EP3757328B1 - Ferme-porte - Google Patents

Ferme-porte Download PDF

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Publication number
EP3757328B1
EP3757328B1 EP20173764.0A EP20173764A EP3757328B1 EP 3757328 B1 EP3757328 B1 EP 3757328B1 EP 20173764 A EP20173764 A EP 20173764A EP 3757328 B1 EP3757328 B1 EP 3757328B1
Authority
EP
European Patent Office
Prior art keywords
throttle
section
door closer
throttle portion
flow
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.)
Active
Application number
EP20173764.0A
Other languages
German (de)
English (en)
Other versions
EP3757328A2 (fr
EP3757328A3 (fr
Inventor
Benjamin Wörner
Jaspar Engels
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.)
Geze GmbH
Original Assignee
Geze 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 Geze GmbH filed Critical Geze GmbH
Priority to RS20241289A priority Critical patent/RS66207B1/sr
Publication of EP3757328A2 publication Critical patent/EP3757328A2/fr
Publication of EP3757328A3 publication Critical patent/EP3757328A3/fr
Application granted granted Critical
Publication of EP3757328B1 publication Critical patent/EP3757328B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
    • E05F3/12—Special devices controlling the circulation of the liquid, e.g. valve arrangement
    • 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
    • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
    • E05Y2800/20—Combinations of elements
    • E05Y2800/205—Combinations of elements forming a unit
    • 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
    • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
    • E05Y2800/20—Combinations of elements
    • E05Y2800/244—Combinations of elements arranged in serial relationship
    • 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
    • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
    • E05Y2900/13—Type of wing
    • E05Y2900/132—Doors

