EP0285775B1 - Ferme-porte - Google Patents

Ferme-porte Download PDF

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Publication number
EP0285775B1
EP0285775B1 EP88102261A EP88102261A EP0285775B1 EP 0285775 B1 EP0285775 B1 EP 0285775B1 EP 88102261 A EP88102261 A EP 88102261A EP 88102261 A EP88102261 A EP 88102261A EP 0285775 B1 EP0285775 B1 EP 0285775B1
Authority
EP
European Patent Office
Prior art keywords
door
control
bore
valve
door closer
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.)
Expired - Lifetime
Application number
EP88102261A
Other languages
German (de)
English (en)
Other versions
EP0285775A1 (fr
Inventor
Gerhard SCHRÖDER
Peter Kubelka
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.)
Gretsch Unitas GmbH Baubeschlaege
Original Assignee
Gretsch Unitas GmbH Baubeschlaege
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
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Publication of EP0285775A1 publication Critical patent/EP0285775A1/fr
Application granted granted Critical
Publication of EP0285775B1 publication Critical patent/EP0285775B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/223—Hydraulic power-locks, e.g. with electrically operated hydraulic valves
    • 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
    • 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
    • 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
    • E05Y2900/10—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 according to the preamble of claim 1.
  • It is a hydraulic door closer, which is often used as a floor door closer.
  • Such door closers can be equipped with a hydraulic locking device that prevents the door from closing automatically from a certain opening angle. This angle is due to the location of a cross channel in the hydraulic Cylinder determined.
  • the hydraulic locking device presupposes the presence of a lockable throttle valve, specifically in accordance with the generic term of this door closer of the second throttle valve.
  • the hydraulically locked door can still be closed by turning it manually in the closing direction.
  • This further throttle valve must be fitted so that it cannot be blocked by the piston or its piston ring in any possible opening position of the door, i.e. the transverse channel of this throttle valve in the front cylinder space is basically open.
  • a door closer according to the preamble of claim 1, which has a first throttle valve, a second shut-off throttle valve and at least one further Has throttle valve
  • this numbering of the throttle valves is not associated with any evaluation and, of course, it does not exclude the presence of additional throttle valves.
  • the exemplary embodiment shows that there may well be more than three throttle valves.
  • three throttle valves are the "minimum equipment" of this door closer and the designation chosen was only for the sake of expediency to present the invention.
  • this door closer is equipped with a pressure relief valve, in particular a non-return valve, which is continuous to the rear cylinder space and with at least one pressure relief valve which can flow through to the front cylinder space.
  • a pressure relief valve in particular a non-return valve
  • This formulation also does not rule out the presence of other valves of this type. According to the exemplary embodiment, there are also other such valves.
  • the opening angle up to which the door still closes automatically is fixed, for example it is of the order of 80 to 90 °.
  • the object of the invention is to develop a door closer according to the preamble of claim 1 so that a determination of the maximum opening angle from which the door still closes automatically is avoided.
  • the door closer is designed according to the preamble of claim 1 in accordance with the characterizing part of this claim.
  • the inner opening of a transverse channel in the cylinder determines the maximum opening distance up to which the door closer can still automatically close the door in relation to the maximum possible piston travel when opening the door. If one now provides several such channels, the inner mouths of which are offset in the direction of displacement of the piston, this advantageously opens up the possibility, by blocking and releasing the individual channels, of the maximum opening angle of the door, from which the door is still closed automatically, in stages change or select within these levels.
  • the relevant relevant cross-channel in the front cylinder chamber is no longer assigned to the first throttle valve, but rather to an additional control valve located to a certain extent between the first and second throttle valve.
  • the second throttle valve shuts off the longitudinal housing duct from the front cylinder chamber.
  • the medium flowing back from the rear into the front cylinder chamber can flow past the first throttle valve into the further housing longitudinal channel and thus always reach the control valve regardless of the opening or closing of the second throttle valve. If one speaks of the inflow and outflow side of the first and second throttle valve or control valve, this applies to the direction of flow of the medium when the door is closed, that is to say when the rear cylinder overflows space in the front.
