CN1119251A - Damping valve used in oscillation damper - Google Patents
Damping valve used in oscillation damper Download PDFInfo
- Publication number
- CN1119251A CN1119251A CN95102047.1A CN95102047A CN1119251A CN 1119251 A CN1119251 A CN 1119251A CN 95102047 A CN95102047 A CN 95102047A CN 1119251 A CN1119251 A CN 1119251A
- Authority
- CN
- China
- Prior art keywords
- valve
- building
- out section
- dividing plate
- plate
- 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.)
- Pending
Links
- 230000010355 oscillation Effects 0.000 title claims description 4
- 238000013016 damping Methods 0.000 title abstract description 11
- 230000011218 segmentation Effects 0.000 claims description 9
- 238000007789 sealing Methods 0.000 claims description 2
- 230000002349 favourable effect Effects 0.000 description 5
- 230000002411 adverse Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 241001672694 Citrus reticulata Species 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/3405—Throttling passages in or on piston body, e.g. slots
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Details Of Valves (AREA)
- Check Valves (AREA)
Abstract
A damping valve in particular using for a vibration damper has a damping valve body with at least one admission channel, for one direction of flow through the valve body. The admission channel communicates a top side and a bottom side of the damping valve body to each other. Also included is a valve plate posited on the valve seat surface, and in which the valve plate is liftable from the valve seat surface, and an additional choke is included in a communicating path between the top side and bottom side of the damping valve, and the cross section of the additional choke is defined by the width of an inflow opening of the admission channel and the average radial distance between the inflow opening and edges which determine the valve plate contour.
Description
The present invention relates to a kind of orifice valve.
Known valve scheme for example comes from DE-OS 2500826, and wherein, the thick relatively valve cover with interior profile covers an annular groove.At present, this member must be transported in the robot device when assembling by hand.
In addition, the helical spring valve of this structure type is known, and its building-out section runner that is used for opposed orifice valve is to realize by an additional disc that is positioned at this orifice valve.In addition, advantageous manner is that this valve body unit that has been provided with non-throttling opening can make this orifice valve realize a standardized structure.But its defective is the weakness that this additional member has restriction and illustrated.
In French prospectus FR-OS 2061905, introduced one and had the very valve of simple structure.This valve body is made of plate, and wherein, institute is porose all makes with stamping technology.Thin valve gap dish is to sit to put on the interior standard pitch circle of a band through hole.This valve gap dish can be established the through hole of variable number.The valve disc that is provided with surplus restrictions has critical defect, and its reason is that this valve disc must be provided with respect to the valve body location.Essential again for this reason manual operations does not have rotational symmetric structure because be used for the valve disc of assembling automatically.Because through hole is positioned at the most heavily stressed zone, so seriously slackened fatigue strength.The danger of Cun Zaiing is in addition, and valve disc may rotate with respect to valve body when assembling or work operation, if not complete plugging fluid stream, is to have reduced flow cross at least.
Task of the present invention is to propose a kind of orifice valve, it can make an identical valve body be used for a large amount of orifice valve structures, simultaneously, it has a motion valve member that is applicable to the little quality of good dynamics characteristic, and only have rotational symmetric part, they can automatically assemble, and have less number of spare parts usually, wherein, these parts itself should be able to have a simple especially structure.
The present invention is this task that so solves: the cross section of this building-out section runner is limited by the width of an ostium of flow channel with at the edge of a decision valve plate profile and the average radial spacing between this ostium.According to favourable mode, an identical valve body can be used for a plurality of different orifice valves.In addition, a less damping force only occurs and sew, because valve plate just can be made accurately especially as single member with very little cost, therefore, cross section just only is in the small wave range.
According to another favourable feature, this ostium is placed in the external diameter scope of orifice valve valve body, and wherein, the external diameter of valve plate has determined the cross section of building-out section runner.Consequently, can realize big additional throttling cross section, because the standard pitch circle of settling this building-out section runner is big equally.Relevant therewith, reduced once more determining the influence of building-out section channel size, particularly to the influence of valve plate external diameter.