Definitions

  • the invention relates to a door closer with a closer body and, in the closer body, a hydraulic system for at least one hydraulic function, in particular for adjusting the opening damping, closing speed and/or closing delay, wherein the hydraulic system comprises at least one channel for a hydraulic medium and at least one throttle valve which has a throttle section located in the flow path of the hydraulic medium through the channel, which forms a gap with the channel wall which determines the size of the flow cross section.
  • Such door closers are generally known, see for example AT 219 450 B , and are used in modern buildings to increase the safety and comfort when using building doors.
  • the use of a hydraulic system makes it possible to provide a door closer with a variety of functions in a simple and reliable manner. These include, for example, adjusting the opening damping, the closing speed and the closing delay.
  • throttle valves also known as regulating valves, in the channels of the hydraulic system.
  • Throttle valves are also generally known, see for example US 3 326 513 A , DE 102 28 872 A1 , or also US 3 155 367 A , whereby the above-cited AT 219 450 B an insert of throttle valves in door closers is removable. These valves are accessible on the outside of the closer body to enable the user or service personnel to carry out adjustments. In practice, the valves are usually screwed into holes in the closer body or its housing, so that by turning the valve using a tool, the axial position of an effective section of the valve, namely the throttle section, can be changed in order to To be able to adjust the effectiveness of each hydraulic function to a desired value.
  • the gap between the throttle section of the valve and the channel wall also known as the throttle gap
  • the gap between the throttle section of the valve and the channel wall is typically very narrow in door closers. This is because the hydraulic systems of door closers are usually subject to high pressures and low volume flows due to their design. Narrow throttle gaps tend to become clogged by impurities that are inevitably present in the hydraulic medium, which impairs functionality and endangers functional reliability. The impurities are in particular particles of various origins, material abrasion and air bubbles.
  • Another problem associated with throttle valves in door closers is that temperature fluctuations result in corresponding changes in the viscosity of the hydraulic medium. Oil is typically used as the hydraulic medium. At lower temperatures, the oil is more viscous than at higher temperatures, so lower temperatures mean that less oil passes through the throttle gap.
  • the object of the invention is therefore to eliminate these disadvantages and to create possibilities to reduce the negative effects of external influences on the hydraulic system and in particular the throttle valves used therein in order to ensure safe and reliable operation of door closers.
  • the throttle section is arranged to be movable relative to the channel wall such that the throttle section positions itself relative to the channel wall under the influence of the flow.
  • the movable throttle section according to the invention can change its position under the influence of the flow, in particular under the influence of impurities contained in the flowing hydraulic medium that are too large for the gap that is currently present. It was surprisingly found that, for example, particles present in the hydraulic medium that would actually be too large for the throttle gap that is set in each case can move the throttle section relative to the channel wall and thus locally enlarge the gap so that they can flow through the gap.
  • the mobility of the throttle section under the influence of the flow is thus equivalent to a throttle gap that adapts itself to the flow.
  • the invention thus creates an adaptive throttle gap.
  • the size of the flow cross-section determined by the gap that is set in each case does not change as a result of this evasive movement of the throttle section or - depending on the geometric conditions at the gap and the manner in which the throttle section is movable - at most changes minimally, because the gap only increases locally. At another point, the gap is simultaneously reduced in size.
  • This aspect of the invention therefore makes use of the knowledge that a movably arranged throttle section can move under the influence of the flow can move relative to the channel wall, while maintaining the size of the flow cross-section, but locally enlarging the gap.
  • the size of the flow cross-section can change minimally during this movement of the throttle section, depending on the respective geometric conditions.
  • a change in the size of the flow cross-section would be so small that it does not represent a change such as can be brought about by the adjustment processes mentioned at the beginning, provided that the respective throttle valve is adjustable.
  • the respective throttle valve is adjustable.
  • the invention can also be used in conjunction with such non-adjustable throttle valves.
  • the mobility of the throttle section relative to the channel wall under the influence of the flow according to the invention is therefore not to be understood as an adjustment movement of the valve or its throttle section, as can be carried out by a user from the outside by means of a tool, for example, provided that the throttle valve has such an adjustment option.
  • the throttle section is preferably designed and arranged in such a way that it has at least one translational or rotational degree of freedom.
  • the throttle section has a longitudinal axis around which the throttle section is rotationally symmetrical. If the throttle valve is adjustable, then the throttle section is preferably movable along an adjustment axis during an adjustment process, wherein this adjustment axis preferably coincides with the mentioned axis of symmetry (longitudinal axis) of the throttle section when the Throttle section is in a centric basic position.