  • the medium can also flow in the opposite direction through a throttle valve _ when the door is opened _ so that the inflow and outflow sides of the throttle valve would then be reversed, but such a flow takes place from the front into the rear cylinder space via the throttle valves and that Control valve not because of the throttling effect, or at least not worth mentioning, because here the overflow takes place via a pressure relief valve opening towards the rear cylinder chamber with a large opening cross section.
  • a particularly preferred embodiment of the invention provides that the closure member of the control valve is designed as a control member which is displaceable and / or rotatable in a bore of the cylinder in which the piston coupled to the rotary member is located, and the inner openings of the outflow channels through the control member individually or can be released one after the other. Because the inner mouths of the outflow channels, i.e. to a certain extent the one end piece of the first flow channel, are arranged offset at least in the longitudinal direction of the cylinder, the displacement distance of the piston, up to which it is driven automatically by the return spring, can be determined by optionally releasing each individual mouth returns to the closed position.
  • all of these openings lie in an area over which the piston or its piston ring moves at least up to the maximum open position of the door. It is preferably the case that the piston or its piston ring is in the maximum open position of the door is moved beyond the "last" mouth. In this case, the maximum open position of the door is always greater than the maximum rotary position up to which the door can still close automatically.
  • the release takes place in such a way that the outflow channel is the first to the outer orifice which is furthest away from the rotary member or the one closest to the cylinder base and the outflow channel to the outer one which is closest to the rotary member Mouth is released last.
  • control member is displaceable in the axial direction of its bore and / or rotatable therein, and is provided with a control edge, control groove or the like.
  • the control member is therefore comparable to a control slide, which can be designed both as a rotary slide and as a longitudinal slide.
  • the design of the closure member or its equipment is either designed with a correspondingly shaped control edge or a flowable control groove or the like. It is also easily conceivable to have more than one, in particular to attach optional tax groove to the control unit.
  • control groove creates the hydraulic connection from the continuing housing longitudinal channel to the mouth of the selected outflow channel on the controller side.
  • a further embodiment of the invention consists in that the inner or control-side openings of the outflow channels are offset in the axial direction of the bore of the control element and the latter is at least displaceable.
  • the inner or control-side openings of the outflow channels are offset in the axial direction of the bore of the control element and the latter is at least displaceable.
  • control member is provided with a control edge which extends in the circumferential direction, in particular circular, and the bore for the control member is preferably directly connected to the flow with the longitudinal housing channel.
  • the bore for the control element and the housing longitudinal channel expediently intersect, in particular at an angle of 90 °.
  • the control edge is attached in such a way that in one end position of the control member, in which it is closest to the longitudinal housing channel, all or at least with the exception of the innermost opening, all other openings are covered. The further the control element is removed from the longitudinal housing channel, the more openings are released.
  • control member can be screwed into a thread in the bore.
  • thread in the bore.
  • it is of course also provided with a thread, but only over a portion of its length, in particular at its end remote from the longitudinal housing channel.
  • a further preferred embodiment of the invention is characterized in that the control member is displaceably but non-rotatably mounted in its bore and is coupled via a threaded connection to an actuating member which is rotatably but non-displaceably mounted in the bore.
  • the threaded connection is either screwed apart or together, so that the control member, depending on the direction of rotation, moves against the longitudinal housing channel or away from it.
  • the actuating member as seen in the longitudinal direction of the bore, always takes up the same space, which is very convenient in terms of actuation, in particular with the aid of a tool or the like, for example a screwdriver or the like.
  • a "connecting channel” in the form of a control groove is provided for their hydraulic connection to the longitudinal housing channel , a control channel or the like.
  • the shape and size of this channel depends on the arrangement of the inner mouths and also the cross section of the outflow channels. In any case, the tax groove should in any case not result in any throttling.
