 is projected into the cylinder body outside in cylinder body 100, so the volume in the cylinder body 100 reduces.Here, the reducing of oily O pressure causes compressed balance component 640 to restore, and therefore, kept the volumetric balance in the cylinder body.
With reference to Figure 11 the variation of the damping force of oil bumper is according to the preferred embodiment of the present invention described.
Figure 11 illustrates the plotted curve of the damping force variation of hydraulic damper according to the preferred embodiment of the present invention.Here, the x axle is represented piston stroke, and the y axle is represented damping force.
With reference to Figure 11, when door or other collision object and vibration damper collision, at the starting point of bump, damping force F
DBe maximum, with the damped collision object.When advancing on the piston 200 stroke S, produce damping.
Here, in the process of passing stroke S, damping force F
DReduce gradually, and damping force F
DCurve form the bending that descends gradually.
That is to say that according to reducing gradually of the speed of collision object, because at the rear portion of stroke S, the gradient of incline section 120 has reduced the cross sectional area in hole 140, so prevented damping force F
DDescend suddenly.
Therefore, hydraulic damper according to the present invention provides the damping force F that reduces gradually
D, make door or other collision object to advance fast and to advance with the speed that lowers gradually then in the collision starting stage.
When the situation among comparison Figure 11 and Fig. 3, whole area-promptly, and the quantity of kinergety-be identical; Yet, damping force F in Figure 11
DGradually change more, compare, by reducing damping force F with Fig. 3
DRealized more smooth damping effect.
Can differently implement with the variety of way that is different from above-mentioned mode of execution according to oil bumper of the present invention, will describe the some of them mode of execution below with reference to the accompanying drawings.
Equally, other mode of execution according to the present invention not only comprises the structure that is formed on the incline section in the cylinder 100, and comprises the identical hydraulic damper configured in one piece except that said structure.
Therefore, the detailed description of those similar parts of having described in the above-described embodiment will no longer repeat.
Figure 12 is the sectional view that the internal structure of the hydraulic damper of another mode of execution according to the present invention is shown.As shown in Figure 12, the incline section 120 that in the inner circumference of cylinder body 100, forms ' form from front to back along the whole inner circumference of cylinder body 100.
That is to say, incline section 120 ' form from the front portion of cylinder body 100 inner circumferences to tilt, and have progressive inclined-plane to the rear portion, this inclined-plane is with predetermined gradient narrow down towards the rear portion (cross-sectional width).
Therefore, when piston 200 was mobile backwards, the size in hole 140 reduced gradually, so when collision object and vibration damper collision, damping force increases.
Those skilled in the art should be understood that in the present invention can make various modifications and variations.Therefore, expectation the present invention covers modification various of the present invention and the modification that falls in claims of the present invention and the equivalent scope thereof.
For example, in embodiments of the present invention, bar 300 forms the contact-impact object; Yet, also may further include the cylinder body guiding element that is used to receive bar 300 and piston 200 ends.In this case, the rear end contact-impact object of cylinder body 100, and be configured to be inserted in the cylinder body guiding element.
And the installation method of hydraulic damper can comprise whole ABAP Adapter or formation and the door hinge all-in-one-piece vibration damper etc. that have vibration damper that form.
And though piston ring 242 is installed on the excircle of piston 200 in embodiments of the present invention, foundation needs, and piston ring 242 can omit.At this moment, hole 140 can form by piston 200 and incline section 120.
Claims (7)
1. hydraulic damper comprises:
Cylinder body, it forms the cylindrical shape that has open front, and forms the profile of described hydraulic damper;
Bar, it has rear end that is inserted in the described cylinder body and the front end of giving prominence to from described cylinder body, and described pole-footing is according to moving forward and backward with contacting optionally of collision object; And
Piston, it is arranged in the described cylinder body and is installed to the rear end of described bar, is used for moving forward and backward with described bar, wherein
Described cylinder body comprises the incline section that is formed on its inner circumference, described incline section tilts for making the internal diameter of described cylinder body reduce gradually along backward direction, and as the area in the hole of the flow channel of oil according to described piston forward and motion backward change.
2. hydraulic damper as claimed in claim 1, wherein said incline section forms along the whole inner circumference of described cylinder body.
3. hydraulic damper as claimed in claim 1, wherein said incline section is formed in the stroke, and described stroke is the zone that the piston in the described cylinder body can move forward and backward therein.
4. as claim 2 or 3 described hydraulic damper, wherein said incline section comprises a plurality of tilting zones with different gradients.
5. hydraulic damper as claimed in claim 4, wherein said a plurality of tilting zones have gradient separately, and described gradient edge direction backward in described incline section increases.
6. as claim 2 or 3 described hydraulic damper, wherein said piston comprises piston ring, described piston ring forms annular and moves with the excircle along described piston around the excircle installation of described piston, and described piston ring is used to control the area in described hole.
7. hydraulic damper as claimed in claim 6, wherein said piston also comprise the ring mounting portion that caves inward in the excircle of described piston, and described ring mounting portion is used for keeping described piston ring so that it can move in described ring mounting portion.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR20060044049 | 2006-05-17 | ||
| KR10200644049 | 2006-05-17 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101074713A true CN101074713A (en) | 2007-11-21 |
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ID=38975929
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710107044 Pending CN101074713A (en) | 2006-05-17 | 2007-05-17 | Hydraulic shock absorber |
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| Country | Link |
|---|---|
| CN (1) | CN101074713A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102734368A (en) * | 2011-04-01 | 2012-10-17 | Smc株式会社 | Hydraulic shock absorber |
| CN103009954A (en) * | 2011-09-22 | 2013-04-03 | F·波尔希名誉工学博士公司 | Lifting device for vehicle |
| CN104315066A (en) * | 2010-03-02 | 2015-01-28 | 日立汽车***株式会社 | Shock absorber |
-
2007
- 2007-05-17 CN CN 200710107044 patent/CN101074713A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104315066A (en) * | 2010-03-02 | 2015-01-28 | 日立汽车***株式会社 | Shock absorber |
| CN104315066B (en) * | 2010-03-02 | 2016-12-07 | 日立汽车***株式会社 | Buffer |
| CN102734368A (en) * | 2011-04-01 | 2012-10-17 | Smc株式会社 | Hydraulic shock absorber |
| CN102734368B (en) * | 2011-04-01 | 2014-10-08 | Smc株式会社 | Hydraulic shock absorber |
| CN103009954A (en) * | 2011-09-22 | 2013-04-03 | F·波尔希名誉工学博士公司 | Lifting device for vehicle |
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