  • the mentioned at least one degree of freedom for self-positioning then relates to this longitudinal axis or axis of symmetry of the throttle section.
  • the throttle section does not have a translational degree of freedom for its self-positioning, but rather one, two or three rotational degrees of freedom.
  • the throttle section has two rotational degrees of freedom, specifically about two axes that run perpendicular to each other and to the axis of symmetry of the throttle section.
  • the throttle section can be inclined or tilted in any direction relative to the axis of symmetry in order to react to impurities in the flow, i.e. to avoid particles if necessary, for example, and to be able to position itself relative to the channel wall under the influence of the flow.
  • the movement of the throttle section under the influence of the flow is in particular an inclination movement, a tipping movement or a deflection movement.
  • the position of the throttle section can also be changed by an adjustment process in order to adjust the size of the flow cross section.
  • This change in position for adjusting the size of the flow section is preferably a linear movement along an axis, also referred to below as the adjustment axis, with respect to which the throttle section has no degree of freedom for the self-positioning according to the invention that takes place under the influence of the flow.
  • the throttle section can be moved along an adjustment axis during the adjustment process, with the throttle section and a channel section delimited by the channel wall tapering along this adjustment axis.
  • the throttle section and the channel section preferably have a conical shape with a circular cross-section perpendicular to the adjustment axis.
  • the throttle section and channel wall In a central basic position, in which the axis of symmetry of the throttle section coincides with the adjustment axis, the throttle section and channel wall consequently form a gap with a circular free cross-sectional area, which determines the flow cross-section of the throttle valve. In this basic position of the throttle section, there is therefore a central throttle gap.
  • the gap width increases locally, while the gap width at a diametrically opposite point decreases accordingly. This means that there are local changes in the gap width, but the size of the flow cross-section, i.e. the free cross-sectional area of the entire gap, practically does not change.
  • the throttle section and the channel section are provided in the form of cones lying one inside the other, forming the circumferential gap.
  • this is not mandatory.
  • the channel wall and the throttle section form an introduction opening on the inflow side that widens against a flow direction and leads into the gap. This can be achieved in particular in a simple manner by rounding off the free end of the throttle section.
  • the throttle valve comprises a base section to which the throttle section is connected and relative to which the throttle section is movable under the influence of the flow.
  • the type of connection which will be discussed in more detail below, is basically arbitrary.
  • the connection between the throttle valve and the base section is a movable bearing which is designed in such a way that it allows the throttle section to position itself under the influence of the flow.
  • connection can, for example, be designed in such a way that the throttle section is suspended or hooked onto the base section in such a way that it can be deflected in all directions - practically like a pendulum.
  • This design therefore provides a multi-part throttle valve, with the parts being movable relative to one another.
  • the base section relative to which the throttle section is movable under the influence of the flow, does not necessarily have to be a component of the throttle valve or be considered a component of the throttle valve.
  • the base section can also form a component of the closing body or its housing or be considered as such a component.
  • the throttle valve can therefore be formed in one piece, namely by the movable throttle section, the movement of which takes place relative to the closing body or its housing.
  • the base section has a position which determines the size of the flow cross-section and is not influenced by the flow, and which can be changed by an adjustment process to adjust the size of the flow cross-section. It is therefore the base section that is moved during an adjustment process, whereby this adjustment movement of the base section is transmitted by suitable, basically arbitrarily designed means to the throttle section, which, through its interaction with the channel wall, namely by forming of the throttle gap, the free cross-sectional area of the throttle gap and thus the size of the flow cross-section.
  • the throttle section is connected to the base section in a fixed or play-like manner with respect to an adjustment axis along which the throttle section is movable for adjusting the size of the flow cross-section, and has at least one translational or rotational degree of freedom for its self-positioning in addition to this connection.
  • the movable arrangement of the throttle section can be such that the throttle section is freely movable relative to the base section to an extent limited only by the channel wall and the base section.
  • the free mobility ensures that even if only comparatively small forces, such as in particular from contaminants flowing with the hydraulic medium, are applied to the throttle section, it can give way by locally enlarging the gap in order to let the contaminants pass through and thus prevent the throttle gap from becoming blocked.
  • connection between the base section and the throttle section can be a form-fitting connection, which is provided with a Self-positioning of the throttle section is subject to sufficient play.
