EP0233500A1 - Actionneur entraîné par fluide sous pression - Google Patents

Actionneur entraîné par fluide sous pression Download PDF

Info

Publication number
EP0233500A1
EP0233500A1 EP87100823A EP87100823A EP0233500A1 EP 0233500 A1 EP0233500 A1 EP 0233500A1 EP 87100823 A EP87100823 A EP 87100823A EP 87100823 A EP87100823 A EP 87100823A EP 0233500 A1 EP0233500 A1 EP 0233500A1
Authority
EP
European Patent Office
Prior art keywords
bellows
housing part
actuating device
housing
recess
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
Application number
EP87100823A
Other languages
German (de)
English (en)
Other versions
EP0233500B1 (fr
Inventor
Peter Stenzel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT87100823T priority Critical patent/ATE55454T1/de
Publication of EP0233500A1 publication Critical patent/EP0233500A1/fr
Application granted granted Critical
Publication of EP0233500B1 publication Critical patent/EP0233500B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/10—Characterised by the construction of the motor unit the motor being of diaphragm type

Definitions

  • the invention relates to an actuating device working with a pressure medium, with a rubber-elastic, preferably rotationally symmetrical bellows, which is arranged with its axial end faces between two housing parts in a medium-tight manner, and a guide element which passes axially through the interior of the bellows and is firmly connected to the first housing part and is mounted on the second housing part in a guide enabling an axial relative movement between this housing part and the guide element.
  • Such actuators can be divided into three groups.
  • the first type of these actuating devices include compressed air cylinders, e.g. according to DIN 24 335, which essentially consist of a pressure-tight housing, a piston guided therein and a piston rod connected to the piston or two piston rods, one on each piston side, with associated seals and bearings for the piston rod in the housing.
  • compressed air cylinders are used on a large scale because they enable the machine element controlled with them to be actuated precisely and reliably over a long operating time. Nevertheless, they have two basic disadvantages.
  • One disadvantage is the required guiding accuracy between the pressure housing on the one hand and the piston on the other hand and the piston rod or piston rods on the one hand and the associated housing-side bearing on the other hand.
  • the second group of hydraulic or pneumatic actuators includes membrane cylinders.
  • the diaphragm which is either clamped or lies loosely on a piston, has taken over the sealing function of the piston seal on the housing cylinder wall, which eliminates a problematic pair of fits compared to the compressed air cylinders.
  • a rigid cylinder housing is present.
  • the necessary two-part design of this housing for clamping the membrane also has a negative effect.
  • the operating pressure and the achievable stroke are limited in this type of actuators.
  • the third category of relevant actuators relates to bellows cylinders.
  • the pressure space for the pressure medium is essentially limited by a rotationally symmetrical bellows, which is designed to be retractable and retractable by means of corresponding folds in the direction of the axis of rotation.
  • Bellows cylinders of this type measured on the two types of actuators discussed above, have a low installation height, a low weight, a large force development and fewer moving parts.
  • they have a decisive disadvantage.
  • An actuating device equipped with a bellows of the type assumed at the outset is the subject of DE-OS 30 32 638.
  • This known actuating device is primarily designed as a lifter for developing relevant tractive force; but it is also intended to be used as a servo cylinder.
  • the known actuating device consists essentially of a rotationally symmetrical bellows, which is arranged with its axial end faces between two housing parts, and a guide element which extends axially inside the bellows. While one end of the axial guide element is firmly connected to the first housing part, its second end passes through a central opening in the second housing part with play.
  • a second bellows is provided, which is smaller than the first and is rotationally symmetrical and is also axially penetrated by the guide element.
  • this bellows is out of funds Opening attached tightly to the second housing part, while on the other hand it is closed by a plate.
  • the two bellows themselves are in communicating connection through the gap between the central opening of the second housing part and the guide element. A seal between the plate and the guide element with respect to the pressure space of the two bellows is achieved in that the plate is welded to the guide element.
  • This known actuating device also has disadvantages.
  • a disadvantage is that the second bellows acts counter to the first, so that the usable pressure area of the first bellows is reduced by the cross-sectional area of the second bellows.
  • the length of the device is increased by the length of the second bellows.
