WO2006029421A1 - Amortisseur fluidique - Google Patents

Amortisseur fluidique Download PDF

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Publication number
WO2006029421A1
WO2006029421A1 PCT/AT2005/000037 AT2005000037W WO2006029421A1 WO 2006029421 A1 WO2006029421 A1 WO 2006029421A1 AT 2005000037 W AT2005000037 W AT 2005000037W WO 2006029421 A1 WO2006029421 A1 WO 2006029421A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid damper
piston
opening
damper according
overload
Prior art date
Application number
PCT/AT2005/000037
Other languages
German (de)
English (en)
Inventor
Marco Rücker
Claus HÄMMERLE
Original Assignee
Julius Blum Gmbh
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 Julius Blum Gmbh filed Critical Julius Blum Gmbh
Priority to DE202005020820U priority Critical patent/DE202005020820U1/de
Publication of WO2006029421A1 publication Critical patent/WO2006029421A1/fr

Links

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
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • 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
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F16F9/0209—Telescopic
    • F16F9/0218—Mono-tubular units
    • 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
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
    • 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
    • F16F9/3415—Special valve constructions; Shape or construction of throttling passages characterised by comprising plastics, elastomeric or porous elements
    • 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
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
    • F16F9/5126—Piston, or piston-like valve elements
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F5/00—Braking devices, e.g. checks; Stops; Buffers
    • E05F5/006—Braking devices, e.g. checks; Stops; Buffers for hinges having a cup-shaped fixing part, e.g. for attachment to cabinets or furniture
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/21—Brakes
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/252—Type of friction
    • E05Y2201/254—Fluid or viscous friction
    • E05Y2201/256—Fluid or viscous friction with pistons or vanes
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/262—Type of motion, e.g. braking
    • E05Y2201/264—Type of motion, e.g. braking linear
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/20—Application of doors, windows, wings or fittings thereof for furniture, e.g. cabinets