  • a form-fitting connection enables sufficiently free movement of the throttle section relative to the base section, allows the throttle section to be moved when the base section is adjusted to set the size of the flow cross-section, and prevents the throttle section from becoming detached from the base section.
  • At least in some hydraulic systems of door closers at least one throttle valve must be able to flow in both directions. Consequently, forces can act on the throttle section in both flow directions.
  • connection between the throttle section and the base section is preferably designed in such a way, in particular as a positive connection, that the throttle section is arranged in a captive manner in both flow directions.
  • connection between the throttle section and the base section can include a rotary bearing with two or three rotational degrees of freedom.
  • the relative movement between the throttle section and the base section can in particular be a rolling movement.
  • the base section and the throttle section preferably have interacting bearing surfaces.
  • These bearing surfaces can be designed in such a way that they form a rotary bearing with one or more rotational degrees of freedom and/or allow a rolling movement.
  • one bearing surface is flat and the other bearing surface is convexly curved.
  • the base section and the throttle section have at least two interacting bearing surface pairs, wherein either one or the other bearing surface pair is effective depending on the direction of the flow.
  • the adaptive property of the throttle valve according to the invention i.e. the possibility of self-positioning of the throttle section under the influence of the flow in order to adjust the throttle gap, is thus guaranteed for each of the two flow directions.
  • the throttle valve according to the invention can therefore be flowed through by the hydraulic medium in both directions without there being a risk of clogging or blockage due to impurities contained in the hydraulic medium.
  • the throttle section and the base section are each designed in such a way that both a positive connection and a movable bearing are realized by interacting bearing surfaces in a particularly effective manner and at the same time with ease of manufacture.
  • the base section and the throttle section have interacting bearing sections, wherein one bearing section is mushroom-shaped and comprises a mushroom head provided with one or more bearing surfaces, wherein the other bearing section engages behind the mushroom head and has a receptacle for the mushroom head, which is delimited by at least one bearing surface interacting with a bearing surface of the mushroom head.
  • the mushroom head generally an extended section, on the one hand and the bearing section that engages behind and accommodates it on the other hand therefore not only form the positive locking means for the positive connection of the throttle section and base section, but at the same time also provide the bearing surfaces for the movable mounting of the throttle section relative to the base section.
  • the mushroom head can be formed on the base section and the bearing section containing the receptacle can be formed on the throttle section, or vice versa.
  • the mushroom head has at least two bearing surfaces, whereby, depending on the direction of the flow, either one or the other bearing surface interacts with a bearing surface that delimits the receptacle.
  • the mushroom head is lens-shaped or designed as an ellipsoid.
  • the shape of the mushroom head is selected in particular such that its bearing surfaces are comparatively slightly curved. This can be achieved, for example, by the aforementioned lens shape of the mushroom head.
  • An appropriately dimensioned ellipsoid can also provide comparatively slightly curved bearing surfaces.
  • a positive connection which at the same time includes a certain amount of play, is one of the preferred options for the connection or coupling between the base section and the throttle section.
  • other alternative designs are also possible.
  • the base section and the throttle section can be connected to one another by at least one elastically deformable element that allows the throttle section to move relative to the base section under the influence of the flow.
  • the elastically deformable element is in particular a separate component to which the base section and throttle section are each firmly connected.
  • the throttle section and base section can be made of rigid or stiff, non-elastically deformable materials, for example plastic or metal.
  • the base section and the throttle section can be directly connected to one another, wherein either the base section or the throttle section has an elastically deformable region which allows movement of the throttle section relative to the base section under the influence of the flow. It is also possible for both the base section and the throttle section to have such an elastically deformable region.
  • the throttle section is made completely or partially from a material which differs in terms of the coefficient of thermal expansion from the material of the closing body in the area of the throttle section.
  • a material which differs in terms of the coefficient of thermal expansion from the material of the closing body in the area of the throttle section.
  • the materials differ from one another with regard to the spatial expansion coefficient or the linear expansion coefficient with respect to an adjustment axis along which the throttle section is movable for adjusting the size of the flow cross-section.
  • the material of the throttle section is a plastic, wherein the material of the closing body is preferably aluminum or steel.
  • a throttle valve for a door closer in particular a door closer as disclosed herein, having a base portion and a throttle portion which is connected to the base portion and is movable relative to the base portion.