  • the second, ie smaller bellows is arranged outside the first, larger bellows and the two bellows have to be adjusted in terms of stroke so that the working stroke can be driven by both bellows. It is therefore practically twice the installation length compared to commercially available bellows cylinders. Also in the embodiments shown in FIGS.
  • the useful stroke must be present twice, ie similar to that of the standard and membrane cylinders. Since the useful stroke of a bellows cylinder with a small diameter is naturally smaller than that of a larger one, the small, i.e. second bellows, is decisive for the stroke, i.e.
  • the largest usable stroke length for the larger bellows must be a larger overall length (initial length) for the smaller bellows be bought. This results in the already discussed, compared to commercially available bellows cylinders with the same stroke even longer basic length (minimum output length) in these designs according to DE-OS 30 32 638.
  • the minimum overall length is predetermined by the fixed dimension between the first housing part of the first bellows and the opposite end plate of the second bellows and the minimum length of this second bellows.
  • the object of the invention is to provide an actuating device of the type assumed at the outset, in which the advantages of bellows cylinders with which the standard cylinder or the membrane cylinder are combined as far as possible are emphasized.
  • a sliding or rolling guide is provided between the second housing part and the guide element in order to achieve internal guidance of the two housing parts and is designed to be medium-tight.
  • the actuating device according to the invention combines the advantages of a bellows construction on the one hand and the standard cylinder or membrane cylinder on the other hand, but avoiding their design-specific disadvantages. It is namely short and lightweight for a given stroke, since the length of the construction is primarily determined only by the stroke length and the length of the guide between the second housing part and the guide element and the pressure space is essentially limited by the bellows.
  • the actuating device according to the invention builds in proportion the smaller the longer the useful stroke becomes. It is also characterized by an exact guidance between the stationary and the moving Lich housing part, so that it can be used without further measures to actuate machine elements to be guided exactly.
  • the piston and the associated guides or bearings can be omitted in the arrangement according to the invention.
  • the actuating device according to the invention is characterized by a simple structure, since both the guide element with the housing part with which it is firmly connected and the guide for the guide element with the second housing part can each be formed in one piece. Overall, there are considerable advantages in terms of space requirements, the use of materials and the costs.
  • An advantageous embodiment of the invention consists in that the guide element is a bolt with a circular cross-section, and the guide between the guide element and the second housing part is designed as a slide or roller bearing arranged in this, which is provided at least on the pressure chamber side with a sealing element. Standard components can thus be used, thereby further reducing the cost of the actuating device according to the invention.
  • the guide pin prefferent for the guide pin to be hollow.
  • the guide between the guide element and the second housing part lies within the interior space defined by the bellows.
  • a housing element is provided in the interior of the bellows, which reduces the dead volume of the bellows, whereby serious energy savings, especially in short strokes compared to known bellows cylinders, are achieved will.
  • This housing element can either be a separate one or it can also be formed by the second housing part, which for this purpose is drawn into the interior of the bellows in such a way that the dead volume of the bellows is also reduced.
  • a further embodiment of the invention consists in that at least one damping element acting between the two housing parts is arranged in the interior of the bellows, which is preferably represented by an industrial shock absorber (FIG. 4a).
  • a particularly expedient embodiment of an actuating device according to the invention, which is double-acting, results from the fact that the reset device is also represented by a bellows construction.
  • the two housing parts of the bellows are rotatably guided to one another. In this way, even in cases where a torque is exerted on one of the housing parts of the actuating device, an exact guidance of the machine element to be actuated is ensured and, moreover, a damaging twisting of the bellows about its axis is prevented.
  • a further exemplary embodiment of the invention consists in that instead of or in addition to a longitudinal guide arranged in the center of the device, several longitudinal guides with a diameter on the periphery of the housing parts but penetrating the bellows are provided.
  • Such an arrangement offers particular advantages if the load or force attack occurs off-center on the movable housing part.