Definitions

  • the present invention relates to a fluid damper, in particular for movable furniture parts, with a guided in a cylinder relative to the cylinder displaceable piston, wherein in the piston and / or between the piston and cylinder at least one through-flow for fluid flowing through is provided.
  • Fluid dampers are known in the prior art in a variety of forms and applications. Among other things, they are used in conjunction with moving furniture parts. Thus, with corresponding fluid dampers, e.g. the closing movement of furniture doors are damped, whereby a loud slamming and possible damage to the doors are prevented.
  • the damping effect of the fluid damper is based essentially on the flow resistance of a fluid present in the cylinder. When pressure is applied to the piston, the latter is displaced relative to the cylinder, the fluid flowing through flow passages through the piston or between the piston and cylinder from one cylinder chamber to another. Instead of or in addition to the damping effect by means of flow resistance, an energy reduction by friction can also be provided.
  • Object of the present invention is to improve a fluid damper to the effect that the described damper bounce is effectively prevented in case of overload.
  • the fluid dampers according to the invention are preferably designed as linear dampers.
  • the inventive type of protection against overload in fluid dampers can be used particularly favorably, the damping effect of which is based essentially on the flow resistance of the fluid.
  • the fluids include both gases, e.g. Air, as well as liquids or hydraulic fluids, such. oils, in question.
  • Preferred embodiments provide for the use of the fluid damper according to the invention in movable furniture parts such as doors, drawer inserts or hinges, in particular furniture hinges.
  • Figs. 1 to 3 a first embodiment according to the invention
  • Figs. 2a and 3a detailed views of Figs. 2 and 3
  • Figs. 4 and 5 are plan views of the piston of the first embodiment from the direction
  • FIG. 11 is a schematic representation of the sequence of the closing movement of a furniture door with fluid damper according to the invention
  • FIGS. 12 and 12a and 12b show a third embodiment according to the invention
  • FIGS. 13 and 13a and 13b Fourth embodiment of the invention
  • Fig. 14 and Fig. 14a to 14d a fifth embodiment of the invention
  • Fig. 15 and Fig. 15a to 15d a sixth embodiment of the invention
  • FIGS. 16 to 18 a show a special shape and design of flow-through openings.
  • the absorber 7 is made of a slightly compressible material, e.g. Sponge rubber, made. It serves to balance the volume of the piston rod 5 when it is pushed in direction 23 into the cylinder 1.
  • the seals 8 and 9 can be designed in any manner known in the art. They only prevent the unwanted outflow of the fluid arranged inside the cylinder 1 and thus an undesired pressure drop.
  • a ring-shaped or tubular closure element 3 is arranged on the piston 2, in the first embodiment according to FIGS. 1 to 5, a ring-shaped or tubular closure element 3 is arranged. This is longitudinally extending and mounted on the piston 2 relative to this displaceable.
  • the closure element 3 fulfills in the present embodiment as well as in the variant according to FIGS. 6 to 9 a double function.
  • the closure element 3 opens the overload openings 10 in the event of an overload, which are arranged in the piston 2.
  • the closure element 3 is formed radially expandable. When pressurized, the closure element 3 can thereby expand in the direction of the wall of the cylinder 1, whereby the annular and disposed between the closure element 3 and the inner wall of the cylinder 1 through-flow opening 4 is reduced in cross section and thus the flow resistance of the fluid is increased.
  • FIG. 4 shows a view from direction AA on the piston 2 in the normal operating situation illustrated in FIG. 2, in which the pressurization is below the threshold value and the fluid can flow through the annular gap 4.
  • Fig. 5 shows the view of the piston 2 from direction AA in the overload situation shown in Fig. 3.
  • FIG. 3 a shows the region marked with a circle in FIG. 3 in an enlarged view.
  • fluid can flow between the closure element 3 and the wall of the cylinder 1 through the flow-through opening 4, whereby the piston 2 is displaceable within the cylinder 1.
  • the annular closure element 3 By increasing the pressurization, the annular closure element 3 is radially expanded, whereby the flow-through opening 4 is reduced in its cross-section.
  • the dimensioning of the piston 2 with the tapered from the piston exterior to the piston interior overload openings 10 and the inner diameter of the cylinder 1 as well as the wall thickness and the material properties of the closure element 3 are chosen so that upon reaching the intended application of the fluid damper threshold by increasing Elongation of the closure element 3, the overload openings 10 are opened in the region 12, so that fluid can flow through them. As a result, blocking or bouncing of the piston is prevented in the case of excessive pressurization.
  • the Matterlastsituatio ⁇ shown in Fig. 5 is shown again in Fig. 3a in a sectional view.
  • a path-dependent control of the flow resistance is realized.
  • the inner diameter of the cylinder in the region in which the piston is displaceable e.g. in the areas 11a, 11b, 11c and 11d, is different in size.
  • FIG. 1 shows the first embodiment in the situation in which the piston rod 5 substantially no pressure is exerted.
  • Fig. 1 also shows the relative position of the piston 2 and the closure element 3 in the return of the piston by means of the spring 6 counter to the direction 23. In the shown restoring situation, a relatively large gap between the closure element 3 and the piston 2 is free. This allows a good flow through the fluid and thus a quick return.