  • Fig.1 shows a basically known closing body 11 of a conventional door closer.
  • the closing body 11 has a cuboid basic shape with a housing 35.
  • a side of the housing 35 is shown which, in the assembled state, is accessible to a user when a Fig.1 a cover (not shown) which can be designed as a slide, for example, is removed.
  • Various functional and display devices are then accessible to the user. These include in particular two throttle valves of a hydraulic system housed in the closing body 11. Of these throttle valves, also referred to as regulating valves, which are screwed into the closing body 11, two components referred to here as base sections 17 are accessible, which are also referred to as the valve head and can be adjusted using a screwdriver.
  • Fig. 2 shows a throttle valve of a conventional door closer known from the prior art.
  • the base section 17 mentioned is provided with a slot 17a for a screwdriver on its front side, which is accessible from the outside when screwed in.
  • the base section 17 has a thread 39, via which the base section 17 and thus the entire throttle valve is screwed into an opening 12 formed in the closer body 11.
  • the throttle valve At its end facing away from the front side with the slot 17a, the throttle valve is provided with a conical throttle section 15, which is arranged in a channel section 25 of a channel of the hydraulic system of the door closer in order to be able to regulate the flow of a hydraulic medium in the form of an oil through the channel.
  • the direction of flow of the hydraulic medium is indicated by the arrows S. In principle, however, it is It is possible for the flow to flow through the channel in the opposite direction. In this case too, the flow can be regulated by the throttle valve 15, 17.
  • the channel is also conical, wherein the conical throttle section 15 and the conical channel section 25 have the same cone angle and consequently the throttle section 15 forms with the wall 19 of the channel section 25 a circumferential throttle gap 21, the width of which is constant along a central axis 15a of the valve 15, 17.
  • the size of the gap 21 determines the size of the flow cross-section in the channel section 25 set by the respective position of the throttle valve 15, 17 in the opening 12 and thus determines the corresponding volume flow of the hydraulic medium.
  • the volume flow can be regulated by changing the position of the valve 15, 17.
  • the user can use a screwdriver via the thread 39 to adjust the valve 15, 17 further into the opening 12 or in the opposite direction, namely along an adjustment axis 23, which here coincides with the central axis 15a of the valve 15, 17.
  • This axial adjustment movement changes the size of the gap 21 between the two conical surfaces, i.e. between the conical outer surface of the throttle section 15 on the one hand and the conical inner wall of the channel section 25 on the other hand.
  • the gap 21 can become clogged by impurities in the hydraulic medium, for example by the schematically indicated particles 37 which are too large to pass through the gap 21.
  • the embodiments of a throttle valve according to the invention described below differ from this known throttle valve in that the throttle section 15 and the base section 17 are not integrally or rigidly connected to one another, but that the throttle section 15 is movable relative to the base section 17.
  • all the above statements regarding the closing body apply here accordingly, ie the invention can be used without changing the closing body.
  • existing known throttle valves such as those in Fig. 2 can be replaced by throttle valves according to the invention without having to modify the closing body.
  • Fig. 3a and 3b, 4a and 4b and 5 illustrate the basic principle of the invention.
  • Possible connections which can also be referred to as couplings or bearings or as comprising couplings or bearings, between the throttle section 15 and the base section 17, which enable the mobility of the throttle section 15 relative to the base section 17, are explained elsewhere using further figures.
  • the mobility of the throttle section 15 enables the throttle section 15 to be deflected under the influence of the flow, in this case by the particles 37 flowing with the hydraulic medium, so that the throttle section 15 is tilted and the central axis 15a runs at an angle to the adjusting axis 23.
  • Fig. 4a and 4b show, this results in a local increase in the gap width, ie an enlarged gap area 22 is created at a circumferential angle area. At the diametrically opposite point, the gap width is reduced accordingly. Overall, this creates a so-called eccentric throttle gap.
  • the particles 37 carried by the hydraulic medium have, as it were, made their own way through the gap 21, namely through the gap area 22 which they themselves have enlarged.
  • the size of the flow cross-section remains constant, i.e. the free cross-sectional area of the gap 21 does not change in terms of its size, but in terms of its shape.
  • Fig.5 shows that the free end of the throttle section 15 can be rounded, whereby an outwardly widening, annular introduction opening 27 is present in the gap 21, which makes it easier for particles 37 or other contaminants of the hydraulic medium to enter the gap 21 and deflect the throttle section 15.
  • the throttle section 15 and the base section 17 are positively connected to one another by two bearing sections that are rotationally symmetrical with respect to the central axis 15a, namely by a mushroom-shaped bearing section 29 of the base section 17 and a Bearing section of the throttle section 15, which comprises a receptacle 31 for the mushroom head 29 and a stop section 32 encompassing the mushroom head 29.