  • an anti-rotation lock of the housing parts is automatically connected to one another.
  • the central area in the middle of the device is free (if necessary) for the central arrangement of a shock absorber, which therefore no longer has to be arranged in pairs or symmetrically to several.
  • the arrangement of a compression spring for the bellows return can also advantageously be carried out in the center.
  • a rotationally symmetrical bellows l which, as can be seen from FIG. 1, can either be folded only once or, as can be seen in the other figures, can be folded several times.
  • the axial faces of the bellows are medium-tight, i.e. compressed air tight, between two e.g. arranged in cross section circular housing parts 2 and 3.
  • the housing part 2 can be the part of the actuating device that is to be installed in a stationary manner, while the housing part 3 can be the actuating part that can be moved relative to it and that can be connected directly or indirectly to the machine element to be moved.
  • the medium-tight connection of the axial end faces of the bellows l to the housing parts 2 and 3 can be achieved in that the end flanges la of the bellows l are clamped by clamping rings 4 provided on the respective housing part 2, which are connected to the respective housing part 2 or 3 by means of screws 5 are screwed.
  • This guide element 6 is guided in a slide bearing 9, which is formed coaxially on the housing part 2, preferably in one piece.
  • a housing element in the form of a disk 11 is arranged in the pressure chamber 7 itself and is displaceably or fixedly mounted on the guide element 6.
  • the disk 11 reduces the dead volume of the pressure chamber 7 in the manner already discussed.
  • a stop disk l2 preferably with screws l3 is fastened to the guide element 6 and comes to rest on the axial end face of the bearing housing 8 at the end of the stroke via an intermediate damping element l4.
  • the housing part 3 is reset to the starting position shown in FIG. 1 by releasing the pressure chamber 7 by means of a compression spring l5, which is clamped between shoulders on the stop disk l2 and the bearing housing 8 (single-acting version with integrated reset).
  • the embodiment according to FIG. 2 differs from that according to FIG. 1 in that the bellows 1 is folded several times and the disk 11 to reduce the dead volume of the pressure chamber 7 has a greater axial height than the disk 11 in accordance with the larger initial length of the bellows 1 according to Fig. l. Furthermore, a mounting plate l6 is indicated on the the stationary housing part 2 is stored and fastened by means not shown.
  • FIG. 4 is supplemented by the fact that a reset mechanism working with pressure medium is provided.
  • This also consists of a bellows 40, one axial end face of which, with respect to the pressure chamber 7, the outer end face of the housing part 2 is connected by a clamping ring 4l, which is screwed to the housing part 2, 4 by screws 42, while the other is axial Front side is connected to an end plate 43, and expediently also by means of a clamping ring 4l with screws 42.
  • the end plate 43 is either axially adjustable with respect to the guide element 6, as shown on the left in FIG.
  • the pressure chamber 7 of the bellows 1 is filled with pressure medium during the working stroke, while the pressure chamber 7 is emptied for the return stroke and the pressure chamber 47 is pressurized with the pressure medium.
  • Fig. 4a the arrangement of Fig. 4 is further developed in that in the interior of the bellows in the housing part 2 e.g. Two diametrically opposed industrial shock absorbers l8 / 4 are arranged, which interact with the movable housing part 2 and thus ensure smooth travel to the end positions.
  • longitudinal guides 6 which run in slide or roller bearings 9, which in turn are equipped with seals l0.
  • a shock absorber 18 can then be arranged centrally for damping.
  • FIGS. 6 to 9 show an embodiment of an actuating device according to the invention, in which end position damping is provided.
  • the bearing housing 8 is arranged penetrating the interior or pressure chamber 7 of the bellows 1. 6, which shows the one end position of the actuating device, the bearing housing 8 engages in a recess 3a (FIG. 7) of the first housing part 3, a space 7.1 for pressure medium remaining in the recess 3a above the upper end of the bearing housing.
  • This space 7.1 increases when the relative movement between the housing parts is removed.
  • the bearing housing 8 comes out of the recess 3a of the first housing part 3 when pressure medium is introduced into the bellows 1.
  • the bearing housing 8 engages in the recess 3a of the first housing part 3 in such a way that a gap is formed between the bearing housing 8 and the first housing part, which gap is designated by 26 in FIGS. 6 and 8.
  • a so-called damping ring 51 is arranged in a recess in the wall of the housing part recess 3a.
  • This damping ring 51 has a sealing surface 55 which engages with the outer surface of the bearing housing 8 and which represents the radially inner surface of the damping ring 51.