  • Fig. 2 the reduction of the cross section of the flow-through opening takes place in the transition between the regions 11b and 11c.
  • annular closure element 3 ' is not displaceable relative to the piston 2' in this embodiment, but engages in a groove 18 in the piston.
  • the closure element 3 ' is radially expandable so that the flow-through openings 4, as already described, can be controlled in their opening cross-section as a function of pressure by the closure element 3'.
  • Another pressure-dependent control of the total flow cross-section is given in this example by the interaction of the brake plate 15 with the Abdecklamelle 16.
  • Both lamellae are displaceable relative to one another and are mounted to the piston 2 'on a connecting rod 14, which connects the piston 2' to the connecting element 13.
  • the piston 2 ' is supported via said connecting rod 14 and the connecting element 13 against the spring 6, which performs the same function as in the first embodiment.
  • the pressure-dependent control takes place in this embodiment in the interaction of the slats 15 and 16 with the pressure-dependent expansion of the closure element 3 '.
  • a constant control of the braking force or damping of the fluid damper 19 for different closing forces is thereby achieved.
  • These change e.g. by aging the closure mechanisms, e.g. hinges, or vary by using different hinge types.
  • the fins 15 and 16 can be made so fine or smooth that they react to low pressures, which particularly well changes in the closing force can be compensated.
  • the closure element 3 ' is then conveniently designed so that it can respond to larger pressure changes.
  • Fig. 6 shows the second embodiment, when the piston rod 5 has been fully extended by means of the spring 6.
  • the overflow 4 'and 4 are open in this situation maximum.
  • the brake plate 17 initially lays against the piston 2 'by displacement along the connecting rod 14 and at least partially closes the flow openings 4'.
  • the brake disk 15 has at least one fin opening 17, which is arranged so that fluid can still flow through the fin opening 17 and at least part of the flow opening 4 '.
  • the covering lamella 16 is likewise displaced in the direction of the piston 2 'and deformed at the corresponding pressure, as shown in FIGS. 7, 7a, 8 and 8a.
  • the overload protection according to the invention also occurs in this exemplary embodiment by opening the overload opening 10, which in the exemplary embodiment is designed in the region of the groove 18.
  • the overload situation is shown in FIG. 9.
  • the closure element 3 ' is stretched by appropriate pressure build-up in the region of the groove 18 so far that the overload opening 10 is opened, whereby the fluid is again given a possibility to bypass the piston 2'.
  • closure member 3 1 is held by a not visible in Fig. 9 support so in its position relative to the piston 2 ', that no relative displacement between closure element 3' and piston 2 'is possible, and the closure element after completion of the overload situation back into the Groove 18 engages.
  • the closure element 3 or 3 In the first two embodiments according to FIGS. 1 to 9, the closure element 3 or 3 'fulfills a dual function. On the one hand, it controls the opening and closing of the overload opening (s) 10. On the other hand, the closure element also controls the flow cross section of the throughflow openings 4.
  • the two functionalities are separated from one another.
  • at least one overload control device 28 is provided for opening and closing the overload opening (s) 10.
  • the fluid damper 19 has a flow-through opening control element 24.
  • the overload control device 28 and the fürströmö Stammelement 24 are separate from each other - different - components of the fluid damper 19th
  • the fürströmöticianskontrollelement 24 has substantially the features of the closure element 3, 3 'of the first two embodiments, or may be formed accordingly.
  • said element 24 is stretchable, so that the passage cross-section of the flow-through 4 is reduced in size with the increase acting on the fluid damper 19 pressurization by the flow control.
  • the closure elements 3, 3 'ring-shaped or tubular and radially expandable it can also be provided that the flow-through opening control element 24 extends longitudinally and preferably has different wall thicknesses along its longitudinal extent.
  • the Element 24 also slidably mounted between a stop 27 on the piston 2 and a stop of the respective connecting element 13 in the cylinder longitudinal direction.
  • FIGS. 12 to 12 b show a first variant of an overload control device 28 separated from the flow-through opening control element 24, in which it essentially has a spring-loaded ball 25.
  • This is intended to close the overload opening 10 as long as the pressurization in the fluid is below a predefinable threshold value. If this is exceeded by the properties of the ball loading spring 26 predeterminable threshold, it comes to the deflection, preferably for compression, the spring 26, whereby the overload opening 10 is released and the fluid is opened a path through the piston 2 therethrough.
  • FIG. 12 a shows the cutout 34 from FIG. 12 in the event of an overload, in which the ball 25 releases the overload opening 10.
  • Fig. 12b shows the same detail in the normal state in which the ball 25 is acted upon by the spring 26, the overload opening 10 closes.
  • the ball 25 loading spring 26 is parallel to the direction of movement of the piston 2 displaceable in the cylinder deflectable.
  • a resilient variant of the overload control device 28 is likewise provided. However, this is deflected in the radial direction.