  • the mushroom head 29 On its front side facing the throttle section 15, the mushroom head 29 is provided with a comparatively slightly curved bearing surface 29a, which interacts with a flat bearing surface 31a running perpendicular to the central axis 15a and delimiting the receptacle 31.
  • the so-called throttle pressure D moves the throttle section 15 in the direction of the base section 17 and thus the aforementioned bearing surfaces 29a and 31a abut one another, the mushroom head 29 can roll on the flat bearing surface 31a of the throttle section 15 if a torque or tilting moment acts on the throttle section 15. Since the positive connection between the throttle section 15 and the base section 17 has sufficient play, the throttle section 15 is practically freely movable relative to the base section 17, so that even comparatively small forces or moments are sufficient to deflect the throttle section 15. This possibility for self-alignment or self-positioning of the throttle section 15 under the influence of the flow is promoted by the described design of the bearing surfaces 29a, 31a.
  • This further pair of bearing surfaces is formed by a circular surface 31 b on the stop section 32 of the throttle section 15 on the one hand and by a circular surface 29 b on the mushroom head 29, these surfaces 31 b, 29 b are each rotationally symmetrical with respect to the central axis of the base section 17 or the central axis 15a of the throttle section 15 coinciding with the adjusting axis 23.
  • Fig.7 shows that the positive connection between the throttle section 15 and the base section 17 in the direction of the adjusting axis 23 has a slight play, because the bearing surfaces 29a, 31 are slightly spaced from each other here.
  • the mushroom head 29 serves as a driver for the throttle section 15 or for holding the throttle section 15.
  • the two bearing surfaces 29b, 31b are in contact with one another.
  • the surfaces 29b, 31b are designed in such a way that - in relation to a plane running perpendicular to the adjusting axis 23 - there is a comparatively flat or small stop angle ⁇ . This ensures that the mushroom head 29 is securely carried or securely held, ie it is ensured that the mushroom head 29 cannot come out of the holder 31.
  • This design of the bearing surfaces 29b, 31b also ensures that the throttle section 15 cannot jam on the mushroom head 29.
  • the surfaces 31a, 31b of the mushroom head 29 can have at least approximately the same, comparatively small curvature, so that the mushroom head 29 has a lens-shaped basic shape.
  • Fig.8 shows a throttle valve according to the invention over its entire axial extent, wherein the throttle section 15 is shown in a tilted position relative to the base section 17, in which the throttle gap has an enlarged gap area 22.
  • the closing body 11 or its housing, at least in the area of the throttle section 15, and the throttle section 15 can be made of different materials that differ from one another in terms of their thermal expansion coefficient.
  • the closing body 11 is made of steel or aluminum, for example, while the throttle section 15 is made of a plastic.
  • the dimensions of the throttle section 15 thus change to a greater extent than those in the area of the closing body 11 that delimits the throttle gap 21.
  • the throttle gap 21 is therefore larger than at higher temperatures.
  • the material can be selected in such a way that adjust such size differences that compensate for a change in the viscosity of the hydraulic medium that is also caused by temperature fluctuations.
  • Fig.9 shows an alternative design of the connection between the throttle section 15 and the base section 17.
  • the throttle section 15 is provided here with an elastically deformable region 33, via which the throttle section 15 is firmly connected to the base section 17.
  • This deformable region 33 enables the mobility of the throttle section 15 relative to the base section 17, as indicated by the double arrow B.
  • the region 33 can be cylindrical with a circular cross-section around the central axis 15a of the throttle section 15, so that it can be deflected in any direction, ie regardless of the circumferential angle range around the central axis 15a at which a contamination penetrates into the gap, this can cause a deflection of the throttle section 15.
  • Fig.10 shows a form-fitting connection with sufficient play between the throttle section 15 and the base section 17, which ensures the mobility of the throttle section 15 relative to the base section 17 in all directions, indicated by a double arrow B.
  • the front end of the mushroom head 29 is flat. There is therefore no rolling movement between the base section 17 and the throttle section 15.
  • the circumferential contact surface 31c on the front side of the stop section 32 of the throttle section 15 is bevelled, i.e. it does not run perpendicular to the central axis 15a of the throttle section 15, so that when the flow passes through the valve, the throttle section 15 is pressed against the surface 29c of the base section 17. Due to the bevel mentioned, the throttle section 15 can be tilted if contamination of the hydraulic medium applies a force or a moment in the area of its free end (not shown here).
  • a further advantage of the invention in all the embodiments described is that the mobility of the throttle section 15 means that impurities, for example in the form of air inclusions, cannot become statically fixed.
  • impurities for example in the form of air inclusions
  • the flow of the hydraulic medium can cause the throttle section 15 to vibrate, whereby impurities in particle form are "shaken loose" and air inclusions are dissolved.
  • the throttle section 15, which is movable under the influence of the flow can therefore not only allow large contaminants to pass through the throttle gap 21, but can also ensure that smaller particles, which could pass through the throttle gap 21 even without the mobility of the throttle section 15, cannot become lodged in the throttle gap 21.