In another favourable structural type of the present invention, this valve disc is a flexible closed disk structure, in the tensioning of inner diameter place.Such valve disc forms an inexpensive especially part.Because this valve disc is a closing structure, so it can do quite thinly, therefore, the quality of valve disc does not have adverse influence to the performance of orifice valve, has however but guaranteed fatigue strength.
According to another favourable feature, this valve base surface is made of a dividing plate labyrinth system, and this system is separated from each other the flow channel of two circulating directions.This dividing plate labyrinth system can realize that the very big pressure that is used for valve plate applies the surface.In addition, do not have the big bearing surface that is used for valve plate, big bearing surface may cause valve plate to be bonded on the valve base surface.Simultaneously, this dividing plate labyrinth system constitutes by the dividing plate segmentation of advantageous manner by arranged concentric, and they have the dividing plate segmentation of radially extending that separately relevant with direction flow channel is used.Except the structure of big as far as possible valve disc pressure acting surface, can also additionally make this dividing plate labyrinth system optimization as follows, promptly under the situation of little valve seat bearing surface, the bending of valve plate is limited in minimum degree.
According to another feature, this orifice valve has a plurality of building-out section runners.By a preferred dependent claims, exist the condition of minimum building-out section flow channel cross-section to be, the ragged edge circumference area of diaphragm of the outer diameter of valve plate and circulating direction outlet side on the contrary is mutually by putting.In addition, this dividing plate labyrinth system preferably has a radial hole as the building-out section runner.
In addition, stipulate preferably that the cross section of at least two building-out section runners has different size mutually.By this favourable feature, can make the bandwidth of the outer diameter of valve disc keep less.Input channel can be arranged to very narrow mutually (compactness), and the hydraulic pressure short circuit can not occur, and when short circuit, resisting medium can be walked around valve disc and be communicated with between flow channel.Only, done the qualification on the size to making the separated valve disc bearing surface of circulating direction.Further set forth the present invention by means of following the description of the drawings.Wherein:
Fig. 1 a, b are the orifice valves on piston rod;
Fig. 2 a, b are the orifice valves in the bottom valve structure;
Fig. 3 a, b are the damping valve bodies as single-piece.
Fig. 1 represents an orifice valve 1 on piston rod 3, such as it generally is applied in the oscillation damper.This orifice valve 1 has a valve body 1a, and it has a flow channel 5a, 5b at least on each circulating direction.Each flow channel 5 is connected upper side 1b and the downside 1c of valve body 1a.Valve plate 7 is placed at least one side, in this embodiment is to be placed on the upper side 1b, and valve plate 7 fixes to clamp at inner diameter 7a place.Valve plate 7 covers one or more flow channel 5b.Flow channel 5b has the outlet cross section on upper side 1b, so flow channel 5b bears the function of an one-way valve.Valve plate 7 is made the circular disk structure of a sealing simultaneously, and when reaching the enable possition of maximum, this disk 7 just is bearing on the support plate 9.In order to make orifice valve 1 adapt to different orifice valve characteristics, this damping valve body 1a can install the valve plate 7 of varying strength very simply.
For opposite circulating direction from the upper side 1b of orifice valve 1 to downside 1c, this valve plate 7 with degree like this cover corresponding flow channel 5a, i.e. building-out section runner 11 of formation in the zone at flow channel 5a between valve plate 7 and the valve body 1a, it can influence a valve 15 that is positioned at orifice valve downside 1c place and is made of the valve disc 13 of tensioning.By selecting the outer diameter 7b of valve plate 7, just can determine the cross section of this building-out section runner 11 under the damping valve body situation of a regulation very simply.