  • the inner orifices are offset both in the axial and in the circumferential direction of the bore for the control element, in particular are arranged along a helical surface line of this bore.
  • the conditions are chosen in particular so that after each about 40 ° angle of rotation of the control member, the next mouth is hydraulically connected to the further longitudinal housing channel via the control groove.
  • the control groove is also helical, ie a helix.
  • a further embodiment of the invention is characterized by a stop pin with a reduced cross-section projecting beyond the control edge against the longitudinal housing channel. This is particularly helpful when setting the maximum opening angle up to which the door should close automatically.
  • the control member is first screwed into its bore until the stop pin strikes a counter-stop surface, in particular the inner end of the bore for the control member which is designed as a blind bore. This initially seals off all internal mouths. Now open the door by the intended maximum opening angle and then screw the control element in the opposite direction out of the blind hole until the door begins to close.
  • the cross section is reduced so much that the gap between the stop pin and the bore wall does not produce a throttling effect.
  • Another preferred embodiment is characterized by markings on the cylinder in the region of the outer mouth of the bore for the control member and a reading mark on the latter or on the actuating member.
  • markings are of course provided in the circumferential direction at the mouth of the bore.
  • an actuation slot for a screwdriver can also be used as a reading mark.
  • the kinematic reversal is also conceivable, according to which the markings are attached to the free end of the control element or, if this is coupled to an actuating element, to the latter, the reading mark then being located at the mouth of the bore for the control element.
  • the piston 1 When opening the door, not shown, which is rotatably connected in a known manner to the rotary member of the door closer, the piston 1 is moved in the cylinder 2 in the direction of arrow 3.
  • the cylinder 2 is located in the housing of the door closer or forms part of the same.
  • the rotary motion of the rotating member is in also of a known type, preferably transmitted via an eccentric mechanism to the piston rod 4 and thus also to the piston 1 firmly connected to it.
  • the rotary member is assigned to the end of the piston rod remote from the piston.
  • the latter is surrounded concentrically by a strong return spring 5, the right end of which in the drawing is supported on the piston 1 and the left end, not shown, of which is supported on a housing wall.
  • the return spring When the piston is moved in the direction of arrow 3, i.e. when the door is opened, the return spring is tensioned.
  • the front cylinder space 6 receiving the piston rod and the spring like the rear cylinder space 7, is filled with a suitable hydraulic fluid.
  • the bore 15 of the first throttle valve 12 opens a further longitudinal duct 16. It consists of the short connector 17 between the first throttle valve 12 and a second throttle valve 18 and a transverse bore 19 which opens into the front cylinder chamber 6.
  • the two throttle valves 12 and 18 are located on a housing or cylinder wall 20.
  • a third throttle valve 22 and a fourth throttle valve 23 are likewise offset in the longitudinal direction on an opposite wall 21 of the housing or the cylinder.
  • the third throttle valve 22 does not include one third channel shown. It has the transverse channel 25, which opens approximately opposite from the transverse channel 10 into the rear cylinder space 7, as well as a longitudinal channel and a further transverse channel 27 opening into the front cylinder space 6.
  • the piston 1 has a two-part piston ring 28.
  • the transverse channel 27 is arranged such that it is released from the piston ring 28 in the starting position of the piston (FIG. 1).
  • the clearance between the piston and the cylinder wall 29 is large enough for the medium to enter the cylinder space 6 from the transverse bore 27 leave as soon as their mouth in the cylinder interior is at least partially released by the piston ring.
  • a fourth channel 37 consists of the transverse bore 30 opening into the front cylinder space, an adjoining longitudinal bore and a further transverse bore 32, 33 which leads to a first pressure relief valve 34 and an annular groove 35 is connected between the parts thereof.
  • the transverse bore 33 also forms the outlet bore of the first pressure relief valve 34. Its inlet bore is denoted by 36 and it opens into the rear cylinder chamber 7. However, it is not released in the starting position of the piston 1, as will be explained below.
  • the inlet 36 of the first pressure relief valve 34 is closed by a spring-loaded (38) closure member 39 of an auxiliary valve 40 attached to the piston 1 (FIG. 1).
  • Both the closure member 39 and the housing 41 of the auxiliary valve 40 have a cup-shaped shape.
  • the pot casing of the housing encompasses that of the closure member and the pot bases are separated from one another.
  • the loading spring 38 for the closure member 39 It is supported on the two pot bases.
  • the pot bottom of the housing 41 has a central hole 42.
  • the closure member 39 is slidably mounted in the housing 41 in the longitudinal direction of the piston axis.
  • a second pressure relief valve 47 is installed in the piston 1 and is closed when the door is closed.
  • Its locking member 48 has the shape of a bolt with an outer collar 49 at its end associated with the rear cylinder space 7. Both the bolt and the collar 49 are designed in a star shape on the outer circumference in order to achieve good guidance in the piston 1 on the one hand and flow through the medium on the other hand.
  • the housing of this second pressure relief valve is formed by the piston 1. Accordingly, the annular valve seat surface is also located there 50.
  • the loading spring 51 holding the closure member in the closed position is centered by a tubular extension, and it is supported with its one end on the outside of the closure member and with its other end on the bottom of the housing 41 of the auxiliary valve 40.
  • the housing 48 of the second pressure relief valve 47 also forms a housing of a third, oppositely opening pressure relief valve 53 which is closed when the door is closed.
  • Its closing element 54 preferably consists of a ball, and its load spring 55, like the other valve springs, is a helical compression spring.
  • the closure member 56 of the first pressure relief valve 34 is preferably a ball and its loading spring is designated 57. It normally keeps the valve closed.
  • the end of the closure member 56 facing away from the spring interacts with the housing valve seat at the right end of the inlet channel 36 in FIG. 1.
  • the closure members 56, 48, 54, 39 of the first, second and third pressure relief valves 34, 47, 53 and the auxiliary valve 40 and thus also these valves themselves are arranged concentrically to the geometric axis of the cylinder or the piston 1. This makes production particularly easy.
  • the separately manufactured base 44 is located at the end of the cylinder facing away from the rotary member. It receives the first pressure relief valve 34 and its transverse bore 33. In addition, an external groove forms the aforementioned annular groove 35. On each side of the latter there is an O-ring 58 or 59. On the outside, it is held by a snap ring 60 or the like.
  • valve bodies of the throttle valves 12, 18, 22 and 23 run perpendicular to the floor when the door closer is designed as a floor door closer in the position of use of the door closer, and their actuating ends (for example 61) are thus easily accessible from above. With another type of door closer, a corresponding adjustment must be made.
  • the housing or the cylinder for the piston 1 is located in an outer housing 62, which can be closed by means of a cover, not shown, so that, in particular, the throttle valves are not accessible to unauthorized persons. It remains to be added that the second pressure relief valve 53 opens at a higher pressure than the first pressure relief valve 34.
  • An adjustable control valve 65 is inserted into the further longitudinal housing channel 16, more precisely into the short connecting piece 17, which is connected directly between the first throttle valve 12 and the second throttle valve 18. Its flow space forming the outflow side when the door is closed is hydraulically connected to or formed by a plurality of outflow channels 66 to 70. Otherwise, the following explanations in connection with this control valve 65, as far as the direction of flow of the medium is concerned, relate to the hydraulic processes when the opened or partially open door is closed.
  • the inner, associated with the closure member 77 of the control valve of the outflow channels 66 to 70 are designated 72 to 76. They can be closed by the closure member and released individually or in succession in a manner to be explained below.
  • the closure member of the control valve 65 is designed as a control member 77 which is displaceable and / or rotatable in a bore 78 of the cylinder 2.
  • the control element 77 of both exemplary embodiments is rotatable in its bore 78. 2, the control member 77 is only rotatable, the control member of the embodiment of FIGS. 3 and 4 additionally shifted in the longitudinal direction of the bore 78. This can be achieved via a threaded connection.