  • the lower axial end face 54 according to FIG. 8 is also designed as a sealing surface which can come into sealing engagement with the opposite groove wall.
  • the actuating device according to FIGS. 6 to 9 has a first or lower pressure medium supply 17.1, 20.1, 21, through which a pressure medium connection with the space 7 of the bellows 1 is created.
  • a plurality of vertical pressure medium supply channels 21 are provided. At least one of these channels 21 is connected via a bore 22 to a channel 24 which extends along the length of the bearing housing 8 and opens into the space 7.1 of the housing part recess 3a on its upper surface.
  • An adjustable throttle device 23, 25 is provided between the bore 22 and the channel 24, as can be seen in particular from FIG. 9. This figure shows a throttle screw 25, by means of which the throttle opening between the channels 22 and 24 can be changed in size.
  • the actuating device according to FIGS. 6 to 9 also has a second upper pressure medium supply 17.2, 20.2, which is connected to the space 7.1 of the housing part recess 3a.
  • the upper ring flange of the space 7.1 is first filled when the pressure medium is supplied. At the same time, the medium flows through the gap 26 to the damping ring 51, which moves into its axially lower sealing position, so that no pressure medium can flow around the damping ring 51 into the interior 7 of the bellows 1. At the same time, further pressure medium flows through the channel 24, the bore 22 and the channel 21 throttled into the interior 7 of the bellows 1, because in this mode of operation the pressure medium supply 17.1 is closed. The entire effective area of the bellows cylinder is thus acted upon and the extension stroke is carried out.
  • the pressure medium supply 17.2 becomes depressurized, and the pressure medium flows out through the pressure medium supply 17.2 during the retracting movement.
  • the damping ring 51 sits with its axially upper grooved end face 54 against the opposite groove wall, so that when there is a sealing engagement between the damping ring 51 and the outer surface of the bearing housing 8, the medium from the reducing pressure space 7 around the ring or through the channels 21, 22 , Throttle opening 23 and channel 24 can flow into the pressure chamber 7.1.
  • This mounting position of the damping ring results in weaker damping. A stronger damping of the retraction stroke movement with the medium connection at 17.2 results if the damping ring with its axial sealing surface points upwards.
  • the pressure medium in the interior 7 of the bellows 1 can now only escape via the channels 21 and 22, the throttle opening 23 and the channel 24 into the room or pressure chamber 7.1 and from there through the pressure medium supply 17.2.
  • the bearing housing 8 moves into the housing part recess 3a with greater damping.
  • two channels 24 are provided, each of which is connected to a pressure medium supply via an adjustable throttle.
  • a check valve can be arranged in each channel 24, which blocks one channel 24 in one direction and the other channel 24 in the opposite direction. This enables separate adjustment of the extension stroke damping and the insertion stroke damping.
  • the grooved damping ring is expediently replaced by a sealing ring that seals on both sides.
  • FIGS. 10 and 11 show a further embodiment of an actuating device according to the invention, in which the force-travel characteristic can be changed.
  • Bellows or bellows cylinders have the property of developing the greatest force at the beginning of their stroke. In a mostly non-linear degressive characteristic, the force drops to values between 75% and 50% of the initial lifting force up to the end of the stroke. This characteristic is caused by the initially large effective area when the bellows is folded, which the pressure medium strikes. With increasing expansion of the bellows, its diameter and thus the effective area decrease.
  • the bearing housing 8 is stepped on the circumference, and the recess 3b of the first housing part receiving the bearing housing 8 has a corresponding stepped design.
  • a damping ring 51.1 or 51.2 which is of the same general type as was described in connection with FIGS. 6 to 9. The number of levels can be changed depending on the desired effect.
  • the damping rings 51 are installed in such a way that the axially upper end face 54 is formed as a sealing surface and accordingly effects a seal when it engages with the opposite groove wall.
  • the radially outer surface and the lower axial end surface are provided with through-flow grooves 53 and 54, respectively, while the radially inner surface 55 is again designed as a sealing surface.
  • the pressure medium is supplied via the feed 17.1.
  • the medium flows through the channels 20.1 and 21 into the lower pressure chamber 7, which is the interior of the bellows 1.
  • the first housing part 3, guided by the guide element 6, starts to move axially and extends accordingly.
  • a vacuum is created in the upper pressure chamber 7.1, through which the check valve 60 is opened, so that when air is used as the pressure medium, a pressure equalization with the surroundings takes place. If a hydraulic fluid is used as the pressure medium, a pressure-free medium connection with a check valve must be provided at 17.2.
  • the effective area is no longer the entire cylindrical area of the bellows 1, but the ring area defined by the diameters D1 and D2.
  • the initial pressure over the first part of the travel path S1 can correspond to the final pressure, but can also be greater or less than the final pressure, since if D1 is assumed to be a fixed output variable, D2 can be designed as required.
  • the effective diameter D1 decreases during the travel path S1, so that the effective area also becomes smaller because the diameter D2 is specified as a fixed size.
  • the force loss typical of the bellows cylinder can during its stroke by increasing the effective area by a further ring area defined by the diameters D2 and D3, so that the falling force-displacement curve receives a positive thrust. Since the travel path S2 is greater than the travel path S1, the whole thing is repeated once again, that is to say the further decreasing diameter D1 and thus the pressure area, a further pressure area is added as compensation, in this example the ring area, defined by the diameters D3 and D4 .
  • the cylinder now has the same force-displacement characteristics over the rest of its path as an unguided bellows cylinder, but the dimensioning can also be laid out in such a way that the stroke ends when the total pressure area is reached.
  • the retracting stroke takes place under the action of external forces.
  • the check valve 60 closes and the pressure medium escapes from the pressure spaces 7 and 7.1 through the channels 21 and 20.1.
  • a separation into the upper pressure chamber 7.1 and the lower pressure chamber 7 again occurs.
  • the external return forces exert a pressure on the pressure medium enclosed in the upper pressure chamber 7.1.
  • the damping rings 51.1 and 51.2 are brought into their lower axial position, so that the pressure medium around the rings 51.1 and 51.2 and through the column 26 into the lower pressure chamber 7 and thus to the unpressurized pressure medium supply 17.1 and thus can flow away.
  • the undesirable ones high initial forces is reduced, which, among other things, extends the application of an actuating device according to the invention.
  • No complex medium transfer pressure control is required in order to obtain an approximately linear force-displacement characteristic, as is present in piston cylinders, in an actuating device according to the invention.
  • Fig. 11 shows a modified embodiment, in which the falling course of the force during the stroke is counteracted by the fact that the outer surface of the bearing housing 8 and the corresponding inner surface of the housing part recess 3b are each formed in the shape of a truncated parabola in such a way that the loss of the active surface through the of the stroke-reducing effective diameter is compensated for at every point of the stroke by the parabolic stump tapering upwards.
  • an exemplary seal 61 which adapts to the increasing width of the gap 26 and bridges it.
  • a greatly reduced initial force results if the check valve 60 is installed in the medium supply 17.1 and the medium is supplied at 17.2. Then, when the damping rings 51.1 and 51.2 are arranged or installed in reverse to the arrangement shown in FIG. 10, the active surface between the diameters D3 and D4 (FIG. 10) is first applied. The extension stroke then begins with a low initial force, which increases gradually when S1 is greater than S2. In the case of the embodiment according to FIG. 11 with a truncated parabolic bearing housing 8, there is a stepless enlargement until the bearing housing 8 leaves the damping ring or the damping rings or the sealing ring 61, which also has to be installed vice versa.
  • a throttle check valve can also be provided. A corresponding adjustment of the throttle causes a gentle start of the extension stroke by only slowly compensating the negative pressure.
  • bearing housing 8 and the associated housing part recess 3b are formed in the shape of a truncated parabola, a corresponding frustoconical shape could also be provided.
  • the damping rings 51.1 and 51.2 are each arranged in a groove which is formed in the wall of the recess 3b.
  • the damping rings are each arranged in a groove in the bearing housing.
  • the damping ring has a movable sealing lip instead of the axial and radial flow grooves, which blocks the passage of the medium in one direction and releases it in the other direction, so that a non-return function is obtained.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Diaphragms And Bellows (AREA)
  • Actuator (AREA)
  • Sowing (AREA)
  • Vending Machines For Individual Products (AREA)
EP87100823A 1986-01-22 1987-01-22 Actionneur entraîné par fluide sous pression Expired - Lifetime EP0233500B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87100823T ATE55454T1 (de) 1986-01-22 1987-01-22 Mit einem druckmedium arbeitende betaetigungsvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863601822 DE3601822A1 (de) 1986-01-22 1986-01-22 Mit einem druckmedium arbeitende betaetigungsvorrichtung
DE3601822 1986-01-22

Publications (2)

Publication Number Publication Date
EP0233500A1 true EP0233500A1 (fr) 1987-08-26
EP0233500B1 EP0233500B1 (fr) 1990-08-08

Family

ID=6292375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87100823A Expired - Lifetime EP0233500B1 (fr) 1986-01-22 1987-01-22 Actionneur entraîné par fluide sous pression

Country Status (3)

Country Link
EP (1) EP0233500B1 (fr)
AT (1) ATE55454T1 (fr)
DE (2) DE3601822A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0470025A1 (fr) * 1990-07-31 1992-02-05 Lohr Industrie Ensemble de manoeuvre à soufflet
DE4108312A1 (de) * 1991-03-14 1992-09-24 Ivan Ivanov Betaetigungsvorrichtung
WO2016016586A1 (fr) 2014-08-01 2016-02-04 Laboratoire Francais Du Fractionnement Et Des Biotechnologies Procédé de production de variants ayant un fc présentant une sialylation améliorée
WO2018078138A1 (fr) 2016-10-28 2018-05-03 Laboratoire Français Du Fractionnement Et Des Biotechnologies Variants de polypeptide fc presentant une demi-vie augmentee

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1459892A (en) * 1922-04-06 1923-06-26 James G Hughes Pneumatic spring
DE1860309U (de) * 1962-07-04 1962-10-18 Osmond Beissbarth O H G Fabrik Pnuematischer wagenheber.
DE2336211B2 (de) * 1973-07-17 1978-10-26 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Einfach wirkender pneumatischer Arbeitszylinder
DE2355593B2 (de) * 1973-11-07 1978-12-14 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Arbeitszylinder zum Ausführen einer jeweils im Bereich der Endlagen gedämpften Arbeitskolbenbewegung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CS204779B1 (en) * 1979-08-30 1981-04-30 Zdenek Pustka Universal pneumatic wool lifter

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1459892A (en) * 1922-04-06 1923-06-26 James G Hughes Pneumatic spring
DE1860309U (de) * 1962-07-04 1962-10-18 Osmond Beissbarth O H G Fabrik Pnuematischer wagenheber.
DE2336211B2 (de) * 1973-07-17 1978-10-26 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Einfach wirkender pneumatischer Arbeitszylinder
DE2355593B2 (de) * 1973-11-07 1978-12-14 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Arbeitszylinder zum Ausführen einer jeweils im Bereich der Endlagen gedämpften Arbeitskolbenbewegung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0470025A1 (fr) * 1990-07-31 1992-02-05 Lohr Industrie Ensemble de manoeuvre à soufflet
FR2665490A1 (fr) * 1990-07-31 1992-02-07 Lohr Ind Ensemble de manóoeuvre a soufflet.
DE4108312A1 (de) * 1991-03-14 1992-09-24 Ivan Ivanov Betaetigungsvorrichtung
WO2016016586A1 (fr) 2014-08-01 2016-02-04 Laboratoire Francais Du Fractionnement Et Des Biotechnologies Procédé de production de variants ayant un fc présentant une sialylation améliorée
WO2018078138A1 (fr) 2016-10-28 2018-05-03 Laboratoire Français Du Fractionnement Et Des Biotechnologies Variants de polypeptide fc presentant une demi-vie augmentee

Also Published As

Publication number Publication date
DE3601822A1 (de) 1987-07-23
ATE55454T1 (de) 1990-08-15
EP0233500B1 (fr) 1990-08-08
DE3764107D1 (de) 1990-09-13

Similar Documents

Publication Publication Date Title
DE4019221C2 (de) Stoßdämpfer mit variabler Dämpfungskraft
DE3434033C2 (fr)
EP0364757B1 (fr) Amortisseur de chocs pour l'amortissement de mouvements
DE2410541C3 (de) Umschaltventil
EP0318816A2 (fr) Amortisseur hydraulique de chocs et de vibrations à amortissement réglable
DE3114437A1 (de) Druckregelventil
DE3019119A1 (de) Pneumatischer antrieb fuer schalt- und stellglieder
DE4320446A1 (de) Stoßdämpfer
DE2335564A1 (de) Hydraulische bremsanlage fuer kraftfahrzeuge
DE2431135C3 (de) Mehrwegeventil
EP0233500B1 (fr) Actionneur entraîné par fluide sous pression
EP0513673A2 (fr) Soupape à ouverture ou fermeture rapide
DE3819817C1 (fr)
EP0341597A2 (fr) Amortisseurs de chocs à caractéristique d'amortissement variable
EP0505349B2 (fr) Vérin hydraulique
DE3931240C2 (de) Stoßdämpfungseinrichtung mit veränderlicher Dämpfungscharakteristik, insbesondere für Kraftfahrzeuge
EP0617202B1 (fr) Dispositif amortisseur de fin de course pour un système mobile
EP0089568B1 (fr) Dispositif d'actionnement rotatif à fluide sous pression
EP0388635B1 (fr) Dispositif de commande électrohydraulique
DE19709593A1 (de) Vorrichtung zur Verzögerung einer bewegten Masse
DE2506451C2 (de) Stufenlos verstellbarer Stoßdämpfer, insbesondere für industrielle Anwendungszwecke
EP1225343A1 (fr) Dispositif d'entrainement par vérin à pression fluidique
DE4413512A1 (de) Kolbenstangenloser Druckmittelzylinder
DE2355541A1 (de) Ventileinrichtung zur steuerung von druckmittelbetaetigten bremsen, insbesondere fuer schienenfahrzeuge
DE2419118C2 (fr)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE ES FR GB GR IT LI LU NL SE

17P Request for examination filed

Effective date: 19871229

17Q First examination report despatched

Effective date: 19881103

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE ES FR GB GR IT LI LU NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

Effective date: 19900808

Ref country code: FR

Effective date: 19900808

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19900808

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19900808

Ref country code: GB

Effective date: 19900808

Ref country code: NL

Effective date: 19900808

Ref country code: BE

Effective date: 19900808

REF Corresponds to:

Ref document number: 55454

Country of ref document: AT

Date of ref document: 19900815

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3764107

Country of ref document: DE

Date of ref document: 19900913

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19901119

EN Fr: translation not filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19910131

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19940125

Year of fee payment: 8

Ref country code: CH

Payment date: 19940125

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19950122

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Effective date: 19950131

Ref country code: LI

Effective date: 19950131

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20000309

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011101