The orifice valve 15 that is positioned at downside 1c place is by ring edge 19 tensionings of a fixing rivet 17 with respect to valve body 1a.Valve body 1a is connected with piston rod 3 by a punching structure 21 separately, and therefore, the tensioning of giving of valve disc 13 can irrespectively realize with the tolerance of the series structure of being made up of support plate 9, valve plate 7 and valve body 1a.
This Fig. 1 b represents the plan view of orifice valve 1.Wherein, valve plate 7 is bearing in the dividing plate labyrinth system 23.This dividing plate labyrinth system 23 has determined the pressure acting surface that valve plate 7 becomes a mandarin from orifice valve downside 1c.
Should also be noted that the dividing plate segmentation 23a that this dividing plate labyrinth system 23 is settled by a plurality of mutual centering forms, dividing plate segmentation 23a interconnects by the dividing plate 23b that radially extends, and so just two flow channel 5a/bs relevant with direction is separated from each other.The optimization approach of this dividing plate segmentation 23b is as follows, guarantees that valve plate 7 has supporting surface as well as possible, and like this, when meeting of orifice valve upper side 1b miscarried life, valve plate 7 can never be crooked.
Dividing plate labyrinth system 23 can guarantee, between valve plate 7 and damping valve body 1a bonding effect does not take place.In addition, on valve plate 7, exist very big pressure acting surface, thereby can easily realize opening.Be separated from each other two flow channel systems 5 reliably in order to ensure valve plate 7, selected valve plate 7 is than the big a certain definite amount X of adjacent outer diameter 5b ' of the pressure acting surface on valve plate 7.
As can be seen, the average space Y between the outer diameter 5a ' of the outer diameter 7b of the width B of flow channel 5a and valve plate 7 and flow channel 5a has determined the cross section of building-out section runner 11.This structure on a big as far as possible index plate can will reduce to minimum degree by the adverse effect that machining error causes.
Fig. 2 a and 2b have represented an orifice valve 1 in the bottom valve structure.Wherein, on the part 25, cylindrical duct 27 of end part 25 lockings and the stream that holds that surrounds this cylindrical duct managed 29 at the bottom of orifice valve valve body 1a was bearing in one.Its main structure is identical with valve among Fig. 1.In addition, be provided with a radial hole 11a who is used for flow channel 5a in valve body 1a, it is exactly a building-out section runner 11 for the orifice valve 15 on next limit 1c.From the plan view of Fig. 2 b as can be seen, maximum valve plate 7 constitutes minimum building-out section runner, that is has only this radial hole 11a to pass to flow channel.When the outer diameter 7a of valve plate 7 dwindled, numerical value Y increased, and therefore, the cross section of building-out section runner 11 increases, and simultaneously, numerical value x (Fig. 1 b) also should remain unchanged.From figure, can know, a plurality of building-out section runners 11 also can be set.By being set, different building-out section flow channel cross-sections just can make orifice valve very accurately consistent with the orifice valve characteristic curve of a regulation.Particularly advantageously be, the cross section of minimum building-out section runner is made of single building-out section runner, this minimum throttling cross section is realized maximum damping function under the highest speed, but therefore very high error sensitivity is arranged also simultaneously, like this, the permissible error of a building-out section runner is just can be not superimposed with the permissible error of other building-out section runner.Thus, the bandwidth of outer diameter 7a (scope) just can keep less.Flow channel 5a/b just can establish very narrowly mutually and the short circuit of fluid power can not take place.When short circuit, resisting medium will be walked around valve disc 7 and be communicated with between flow channel 5a/b.Only the supporting surface (numerical value x) of valve disc 7 has been done defining on the size.Valve disc 7 is separated from each other circulating direction.
That should note also has, and this system for partition wall 23 is replenished by supporting surface 23c separately in this is implemented, and these supporting surfaces should be able to prevent the bending deflection of valve plate 7.