  • the overload control device for opening and closing the overload opening 10 on a resilient ring or a, preferably c-shaped, resilient ring segment 29 This closes in normal operation with the cap 30, the overload opening 10 in the piston 2. Only when a predetermined by the elastic properties of the ring segment 29 (or ring) predetermined threshold of pressurization, the ring segment 29 is stretched so far that the overflow 10 released and fluid can flow past and past the piston 2. This situation is shown in the section 35 in Fig. 13a. 13b indicates in an exploded view that the resilient ring segment 29 partially surrounds the piston 2, wherein the overload opening 10 is arranged in the lateral surface of the piston 2.
  • the overload control device 28 has an eccentrically expandable ring 31.
  • This is in the illustrated embodiment, as can be seen particularly well in Fig. 14b, equipped with a locking lug 32, which is intended to be anchored in the receptacle 33 of the piston 2.
  • the eccentrically stretchable ring 31 is only partially or fixed only in a small portion of the piston 2.
  • this unilateral fixation results in eccentric expansion of the ring 31. If the predefinable threshold value is exceeded, the overload opening 10 in the piston 2 shown in FIG. 14d is released by corresponding expansion, whereby fluid can once again flow past the piston 2.
  • 14c shows the same view from direction 37 on the piston 2, but in the situation in which the pressurization of the eccentrically expandable ring 31 is below the threshold and the overload opening 10 is closed by the ring 31.
  • 14a shows the detail 36 from the sectional view 14. In the situation shown here, the overflow opening 10 is closed by the eccentrically expandable ring 31.
  • FIGS. 15 to 15 d show a further exemplary embodiment according to the invention, in which the overload control device 28 has a preferably disc-shaped overload lamella 38 which has at least one elastically deformable region 39 for opening and closing overload openings 10 provided in the piston 2.
  • the region or regions 39 are partially surrounded by preferably substantially V-shaped or U-shaped recesses 41.
  • the tabs thus formed can be bent with appropriate pressurization and thus open the overload openings 10, which in turn fluid can flow through the piston 2.
  • the overload lamella 38 is mounted on the latter in an axially displaceable manner parallel to the direction of movement of the piston 2. Fig.
  • FIG. 15b shows the situation in which the overload plate 38 is removed from its stop on the piston 2.
  • Fig. 15c shows the situation in which, although it rests on the piston 2 but the overload opening 10 is not yet released.
  • the deformable portions 39 are bent after exceeding the threshold value of the pressure load and the overload opening (s) 10 is (are) released.
  • FIGS. 16 to 18 furthermore show a variant in which, for the purpose of controlling the flow cross-section, substantially groove-shaped throughflow openings extending in addition to and extending essentially parallel to the direction of movement of the piston are provided. This can be arranged both in the inner wall of the cylinder 1 facing the piston 2 and in the piston 2 and / or in the flow-through opening control element 24 or in the closure element 3, 3 '. As shown in FIGS.
  • FIG. 16a shows the cross section in the position shown in Fig. 16, in which the piston is at the beginning of the damping movement. If the piston rod 5 and thus the piston are pushed further, in the situation illustrated in FIGS. 17 and 17a there is already a change in both the groove-shaped throughflow openings 42 and the annular throughflow opening 4. In the situation illustrated in FIGS. 18 and 18a , in which the piston rod 5 is almost completely inserted into the cylinder, the annular flow openings 4 are completely closed. In this area, no groove-shaped flow openings 42 are more provided in the cylinder inner wall.
  • pressurization and elongation can by material selection and appropriate dimensioning of the closure element 3 and 3 'and
  • Overload control device 28 and the fürströmö Stammmaschines 24 can be achieved.
  • Preferred is e.g. a quadratic context in which the
  • thermoplastics and / or elastomers such as e.g. TPE's (thermoplastic elastomers).
  • TPE's thermoplastic elastomers
  • Fig. 10 shows a furniture hinge 20 as an application form on which a fluid damper 19 according to the invention is arranged. This is placed here on the hinge arm 22. The piston rod is supported on the opposite side.
  • Fig. 11 shows schematically the closing behavior of a door which is equipped with a furniture hinge with inventive fluid damper 19.
  • the phases I to IV of the closing process are differentiated.
  • phase I up to a closing angle of approx. 20 °
  • the fluid damper is not in action.
  • phase II there is a gentle first braking and interception of the door.
  • phase III the essential braking process is ensured by an interaction of the above-described pressure-dependent and path-dependent damping.
  • area IV the door speed is already slowed to almost zero. There is a gentle closing.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne un amortisseur fluidique (19) notamment destiné à des parties mobiles de meubles, comportant un piston (2, 2') pouvant coulisser dans un cylindre (1), une ouverture d'écoulement (4, 4') destinée à du fluide qui s'écoule étant prévue dans le piston (2, 2') et/ou entre le piston (2, 2') et le cylindre (1). Au-dessus d'une valeur seuil de pression exercée sur le piston fluidique (19), au moins une ouverture de délestage (10) pratiquée dans le piston (2, 2') et/ou entre le piston (2, 2') et le cylindre (1) peut être ouverte.
PCT/AT2005/000037 2004-09-17 2005-02-04 Amortisseur fluidique WO2006029421A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE202005020820U DE202005020820U1 (de) 2004-09-17 2005-02-04 Fluiddämpfer

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA1570/2004 2004-09-17
AT15702004 2004-09-17

Publications (1)

Publication Number Publication Date
WO2006029421A1 true WO2006029421A1 (fr) 2006-03-23

Family

ID=34960704

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT2005/000037 WO2006029421A1 (fr) 2004-09-17 2005-02-04 Amortisseur fluidique

Country Status (4)

Country Link
CN (1) CN201021704Y (fr)
AT (1) AT10342U1 (fr)
DE (1) DE202005020820U1 (fr)
WO (1) WO2006029421A1 (fr)

Cited By (8)

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Publication number Priority date Publication date Assignee Title
EP2114203A1 (fr) * 2007-01-31 2009-11-11 Deon AG Entraînement de meuble à moteur électrique
AT508069B1 (de) * 2009-03-25 2015-03-15 Blum Gmbh Julius Möbelscharnier
WO2015086093A1 (fr) * 2013-12-13 2015-06-18 Kesseböhmer Produktions GmbH & Co. KG Frein de sécurité pour colonne de meuble télescopique
CN105650305A (zh) * 2016-02-24 2016-06-08 北京亚泰金合机械设备有限公司 缓冲阀
AT518359A1 (de) * 2016-03-07 2017-09-15 Blum Gmbh Julius Möbeldämpfer
EP3279499A1 (fr) * 2016-08-05 2018-02-07 BeijingWest Industries Co. Ltd. Amortisseur hydraulique doté d'une bande d'usure autoréglable
AT520128A1 (de) * 2017-07-13 2019-01-15 Blum Gmbh Julius Möbeldämpfer
EP3485180B1 (fr) * 2016-07-12 2022-06-01 Stabilus GmbH Amortisseur de frein de voie

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102155514B (zh) * 2010-02-11 2012-11-07 北京世博金属制品有限公司 无级变速液体阻尼器
DE202010013462U1 (de) * 2010-09-23 2012-01-02 Grass Gmbh Vorrichtung zur Beeinflussung eines Stoßvorgangs beim Bewegen eines Möbelteils und Möbel
AT12632U1 (de) 2010-12-10 2012-09-15 Blum Gmbh Julius Dämpfvorrichtung für einen möbelbeschlag
CN103089891A (zh) * 2011-11-01 2013-05-08 成都红美金属制品有限公司 用于轿车的减振阻尼器
ES2667369T3 (es) 2012-01-25 2018-05-10 Fulterer Ag & Co Kg Dispositivo de extracción para al menos dos piezas de mueble extraíbles
AT512306B1 (de) 2012-01-25 2013-07-15 Fulterer Gmbh Vorrichtung zur dämpfung der bewegung eines beweglich gelagerten bauteils
AT512300B1 (de) 2012-01-25 2013-07-15 Fulterer Gmbh Vorrichtung zur dämpfung der bewegung eines beweglich gelagerten bauteils
AT512299B1 (de) 2012-01-25 2013-07-15 Fulterer Gmbh Einziehvorrichtung für mindestens zwei ausziehbare möbelteile
AT512415B1 (de) 2012-03-20 2013-08-15 Fulterer Gmbh Zuziehvorrichtung für ein beweglich gelagertes Möbelteil
CN103375526B (zh) * 2012-04-28 2016-02-10 中国铁路总公司 弹性装置、缓冲器及轨道车辆
CN103423364B (zh) * 2013-08-12 2015-08-05 江苏大学 一种阻尼可调的液压减振器
CN103615494A (zh) * 2013-11-29 2014-03-05 常州大学 一种用于管道减振的阻尼器
DE202014002228U1 (de) 2014-03-14 2014-05-06 Erwin Krüger Fluiddämpfer für gegeneinander verstellbare Möbelteile mit einem relativ in einem Zylinder verstellbar geführten Kolben
CN105276057B (zh) * 2014-07-04 2019-12-17 宁波裕盛家居科技有限公司 一种气动阻尼缓冲器
DE102015109188A1 (de) 2015-06-10 2016-12-15 Samuel Grega Kolben für einen Fluiddämpfer, der für gegeneinander verstellbare Möbelteile mit einem relativ in einem Zylinder verstellbar geführten Kolben ausgebildet ist
DE202018006847U1 (de) 2017-08-02 2023-10-05 Wolfgang Held Fluiddämpfer für gegeneinander verstellbare Körper mit einem in einem Zylinder verstellbar geführten Kolben
EP3665399B1 (fr) 2017-08-09 2024-01-03 Wolfgang Held Amortisseur à fluide pour parties de meubles réglables les unes par rapport aux autres pourvu d'un piston guidé de manière réglable dans un cylindre
TWI645811B (zh) 2017-11-06 2019-01-01 川湖科技股份有限公司 可活動傢俱件及其緩衝裝置
CN107972012B (zh) * 2017-11-27 2020-11-10 常州大学 一种可用作机器人腿的竖向柔性伸缩膝关节
US10808874B2 (en) * 2017-11-30 2020-10-20 General Electric Company Inline fluid damper device
DE202018103637U1 (de) * 2018-06-26 2019-09-27 Druck- und Spritzgußwerk Hettich GmbH & Co. KG Dämpfer
DE202019100230U1 (de) * 2019-01-16 2020-04-17 Grass Gmbh Vorrichtung zur Bewegungsdämpfung eines Möbelteils und Führungsvorrichtung
AT523986B1 (de) 2020-07-13 2023-05-15 Blum Gmbh Julius Möbeldämpfer
EP4198238B1 (fr) 2021-12-14 2024-06-12 Julius Blum GmbH Amortisseur pour une butée destinée au stockage mobile d'un élément pivotant ou d'un élément d'extraction

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US5927448A (en) * 1996-03-15 1999-07-27 Fuji Seiki Kabushiki Kaisha Shock absorber
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EP2114203A1 (fr) * 2007-01-31 2009-11-11 Deon AG Entraînement de meuble à moteur électrique
AT508069B1 (de) * 2009-03-25 2015-03-15 Blum Gmbh Julius Möbelscharnier
AU2013407407B2 (en) * 2013-12-13 2017-09-21 Kesseböhmer Holding Kg Safety brake for telescopic furniture post
WO2015086093A1 (fr) * 2013-12-13 2015-06-18 Kesseböhmer Produktions GmbH & Co. KG Frein de sécurité pour colonne de meuble télescopique
US10258146B2 (en) 2013-12-13 2019-04-16 Kesseböhmer Produktions GmbH & Co. KG Safety brake for telescoping furniture post
CN105650305A (zh) * 2016-02-24 2016-06-08 北京亚泰金合机械设备有限公司 缓冲阀
AT518359A1 (de) * 2016-03-07 2017-09-15 Blum Gmbh Julius Möbeldämpfer
AT16871U1 (de) * 2016-03-07 2020-11-15 Blum Gmbh Julius Möbeldämpfer
EP3485180B1 (fr) * 2016-07-12 2022-06-01 Stabilus GmbH Amortisseur de frein de voie
EP3279499A1 (fr) * 2016-08-05 2018-02-07 BeijingWest Industries Co. Ltd. Amortisseur hydraulique doté d'une bande d'usure autoréglable
US10247272B2 (en) 2016-08-05 2019-04-02 Beijingwest Industries Co., Ltd. Hydraulic damper having self-adjusting wear band
AT520128A1 (de) * 2017-07-13 2019-01-15 Blum Gmbh Julius Möbeldämpfer
US11140984B2 (en) 2017-07-13 2021-10-12 Julius Blum Gmbh Furniture damper
EP4357638A2 (fr) 2017-07-13 2024-04-24 Julius Blum GmbH Amortisseur pour meubles

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