  • the control member 77 is equipped at its outer end with a threaded extension 79 which can be screwed into a thread 80 at the outer end of the bore 78.
  • the control member 77 is provided at its inner end portion with a control edge which has a circular shape. It can be, for example, the edge 81 in FIG. 4. In this exemplary embodiment, this is followed by a stop pin 82 of smaller diameter.
  • the inner openings 72 to 77 of the outflow channels 66 to 70 are offset in the axial direction of the bore 78.
  • a displacement in the circumferential direction of the bore is also provided, so that the inner openings in both exemplary embodiments are arranged along a helix or helical surface line of the bore 78.
  • the bore 78 for the control member 77 is directly connected to the flow with the further housing longitudinal channel 16 or the connecting piece 17.
  • the bore 78 crosses the channel 16 or 17 and preferably runs perpendicularly thereto.
  • the geometric axes of the first and second throttle valve and of the adjustable control valve 65 run parallel to one another and are expediently also arranged in a common plane.
  • control member 77 of the embodiment shown in FIGS. 1 and 2 a bolt-shaped section 82, which extends over a region of the bore 78, within which the inner openings 72 to 76 of the outflow channels 66 to 70 are located. Because this control element 77 can only be rotated but cannot be displaced, the outer casing of this bolt-shaped section 82 covers the inner openings 72 to 76 in every rotational position and also closes them off. However, because of the control groove 83 incorporated into the outer casing of this bolt-shaped section 82, they can be individually “released” by a corresponding rotation of the control member 77.
  • the control groove is open at the bottom in Fig. 2, i.e.
  • control groove 83 also has a helical shape. It is chosen so that only one inner mouth can be brought into hydraulic connection with the channel 16.
  • the closure member 77 of the adjustable control valve 65 does not move in the axial direction, that is to say it is always equally accessible from the outside, the locking member 77 of FIG. 4 penetrates more or less deeply into the bore 78 when rotating.
  • This is not very welcome in terms of actuation, for example by means of a key, screwdriver or the like.
  • the closure member 77 can be made somewhat shorter and can be coupled via a threaded connection to an actuating member, not shown, which is rotatable but non-displaceably mounted in the bore 78. But then it must be longitudinally displaceable, but non-rotatable in the bore.
  • an inward movement is achieved by rotating the latter in one direction of rotation and an outward movement of the closure element 77 by rotating in the opposite direction.
  • this door closer Since the position of the control groove 83 or the control edge 81 cannot be easily recognized from the outside, in particular when using an actuating member, a further development of this door closer provides that 78 markings in the form of a scale or the like surround the mouth of the bore. be attached and there is an associated reading mark at the outer end of the closure member or its actuating member. The arrangement can also be reversed. In this way, an exact setting is possible, which is particularly important in the embodiment variant according to FIG. 2. If space is available, the opening angle of the door up to which it closes automatically can be specified directly above.
  • this door closer is as follows, with two cases to be distinguished. In the first case, the second throttle valve 18 is open. This means that the door is not hydraulically locked.
  • the return spring 5 presses the piston 1 and all parts coupled with it in terms of movement back into the starting position shown in FIG. 1.
  • the medium can also flow into the front cylinder chamber 6 in this way. Because the control valve determining the flow path has a larger flow cross-section than the second throttle valve, at least the majority of the back-flowing liquid flows through the control valve 65.
  • the third channel or its transverse channel 27 is finally released, so that in the final phase of the door closing, the medium can also flow back into the front cylinder chamber 6 via the third channel and the third throttle valve. This causes an accelerated closing in the final phase and a strong decrease in the throttling effect, so that the door closer provides sufficient torque to actuate a lock latch on the door.