In Fig. 3 a and 3b again as independent component description orifice valve valve body 1a.Based on the fact that is provided with a plurality of building-out section runners 11, can be with the pressure acting surface, particularly Wai Bian dividing plate circumferential area 23d is provided with on positions far away relatively outward diametrically, so just produces the pressure acting surface of the valve plate 7 of a maximum.In this embodiment, dividing plate labyrinth system 23 also has the dividing plate segmentation 23a of arranged concentric, and they are separated from each other flow channel 5 by the dividing plate 23b that radially extends.Thus, the flow channel 5 that is used for two flow directions just can be placed in one common or be the standard pitch circle of closely putting together at least.
Claims (9)
1, orifice valve especially for oscillation damper comprises a valve body, this valve body has at least one input channel that is used for a circulating direction, this passage interconnects a upper side and a downside of orifice valve valve body, also comprise a valve plate that is positioned on the valve seat surface and can rises from valve seat surface, and the building-out section runner in access path between orifice valve upper side and downside, it is characterized in that
The cross section of this building-out section runner (11) by the inflow entrance width of flow channel (5) with at the edge of a decision valve plate profile (7a, 7b) and the average radial spacing (Y) between the inflow entrance determine.
2, by the described orifice valve of claim 1, it is characterized in that this building-out section runner (11) is arranged in the outer diameter zone of orifice valve valve body (1a), simultaneously, the outer diameter (7b) of this valve plate (7) has determined the cross section of this building-out section runner.
3,, it is characterized in that this valve plate (7) is to be arranged to the diskware of a flexible sealing and to be stretched on the inner diameter (7a) by the described orifice valve of claim 1.
4,, it is characterized in that this valve seat surface is made of a dividing plate labyrinth system (23) by the described orifice valve of claim 1, (5a 5b) is separated from each other with the flow channel of two circulating directions in this system.
5, by the described orifice valve of claim 4, it is characterized in that this dividing plate labyrinth system (23) is made of the dividing plate segmentation (23a) of arranged concentric, and dividing plate segmentation (23a) has the dividing plate segmentation (23b) of radially extending so that separate the flow channel relevant with direction.
6, by claim 1 and 2 described orifice valves, it is characterized in that this orifice valve (1) has a plurality of building-out section runners (11).
7, by the described orifice valve of claim 2, it is characterized in that, when circumference dividing plate (23d) next-door neighbour of the ragged edge of the exit region of the outer diameter (7b) of valve plate (7) and the opposite circulating direction of decision, there is the building-out section flow channel cross-section of maximum.
8,, it is characterized in that this dividing plate labyrinth system (23) has a radial hole (11a) as the building-out section runner by the described orifice valve of claim 7.
9,, it is characterized in that the cross section of at least two building-out section runners (11) has different numerical value mutually by the described orifice valve of claim 6.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4404835A DE4404835A1 (en) | 1994-02-16 | 1994-02-16 | Damping valve esp. for oscillation damper |