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Claims (18)

  1. Ferme-porte comprenant un corps de fermeture (11) et, dans le corps de fermeture (11), un système hydraulique pour au moins une fonction hydraulique, en particulier pour régler l'amortissement de l'ouverture, la vitesse de fermeture et/ou la temporisation de la fermeture,
    le système hydraulique comprenant au moins un canal (13) pour un fluide hydraulique et au moins une vanne d'étranglement (15, 17) qui présente une section d'étranglement (15) située dans le trajet d'écoulement du fluide hydraulique à travers le canal (13), laquelle forme avec la paroi du canal (19) un interstice (21) déterminant la taille de la section d'écoulement,
    caractérisé en ce que
    la section d'étranglement (15) est agencée de manière mobile par rapport à la paroi du canal (19) de telle sorte que la section d'étranglement (15) se positionne elle-même par rapport à la paroi du canal (19) sous l'influence de l'écoulement.
  2. Ferme-porte selon la revendication 1,
    caractérisé en ce que
    la section d'étranglement (15) ne présente pas de degré de liberté en translation pour son auto-positionnement, mais un, deux ou trois degrés de liberté en rotation.
  3. Ferme-porte selon la revendication 1 ou la revendication 2,
    caractérisé en ce que
    pour régler la taille de la section d'écoulement, la position de la section d'étranglement (15) est en outre apte à être modifiée par une opération de réglage.
  4. Ferme-porte selon la revendication 3,
    caractérisé en ce que
    la section d'étranglement (15) est apte à être déplacée le long d'un axe de réglage (23) lors de l'opération de réglage, la section d'étranglement (15) et/ou une section de canal (25) délimitée par la paroi de canal (19) se rétrécissant en particulier le long de l'axe de réglage (23), la section d'étranglement (15) et/ou la section de canal (25) ayant de préférence une forme conique avec une section transversale circulaire perpendiculaire à l'axe de réglage (23).
  5. Ferme-porte selon l'une des revendications précédentes,
    caractérisé en ce que
    la paroi de canal (19) et la section d'étranglement (15) forment, côté arrivée, une ouverture d'introduction (27) s'élargissant dans le sens opposé à une direction d'écoulement (S) et menant dans l'interstice (21).
  6. Ferme-porte selon l'une des revendications précédentes,
    caractérisé en ce que
    la vanne d'étranglement (15, 17) ou le corps de fermeture (11) comprend une section de base (17) à laquelle la section d'étranglement (15) est reliée et par rapport à laquelle la section d'étranglement (15) est apte à être déplacée sous l'influence de l'écoulement.
  7. Ferme-porte selon la revendication 6,
    caractérisé en ce que
    la section de base (17) présente une position qui détermine la taille de la section d'écoulement, qui n'est pas influencée par l'écoulement et qui est apte à être modifiée par une opération de réglage pour ajuster la taille de la section d'écoulement.
  8. Ferme-porte selon la revendication 6 ou la revendication 7,
    caractérisé en ce que
    la section d'étranglement (15) est reliée à la section de base (17) de manière fixe ou avec jeu par rapport à un axe de réglage (23) le long duquel la section d'étranglement (15) est apte à être déplacée pour régler la taille de la section d'écoulement, et présente pour son auto-positionnement, en plus de cette liaison, au moins un degré de liberté en translation ou en rotation.
  9. Ferme-porte selon l'une des revendications 6 à 8,
    caractérisé en ce que
    la section d'étranglement (15) est apte à être déplacée de façon libre par rapport à la section de base (17) dans une mesure limitée uniquement par la paroi de canal (19) et la section de base (17).
  10. Ferme-porte selon l'une des revendications 6 à 9,
    caractérisé en ce que
    la liaison entre la section de base (17) et la section d'étranglement (15) comprend une liaison par complémentarité de forme qui présente un jeu suffisant pour permettre l'auto-positionnement de la section d'étranglement (15).
  11. Ferme-porte selon l'une des revendications 6 à 10,
    caractérisé en ce que
    la liaison entre la section de base (17) et la section d'étranglement (15) comprend un palier de rotation à deux ou trois degrés de liberté en rotation.
  12. Ferme-porte selon l'une des revendications 6 à 11,
    caractérisé en ce que
    le mouvement relatif entre la section d'étranglement (15) et la section de base (17) est un mouvement de roulement.
  13. Ferme-porte selon l'une des revendications 6 à 12,
    caractérisé en ce que
    la section de base (17) et la section d'étranglement (15) présentent des surfaces d'appui coopérantes, l'une des surfaces d'appui étant plane et l'autre surface d'appui étant incurvée de manière convexe.
  14. Ferme-porte selon l'une des revendications 6 à 13,
    caractérisé en ce que
    la section de base (17) et la section d'étranglement (15) présentent au moins deux paires de surfaces d'appui coopérantes, l'une ou l'autre paire de surfaces d'appui étant active en fonction de la direction (S) de l'écoulement.
  15. Ferme-porte selon l'une des revendications 6 à 14,
    caractérisé en ce que
    la section de base (17) et la section d'étranglement (15) présentent des sections d'appui coopérantes, l'une des sections d'appui étant réalisée sous forme de champignon et comprenant une tête (29) en forme de champignon pourvue d'une ou de plusieurs surfaces d'appui (29a, 29b, 29c), l'autre section d'appui s'engageant derrière la tête en forme de champignon et comprenant un logement (31) pour la tête (29) en forme de champignon, qui est délimité par au moins une surface d'appui (31a, 31b, 31c) coopérant avec une surface d'appui (29a, 29b, 29c) de la tête (29) en forme de champignon.
  16. Ferme-porte selon la revendication 15,
    caractérisé en ce que
    la tête (29) en forme de champignon présente au moins deux surfaces d'appui (29a, 29b), l'une ou l'autre des surfaces d'appui coopérant avec une surface d'appui (31a, 31b) de la section d'étranglement (15) en fonction de la direction (S) de l'écoulement, la tête (29) en forme de champignon étant de préférence de forme lenticulaire ou ellipsoïdale.
  17. Ferme-porte selon l'une des revendications 6 à 16,
    caractérisé en ce que
    la section de base (17) et la section d'étranglement (15) sont reliées entre elles par au moins un élément élastiquement déformable qui permet un mouvement de la section d'étranglement (15) par rapport à la section de base (17) sous l'influence de l'écoulement.
  18. Ferme-porte selon l'une des revendications 6 à 16,
    caractérisé en ce que
    la section de base (17) et la section d'étranglement (15) sont directement reliées l'une à l'autre, la section de base (17) et/ou la section d'étranglement (15) présentant une zone élastiquement déformable (33) qui permet un mouvement de la section d'étranglement (15) par rapport à la section de base (17) sous l'influence de l'écoulement.
EP20173764.0A 2019-06-28 2020-05-08 Ferme-porte Active EP3757328B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
RS20241289A RS66207B1 (sr) 2019-06-28 2020-05-08 Zatvarač vrata

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019209557.7A DE102019209557B4 (de) 2019-06-28 2019-06-28 Türschliesser mit drosselventil und strömungsabhängigem drosselabschnitt

Publications (3)

Publication Number Publication Date
EP3757328A2 EP3757328A2 (fr) 2020-12-30
EP3757328A3 EP3757328A3 (fr) 2021-03-17
EP3757328B1 true EP3757328B1 (fr) 2024-09-11

Family

ID=70682575

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20173764.0A Active EP3757328B1 (fr) 2019-06-28 2020-05-08 Ferme-porte

Country Status (5)

Country Link
EP (1) EP3757328B1 (fr)
DE (1) DE102019209557B4 (fr)
FI (1) FI3757328T3 (fr)
PL (1) PL3757328T3 (fr)
RS (1) RS66207B1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3155367A (en) * 1962-01-11 1964-11-03 Vernay Laboratories Valve plunger
DE10228872A1 (de) * 2002-06-27 2004-01-15 Dorma Gmbh + Co. Kg Regulierventil für einen Türschliesser oder hydraulischen Drehflügelantrieb

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT219450B (de) * 1959-07-02 1962-01-25 Ver Baubeschlag Gretsch Co Hydraulische Dämpfeinrichtung für Türschließer
US3326513A (en) * 1964-11-10 1967-06-20 Yarway Corp Means for interconnecting valve members
DE9203872U1 (de) * 1992-03-23 1992-09-10 Schmid, Paul, Rothrist Türschließer mit Fluid-Drosselventil mit thermostatischer Drosselung, zum Ausgleich der Fluidviskositätsänderung bei schwankender Temperatur

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3155367A (en) * 1962-01-11 1964-11-03 Vernay Laboratories Valve plunger
DE10228872A1 (de) * 2002-06-27 2004-01-15 Dorma Gmbh + Co. Kg Regulierventil für einen Türschliesser oder hydraulischen Drehflügelantrieb

Also Published As

Publication number Publication date
DE102019209557B4 (de) 2025-07-17
EP3757328A2 (fr) 2020-12-30
PL3757328T3 (pl) 2025-02-17
FI3757328T3 (fi) 2024-12-05
DE102019209557A1 (de) 2020-12-31
EP3757328A3 (fr) 2021-03-17
RS66207B1 (sr) 2024-12-31

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