  • the second throttle valve 18 is closed. If the door is only opened by an angle of, for example, 80 °, then all outer openings 71 of the outflow channels 66 to 70 of the control valve 65 are still released by the piston or piston ring 28 if the adjustable opening angles on the control valve 65 are greater than, for example, 80 °. Therefore, the door closes after the actuation force ceases to exist solely on the basis of the force of the return spring 5, the medium being able to flow into the front cylinder space via the throttle valve 12 and the mouth 71.
  • adjustable control valve 65 it is possible, for example, to select opening angles which, beginning with the 80 ° open position, are each increased by e.g. 10 ° apart.
  • one of the five outflow channels can then be flowed through, depending on the setting of the control valve 65, while the other four are shut off. If the angle of rotation of the door belonging to this setting of the control valve is exceeded, it remains hydraulically locked.
  • the sealing ring 43 of the auxiliary valve 40 closes the inlet bore 36 of the first pressure relief valve 34.
  • this is the outer mouth 71 of the "selected" outflow channel and thus also the flow through the first channel 14 released so that the back-flowing medium can now flow through the first channel 14 and the first throttle valve 12 to the front cylinder chamber 6.
  • the third channel 27 is finally released.
  • the auxiliary valve and the pressure relief valves work, as said, in the manner of check valves, ie they open when the prevailing pressure exerts a greater force on their closure member than the closing spring acting in the opposite direction.
  • the piston movement creates an overpressure in the front cylinder chamber, while when the door is closed, the rear cylinder chamber 7 comes under overpressure.
  • this overpressure acts, as described above, on the closure member 56 of the first overpressure valve 1.
  • it also acts on the closure member 54 of the third pressure relief valve 53.
  • the hydraulic path goes through the radial slot or slots 52 and the opening of the tubular extension for centering the load spring 51.
  • the load spring 55 of the third pressure relief valve 53 and that of the first pressure relief valve 34 are now coordinated so that the third pressure relief valve 53 opens at a higher pressure than the first pressure relief valve 34, what you can see from the dimensioning of the springs in the drawing.
  • the pressure in the rear cylinder space 7 becomes large enough to also open the third pressure relief valve 53.
  • a sufficiently large return flow cross-section is available which mitigates or eliminates the strong throttling set.
  • the third pressure relief valve 53 can of course be effective from any opening position of the door, in contrast to the first pressure relief valve 34, which is only "released" from an opening angle of the door of, for example, 80 °.
  • the first pressure relief valve 34 has a stable open position. Its inlet bore 36 has a small cross section, so that the force when the valve is closed is relatively small. As soon as the valve 34 opens, however, the liquid acts against a larger area, which then requires less force to keep it open. After there is a back pressure in the fourth channel through the fourth throttle valve 23, the first throttle valve 34 only closes again when the hydraulic fluid can flow out via another route or when the door is stopped in an intermediate position before the "set" outflow channel of the control valve 65 is released. It is particularly advantageous that the closing speed of the door leaf in the range above, for example, 80 ° to 90 ° due to the use of the fourth Throttle valve 23 can be adjusted.
  • the mentioned outer collar 48 of the second pressure relief valve 47 is not circular on the outside, but is star-shaped. It is thereby achieved in a very advantageous manner that the damping fluid is not swirled so strongly when flowing over into the rear cylinder space 7.

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  • Fluid-Pressure Circuits (AREA)

Claims (11)

1. Ferme-porte comprenant un organe tournant qui peut être relié à la porte et dont le mouvement peut être converti en un mouvement de coulissement d'une tige de piston (4), cependant qu'un piston (1) pouvant coulisser dans un cylindre (2) à l'encontre de la force d'un ressort de rappel (5) se trouve à l'extrémité de la tige de piston qui est éloignée de l'organe tournant, qu'en outre, lors de l'ouverture de la porte, un liquide hydraulique est poussé par le piston de la chambre antérieure (6) du cylindre qui reçoit la tige de piston à travers une soupape de surpression (47), et en particulier une soupape antiretour, jusque dans une chambre postérieure (7) du cylindre depuis laquelle il reflue dans la chambre antérieure (6) du cylindre lors de la rotation de la porte dans la direction de fermeture en passant par un premier canal de boîtier (14), ainsi que par une première soupape d'étranglement (12) qui y est insérée et par une deuxième soupape d'étranglement (18) qui peut être fermée et qui est reliée hydrauliquement à cette dernière par l'intermédiaire d'un canal longitudinal de continuation (16) du boîtier, qu'en outre l'embouchure du canal de retour (19) entre la deuxième soupape d'étranglement (18) et la chambre antérieure (6) du cylindre est libre pour tout angle d'ouverture de la porte, et qu'en outre, lorsque la deuxième soupape d'étranglement (18) est fermée, les chambres postérieure et antérieure du cylindre peuvent être reliées en ce qui concerne l'écoulement par l'intermédiaire d'un troisième canal comprenant au moins une autre soupape d'étranglement (23), ainsi qu'au moins une soupape de surpression (34) pouvant être traversée vers la chambre antérieure (6) du cylindre, caractérisé par le fait que, dans le canal longitudinal de continuation (16) du boîtier, entre la première soupape d'étranglement (12) et la deuxième (18), est insérée une soupape de commande (65) réglable dont le côté de l'échappement est relié hydrauliquement à plusieurs canaux d'échappement (66 à 70) dont les embouchures extérieures (71) associées à la chambre antérieure (6) du cylindre sont disposées en étant décalées dans la direction longitudinale du cylindre et dont les embouchures intérieures (72 à 76) peuvent être fermées par l'organe de fermeture (77) de la soupape de commande (65), cependant que l'organe de fermeture (77) ne libère à chaque fois qu'une embouchure intérieure ou une au moins, et que, dans ce dernier cas, l'embouchure intérieure reliée à l'embouchure extérieure qui est la plus éloignée de l'organe tournant peut être à chaque fois libérée la première, et par le fait que les embouchures extérieures (71) sont toutes plus éloignées de l'organe tournant que celle du canal de retour (19) de la deuxième soupape d'étranglement (18).
2. Ferme-porte selon la revendication 1, caractérisé par le fait que l'organe de fermeture de la soupape de commande (65) est réalisé sous la forme d'un organe de commande (77) qui peut coulisser et/ou tourner dans un perçage (78) du cylindre (2), et que les embouchures intérieures (72 à 76) des canaux d'échappement (66 à 70) peuvent être libérées individuellement ou l'une après l'autre par l'organe de commande.
3. Ferme-porte selon la revendication 2, caractérisé par le fait que l'organe de commande (77) peut coulisser dans la direction axiale de son perçage (78) et/ou qu'il peut y tourner, et qu'il est muni d'un bord de commande (81), d'une rainure de commande (83) ou similaire.
4. Ferme-porte selon la revendication 3, caractérisé par le fait que les embouchures intérieures (72 à 76) des canaux d'échappement (66 à 70) sont décalées dans la direction axiale du perçage (78), et que l'organe de commande (77) est au moins coulissant.
5. Ferme-porte selon la revendication 4, caractérisé par le fait que l'organe de commande (77) est muni d'un bord de commande (81), en particulier en forme de cercle, qui s'étend dans la direction de la périphérie, et que le perçage (78) destiné à l'organe de commande (77) est en communication, de préférence directement, avec le canal longitudinal de continuation (16) du boîtier.
6. Ferme-porte selon l'une au moins des revendications 2 à 5, caractérisé par le fait que l'organe de commande (77) peut être vissé dans un filetage (80) du perçage (78).
7. Ferme-porte selon l'une au moins des revendications 2 à 6, caractérisé par le fait que l'organe de commande (77) est monté dans le perçage (78) en pouvant coulisser, mais non tourner, et qu'il est accouplé par l'intermédiaire d'une liaison par vis à un organe d'actionnement qui est monté dans le perçage (78) en pouvant tourner, mais non coulisser.
8. Ferme-porte selon la revendication 2 ou 3, caractérisé par le fait que l'organe de commande (77) est monté dans le perçage (78) en pouvant tourner, mais non coulisser, et que les embouchures intérieures (72 à 76) des canaux d'échappement (66 à 70) sont ménagées en étant décalées au moins dans la direction de la périphérie, l'organe de commande (77) ou une partie en forme de goujon (82) de celui-ci s'étendant sur la région des embouchures intérieures et recouvrant celles-ci, et par le fait qu'est ménagée sur la surface latérale extérieure de l'organe de commande, ou de sa partie en forme de goujon (82), une rainure de commande (83) dont une extrémité est ouverte vers le canal longitudinal de continuation (16) du boîtier, la rainure de commande (83) pouvant être associée à chaque fois à une embouchure intérieure (72 à 76) par rotation de l'organe de commande (77).
9. Ferme-porte selon l'une au moins des revendications 2 à 8, caractérisé par le fait que les embouchures intérieures (72 à 76) sont disposées en étant décalées dans la direction axiale du perçage (78) et dans la direction de sa périphérie, en particulier le long d'une ligne hélicoïdale de la surface latérale des perçages.
10. Ferme-porte selon l'une au moins des revendications 2 à 7, caractérisé par un goujon de butée (82) à section transversale réduite qui fait saillie au-delà du bord de commande (81) vers le canal longitudinal de continuation (16) du boîtier.
11. Ferme-porte selon l'une au moins des revendications 2 à 10, caractérisé par des repères sur le cylindre (2) dans la région de l'embouchure extérieure du perçage (78) destiné à l'organe de commande (77), et par un index sur ce dernier ou sur son organe d'actionnement
EP88102261A 1987-03-27 1988-02-17 Ferme-porte Expired - Lifetime EP0285775B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8704569U 1987-03-27
DE8704569U DE8704569U1 (de) 1987-03-27 1987-03-27 Türschließer

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EP0285775A1 EP0285775A1 (fr) 1988-10-12
EP0285775B1 true EP0285775B1 (fr) 1991-05-15

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JP2854614B2 (ja) * 1989-07-21 1999-02-03 リョービ株式会社 ドアクローザ
TWI629405B (zh) 2017-07-18 2018-07-11 朕豪工業股份有限公司 關門器
GB2580013B (en) * 2018-09-28 2023-05-17 Assa Abloy Ltd Door-closer with overload valve

Citations (1)

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Publication number Priority date Publication date Assignee Title
DE8526660U1 (de) * 1985-09-18 1987-01-22 Gretsch-Unitas GmbH Baubeschläge, 7257 Ditzingen Türschließer

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DE259612C (fr) *
DE1301960B (de) * 1966-07-21 1969-08-28 Continental Elektro Ind Ag Einrichtung zur Betaetigung eines hydraulischen Motors mit einem Steuerschieber und Verblockventilen
DE2052325A1 (de) * 1970-10-24 1972-04-27 Mainz Gmbh Feinmech Werke Verfahren zur Umsetzung digitaler Eingangssignale in diskrete Ausgangspositionen oder in Geschwindigkeiten (Hydraulischer Schrittmotor)
DE2545616A1 (de) * 1971-08-25 1977-04-14 Daimler Benz Ag Hydraulischer positionierantrieb
US3951042A (en) * 1974-03-29 1976-04-20 Weiss Adolf F Apparatus for stroke control in high pressure machinery
FR2457401A1 (fr) * 1979-05-23 1980-12-19 Chrysler France Servo-moteur a commande par depression

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Publication number Priority date Publication date Assignee Title
DE8526660U1 (de) * 1985-09-18 1987-01-22 Gretsch-Unitas GmbH Baubeschläge, 7257 Ditzingen Türschließer

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DE8704569U1 (de) 1987-07-16
DE3862792D1 (en) 1991-06-20
EP0285775A1 (fr) 1988-10-12

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