| DEP4404835.1 | 1994-02-16 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1119251A true CN1119251A (en) | 1996-03-27 |
Family
ID=6510336
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN95102047.1A Pending CN1119251A (en) | 1994-02-16 | 1995-02-16 | Damping valve used in oscillation damper |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPH07229532A (en) |
| CN (1) | CN1119251A (en) |
| BR (1) | BR9500647A (en) |
| DE (1) | DE4404835A1 (en) |
| ES (1) | ES2126426B1 (en) |
| FR (1) | FR2716247B1 (en) |
| IT (1) | IT1273499B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110273964A (en) * | 2018-03-14 | 2019-09-24 | Zf腓特烈斯哈芬股份公司 | Orifice valve for damper |
| CN112648323A (en) * | 2019-10-10 | 2021-04-13 | 采埃孚股份公司 | Throttle point device for vibration damper |
| CN112648325A (en) * | 2019-10-10 | 2021-04-13 | 采埃孚股份公司 | Throttle point device for vibration damper |
| CN113969954A (en) * | 2020-07-23 | 2022-01-25 | 蒂森克虏伯比尔斯坦有限公司 | Shock absorber valve assembly with switchable bypass |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10011168C1 (en) * | 2000-03-08 | 2001-09-06 | Mannesmann Sachs Ag | Damper valve has axial through flow ducts partly covered by valve disc, outlets, feeder opening, funnel, curved section and arm |
| DE10222054A1 (en) * | 2002-05-17 | 2003-11-27 | Volkswagen Ag | Damper valve with a defined preload and assembly method |
| DE102004034724A1 (en) * | 2004-07-17 | 2005-10-27 | Zf Friedrichshafen Ag | Damping valve for fluid flow has body with bores connected to ring channels closed by plate springs with springs for first flow direction being stronger than springs for second flow direction |
| DE102006033378A1 (en) * | 2006-07-19 | 2008-01-31 | Dr.Ing.H.C. F. Porsche Ag | Valve device i.e. non-return valve, for shock absorber of motor vehicle, has valve body completely fitted at one of contact surfaces, when valve device is closed and contact surface partially overlaps and fits at another contact surface |
| SE533996C2 (en) * | 2009-04-23 | 2011-03-22 | Oehlins Racing Ab | Pressure regulator in a shock absorber valve |
| JP5681372B2 (en) | 2010-04-02 | 2015-03-04 | カヤバ工業株式会社 | Attenuator structure |
| JP5798842B2 (en) * | 2011-09-02 | 2015-10-21 | カヤバ工業株式会社 | Shock absorber |
| EP3212958B1 (en) * | 2014-10-27 | 2019-09-04 | ThyssenKrupp Bilstein GmbH | Method for operating a controllable shock absorber for motor vehicles |
| DE102018112458A1 (en) * | 2018-05-24 | 2019-11-28 | Stabilus Gmbh | Method of making a piston and piston |
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| US2467098A (en) * | 1945-12-13 | 1949-04-12 | Gen Motors Corp | Piston for hydraulic shock absorbers |
| FR65878E (en) * | 1953-04-16 | 1956-03-22 | ||
| FR1185696A (en) * | 1957-11-04 | 1959-08-04 | Damper piston | |
| US3078965A (en) * | 1959-11-18 | 1963-02-26 | Bourcier Carbon Previnquieres | Shock absorbers |
| DE1138594B (en) * | 1960-04-07 | 1962-10-25 | Christian Marie Lucien Louis B | Spring disc valve, especially for shock absorbers |
| DE1112348B (en) * | 1960-06-18 | 1961-08-03 | Fichtel & Sachs Ag | Piston or shut-off plate for vibration damper |
| DE1183384B (en) * | 1961-02-13 | 1964-12-10 | Boge Gmbh | Single tube telescopic vibration damper, especially for motor vehicles |
| NL291950A (en) * | 1962-04-26 | 1900-01-01 | ||
| DE1142471B (en) * | 1962-06-27 | 1963-01-17 | Boge Gmbh | Pistons for hydraulic telescopic vibration dampers, especially of motor vehicles |
| DE1575232B1 (en) * | 1967-01-27 | 1970-01-02 | Peddinghaus Dr Carl Ullrich | Shock-absorber butt |
| FR2061905A5 (en) * | 1969-10-01 | 1971-06-25 | Allinquant Fernand | |
| DE2500826C2 (en) * | 1975-01-10 | 1983-03-24 | Volkswagenwerk Ag, 3180 Wolfsburg | Valve arrangement for a telescopic vibration damper for the wheel suspension of motor vehicles |
| DE2424040C3 (en) * | 1974-05-17 | 1981-07-30 | Boge Gmbh, 5208 Eitorf | Vibration damper pistons, in particular for motor vehicles |
| FR2312925A7 (en) * | 1975-05-07 | 1976-12-24 | Allinquant Fernand | Shock absorber for road vehicle - has piston with twelve axial bores covered by disc springs |
| DE7529323U (en) * | 1975-09-17 | 1976-02-12 | Boge Gmbh, 5208 Eitorf | Working piston of a hydraulic telescopic vibration damper, in particular for wheel suspensions of motor vehicles |
| DE8301451U1 (en) * | 1983-01-20 | 1983-07-14 | August Bilstein Gmbh & Co Kg, 5828 Ennepetal, De | |
| JPS59194143A (en) * | 1983-04-18 | 1984-11-02 | Showa Mfg Co Ltd | Piston structure for hydraulic damper |
| JPS60132143A (en) * | 1983-12-21 | 1985-07-15 | Kayaba Ind Co Ltd | Piston part of hydraulic shock absorber |
| DE3701557A1 (en) * | 1987-01-21 | 1988-08-04 | Bilstein August Gmbh Co Kg | SHOCK ABSORBER PISTON, ESPECIALLY FOR MOTOR VEHICLE PIPE SHOCK ABSORBER |
| ES1003062Y (en) * | 1987-08-03 | 1989-02-16 | La Industrial Plastica Y Metalurgica, S.A. | NEW PISTON FOR SHOCK ABSORBERS |
| JPH01288643A (en) * | 1988-05-13 | 1989-11-20 | Tokico Ltd | Oil pressure shock absorber |
| JPH0292154U (en) * | 1989-01-10 | 1990-07-23 | ||
| FR2693524B1 (en) * | 1992-07-10 | 1994-12-23 | Carbon Ste Fse Amortisseurs | Piston with improved floating valve for hydraulic shock absorber, in particular the pressurized monotube type. |
| ES2115429B1 (en) * | 1993-05-10 | 1999-02-16 | Fichtel & Sachs Ag | VALVE FOR A HYDRAULIC TELESCOPIC VIBRATION DAMPER. |
-
1994
- 1994-02-16 DE DE4404835A patent/DE4404835A1/en not_active Ceased
-
1995
- 1995-01-24 ES ES009500118A patent/ES2126426B1/en not_active Expired - Lifetime
- 1995-02-06 IT ITMI950194A patent/IT1273499B/en active IP Right Grant
- 1995-02-07 JP JP7041387A patent/JPH07229532A/en active Pending
- 1995-02-15 BR BR9500647A patent/BR9500647A/en not_active Application Discontinuation
- 1995-02-16 CN CN95102047.1A patent/CN1119251A/en active Pending
- 1995-02-16 FR FR9501766A patent/FR2716247B1/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110273964A (en) * | 2018-03-14 | 2019-09-24 | Zf腓特烈斯哈芬股份公司 | Orifice valve for damper |
| CN110273964B (en) * | 2018-03-14 | 2022-07-29 | Zf腓特烈斯哈芬股份公司 | Damping valve for shock absorber |
| CN112648323A (en) * | 2019-10-10 | 2021-04-13 | 采埃孚股份公司 | Throttle point device for vibration damper |
| CN112648325A (en) * | 2019-10-10 | 2021-04-13 | 采埃孚股份公司 | Throttle point device for vibration damper |
| CN112648323B (en) * | 2019-10-10 | 2024-04-05 | 采埃孚股份公司 | Throttle point device for vibration damper |
| CN113969954A (en) * | 2020-07-23 | 2022-01-25 | 蒂森克虏伯比尔斯坦有限公司 | Shock absorber valve assembly with switchable bypass |
Also Published As
| Publication number | Publication date |
|---|---|
| ITMI950194A0 (en) | 1995-02-06 |
| FR2716247B1 (en) | 1997-03-28 |
| ES2126426B1 (en) | 1999-11-16 |
| ITMI950194A1 (en) | 1996-08-06 |
| DE4404835A1 (en) | 1995-08-17 |
| ES2126426A1 (en) | 1999-03-16 |
| FR2716247A1 (en) | 1995-08-18 |
| JPH07229532A (en) | 1995-08-29 |
| IT1273499B (en) | 1997-07-08 |
| BR9500647A (en) | 1995-10-24 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |