EP0545624B1 - Ferme-porte de sol - Google Patents

Ferme-porte de sol Download PDF

Info

Publication number
EP0545624B1
EP0545624B1 EP92310782A EP92310782A EP0545624B1 EP 0545624 B1 EP0545624 B1 EP 0545624B1 EP 92310782 A EP92310782 A EP 92310782A EP 92310782 A EP92310782 A EP 92310782A EP 0545624 B1 EP0545624 B1 EP 0545624B1
Authority
EP
European Patent Office
Prior art keywords
piston
door
back check
action
speed
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
EP92310782A
Other languages
German (de)
English (en)
Other versions
EP0545624A3 (en
EP0545624A2 (fr
Inventor
Motoharu Yamane
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.)
Ryobi Ltd
Original Assignee
Ryobi Ltd
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
Priority claimed from JP10598791U external-priority patent/JP2557382Y2/ja
Priority claimed from JP10912991U external-priority patent/JP2557385Y2/ja
Application filed by Ryobi Ltd filed Critical Ryobi Ltd
Publication of EP0545624A2 publication Critical patent/EP0545624A2/fr
Publication of EP0545624A3 publication Critical patent/EP0545624A3/en
Application granted granted Critical
Publication of EP0545624B1 publication Critical patent/EP0545624B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
    • E05F3/10—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes with a spring, other than a torsion spring, and a piston, the axes of which are the same or lie in the same direction
    • 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
    • E05F3/225—Additional arrangements for closers, e.g. for holding the wing in opened or other position mounted at the bottom of wings, e.g. details related to seals, covers, connections to the wings, embedding in the floor
    • 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
    • E05Y2201/252—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
    • E05Y2600/00—Mounting or coupling arrangements for elements provided for in this subclass
    • E05Y2600/40—Mounting location; Visibility of the elements
    • E05Y2600/41—Concealed
    • 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
    • E05Y2600/00—Mounting or coupling arrangements for elements provided for in this subclass
    • E05Y2600/40—Mounting location; Visibility of the elements
    • E05Y2600/452—Mounting location; Visibility of the elements in or on the floor or wall
    • 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
    • E05Y2800/40—Physical or chemical protection
    • E05Y2800/414—Physical or chemical protection against high or low temperatures
    • 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 present invention relates to a floor hinge in which a door opening rotational force of a door is converted into a linear motion, a piston is moved while accumulating a return spring by a door opening action, and the piston is then returned to an original position by the accumulated force of the return spring.
  • the return speed of the piston is classified into four speeds by the action of a hydraulic pressure control circuit.
  • the four speed modes correspond to a delayed action, a first speed door closing action, a second speed door closing action and a latching action of the door, respectively.
  • EP-A-0407150 discloses a floor hinge for achieving four speed modes, i.e., a delayed action, a first speed door closing action, a second speed door closing action and a latching action.
  • a back check adjusting valve and a latching action adjusting valve are disposed in a first hydraulic passage for causing working oil within a piston rear chamber to flow into a piston front chamber
  • a first speed adjusting valve and a second speed adjusting valve are disposed in a second hydraulic passage for causing the working oil within the piston front chamber to flow into the piston rear chamber.
  • each member of the floor hinge may be broken. If a safety mechanism is provided to avoid the breakage of a sealing portion of the floor hinge, such a safety mechanism must be provided on the piston to make the piston bulky and complicated and to make troublesome the working operation of the piston.
  • an object of the present invention is to provide a floor hinge which may perform a door closing action concomitant with a delaying action, a first speed door closing action, a second speed door closing action and a latching action of the door and in which the four speeds modes may be adjusted independently of each other.
  • Another object of the present invention is to provide a floor hinge which can ensure a slow door opening operation within a range from a predetermined door opening angle to the maximum door opening angle and which has a back check mechanism functioning in such a manner that a piston motion is locked when the door is opened rapidly under the influence of a door opening force lower than a predetermined strength, and a piston motion is performed gradually.
  • Preferred embodiments of the invention satisfy the above-mentioned objects.
  • the output shaft is rotated, and the piston is moved toward the piston rear chamber while compressing the return spring by the rotational motion-linear motion converting mechanism so that the door is opened at a maximum door opening angle (for example, 120°) which is predetermined.
  • a maximum door opening angle for example, 120°
  • the check valve disposed in the first hydraulic passage is opened by the increase of working oil pressure within the piston rear chamber, the working oil within the piston rear chamber flows through the first hydraulic passage into the piston front chamber for ensuring the movement of the piston.
  • the bypass passage throttle means operates to ensure a slow retracted motion of the back check piston.
  • the piston When the door opening force is released at the door maximum opening angle, the piston is returned toward the piston front chamber by the returning force of the spring. At this time, the check valve disposed in the first hydraulic passage is closed by the increase of the working oil pressure of the piston front chamber.
  • the delaying action in the range of the door opening angle of, for example, 120 to 75°
  • the working oil within the piston front chamber will be able to flow into the piston rear chamber through the second hydraulic passage and the delayed action adjusting valve.
  • the first speed door closing action in the range of the door opening angle of, for example, 75 to 25°
  • the working oil within the piston front chamber will flow into the piston rear chamber through the second hydraulic passage and the first speed adjusting valve.
  • the working oil within the piston front chamber will flow into the piston rear chamber through the third hydraulic passage and the second speed adjusting valve.
  • the latching action in the range of the door opening angle of, for example, 5 to 0°
  • the working oil within the piston front chamber will flow into the piston rear chamber through the third hydraulic passage and the latching action adjusting valve.
  • the return motion of the piston is the four-speed mode corresponding to the restrictions of the delaying action adjusting valve, the first speed adjusting valve, the second speed adjusting valve and the latching action adjusting valve.
  • the returning motion of the piston is transmitted to the output shaft in the four-speed modes by the rotational motion-linear motion converting mechanism so that the door is closed in the order of the delayed action, the first speed door closing action, the second speed door closing action and the latching action.
  • the floor hinge may be applied to any type of a right swing door, a left swing door and a biparting door.
  • the floor hinge includes an output shaft 1 connected to the door and serving as a rotary shaft of the door and a main piston 3 connected to the output shaft 1 by a rotational motion-linear motion converting mechanism A which uses a cam mechanism.
  • the piston 3 is reciprocatingly moved by the rotation of the output shaft 1 in response to the door opening action to thereby compress a return spring 2. Then, the piston is returned back to the original position (door closing position) by the returning force of the return spring 2 to thereby transmit the door closing force to the output shaft 1 through the rotational motion-linear motion converting mechanism A.
  • the moving speed of the piston during the door closing action is subjected to a speed control by controlling a flow rate of the working oil of the piston front chamber 4 to a piston rear chamber 5 through a hydraulic control circuit B in the following order.
  • a delaying (hereinafter "delayed") action for a extremely low speed door closing action is performed.
  • a door closing action range of the door opening angle of 75° to 25° i.e., a door closing action process from FIG. 2B to FIG.
  • a first speed door closing action for a high speed door closing operation is performed.
  • a second speed door closing action for a slow door closing action is performed.
  • a latching action is performed for a high speed door closing action to close and latch the door.
  • the rotational motion-linear motion converting mechanism A is brought into contact with a back check piston 16 receiving a biasing force of a back check spring 17.
  • the back check piston 16 causes the back check spring 17 to be compressed retracted. Accordingly, a check valve 34 for the back check is not closed.
  • the returning action of the piston 3 is ensured and the door may be opened up to a maximum door opening angle. In the case where the door is opened quickly, since the check valve 34 for the back check is closed, the back check piston 16 is not retracted.
  • a back check hydraulic pressure control circuit C having a back check safety valve 36 causes the working oil within a back check cylinder 19b to escape into the piston rear chamber 5, thus ensuring the retraction of the back check piston 16 and avoiding the load imposed onto the output shaft 1 and a stationary portion of the door.
  • the floor hinge has a body case 19.
  • the body case 19 is in the form of a longitudinal flat cylindrical shape and has, on its right end side, a main piston cylinder 19a which is liquid tightly sealed by a cylinder head for accommodating and, on its left side, the back check cylinder 19b which is liquid tightly sealed by a back check cylinder head 21.
  • the back check cylinder 19b has, on its upper side, an opening which is liquid tightly closed by a lid plate 22 with the output shaft 1 projecting therethrough.
  • the main piston 3 is received in the cylinder 19a.
  • the back check cylinder 19b receives the back check piston 16 slidably.
  • the piston front chamber 4 is defined between the piston 3 and the cylinder head 20.
  • the piston rear chamber 5 is in fluid communication with the back check cylinder 19b through a bypass passage 35.
  • the output shaft 1 is supported by a bearing 18 provided at a bottom of the body case 19 and a bearing 23 provided on the lid plate 22.
  • a leaf shaped cam 24 is fixed within the body case 19.
  • the output shaft 1 is fixedly inserted to an arm lever (not shown) fixed, at its outer end, to a lower end of the door (not shown).
  • the cam 24 is interposed between an upper swing plate 25 and a lower swing plate 26.
  • Three cam followers 27, 28 and 29 are pivotally supported between the upper and lower swing plates 25 and 26 which clamp a proximal end of a connecting rod 30 on the side of the piston 3, and the swing plates 25 and 26 are fixed by fastening screws 38.
  • the connecting rod 30 is coupled, at its distal end, to a piston pin 37 which is inserted through a circumferential surface of the piston 3 into a recess formed in the rear side of the piston 3.
  • the cam 24 is arranged with its apex being directed to the piston 3 and being aligned with the longitudinal direction of the body case 19 when the door is fully closed.
  • the two cam followers 27 and 28 are located on the side of the check piston 16 relative to the cam 24 so that the two cam followers may be brought into contact with both shoulder portions, having the smallest radius, of the cam 24 when the door is full-closed, whereas the remaining one 29 of the cam followers is located with a predetermined interval relative to the cam 24 on the side of the piston 3.
  • the rotational motion-linear motion converting mechanism A is thus constructed by utilizing the cam and cam followers.
  • the return spring 2 is disposed in a compressed state within the body case 19 so as to surround the connecting rod 30 and is interposed between the piston located corresponding to the fully closed condition of the door and a stepped portion 19c formed in the body case 19.
  • the back check piston 16 is urged by the back check spring 17 received in the compressed state within the back check cylinder 19b.
  • An opening o is formed on a bottom of the body case 19 below the lower swing plate 26.
  • a diaphragm packing 31 is applied to a stepped portion, directed downwardly, of an edge of the opening, thereby fluid-tightly closing the interior of the case body 19 with a cup-shaped plug 32.
  • the diaphragm packing 31 is deformed inwardly to function to avoid a damage of the body case 19 in the case where the working oil within the piston rear chamber 5 is expanded due to an accidental elevation of the temperature.
  • the working oil is filled in the body case 19 by overturning the body case 19 and removing the cup-shaped plug 3 and the diaphragm packing 31.
  • the hydraulic control circuit B includes: a first hydraulic passage 7 formed between the piston front chamber 4 and the piston rear chamber 5 in an end wall of the piston 3 with the check valve 6 being arranged in a predetermined position for ensuring the door closing/opening operation; a second hydraulic passage 11 formed in wall of the cylinder in the form of plural branches for ensuring the delayed action (i.e., the door opening process ranging from the maximum door opening angle of 120° shown in FIG. 2a to the door opening angle 75° shown in FIG. 2b) and the first speed door closing operation (i.e., the door closing process ranging from the door opening angle of 75° shown in FIG. 2A to the door opening angle 25° shown in FIG.
  • the delayed action i.e., the door opening process ranging from the maximum door opening angle of 120° shown in FIG. 2a to the door opening angle 75° shown in FIG. 2b
  • the first speed door closing operation i.e., the door closing process ranging from the door opening angle of 75° shown in FIG. 2A to the door opening angle 25
  • the second speed door closing operation i.e., the door closing process ranging from the door opening angle of 25° shown in FIG. 2C to the door opening angle of 5° shown in FIG. 2C
  • the latching action i.e., the door closing process from the door opening angle of 5° shown in FIG. 2C to the door opening angle of 0° shown in FIG. 2E.
  • valve body (ball) 6a is separated away from its valve seat 6b by the increased pressure of the working oil within the piston rear chamber 5 during the door opening operation, allowing the working oil to flow into the piston front chamber 4 and also serves to interrupt the flow of the working oil in the reverse direction during the door closing operation.
  • the valve body 6a is maintained in the passage 7 by a plurality of projection 6c extended radially.
  • the passage 7 is communicated with a space 3a provided in the piston 3.
  • One end of the connecting rod 30 is inserted into the space 3a.
  • the second hydraulic passage 11 is formed, in the wall of the case 19, in the form of plural branches composed of a main passage 11a and four branch passages 11b (first branch), 11c second branch), 11d (third branch) and 11e (fourth branch) (FIGS. 1a and 3).
  • Oil ports a (second) and b (first) of the branch passages 11b and 11c face the piston front chamber 4 at predetermined positions, and oil ports a ' (fourth) and b '(third) of the branch passages 11d and 11e face the rear piston chamber 5 at predetermined positions.
  • the first and second branch passages 11b and 11c are disposed close to each other and the third and fourth branch passages 11d and 11e are disposed close to each other.
  • the first and second branch passages 11b and 11c are disposed in front position of the main piston cylinder 19a and the third and fourth branch passages 11d and 11e are disposed in a rear position of the main piston cylinder 19a.
  • the oil ports a (second) and a ' (fourth) are in fluid communication with each other, and the oil port b ' (third) is closed by the piston 3 so that the communication between the ports b and b ' is interrupted.
  • the oil ports b and b' are in fluid communication with each other and the oil port a is closed by the piston 3 so that the communication between the oil ports a and a ' is interrupted.
  • a delayed action adjusting valve 9 which is adjustable from the outside is provided to face the oil port a' (FIG. 3).
  • a first speed adjustment valve 10 which is adjustable from the outside is provided to face the oil port b .
  • the delayed action adjusting valve 9 and the first speed adjusting valve 10 are arranged so that they would not interfere with each other.
  • the restriction of the delayed action adjusting valve 9 is adjusted to a large level in a predetermined manner.
  • the restriction of the first speed adjusting valve 10 is adjusted to a small level in a predetermined manner.
  • the third hydraulic passage 15 is formed in the cylinder wall in the form of plural branches composed of a main passage 15a and four branch passages 15b (first), 15c (second), 15d (third) and 15e (fourth) and is offset from the second hydraulic passage 11 toward the cylinder head 20.
  • first and second branch passages 15b and 15c are deviated from the first and second branch passages 11b and 11c of the second hydraulic passage 11 toward the cylinder head 20.
  • a pair of third and fourth branch passages 15d and 15e are also deviated from the third and fourth branch passages 11d and 11e of the second hydraulic passage 11 toward the cylinder head 20.
  • Oil ports c (second) and d (first) of the passages 15b and 15c face the piston front chamber 4 at predetermined positions.
  • Oil ports c ' (fourth) and d ' (third) of the passages 15d and 15e face the piston rear chamber 5 at predetermined positions.
  • the oil ports c and c ' are in fluid communication with each other, and the oil port d ' is closed by the piston 3 so that the fluid communication between the ports d and d ' is interrupted. Also, in the latching action from the door opening angle of 5° to the door opening angle of 0°, the oil ports d and d ' are in fluid communication with each other, and the oil port c is closed by the piston so that the fluid communication between the ports c and c ' is interrupted.
  • a second speed adjusting valve 13 which may be adjusted from the outside is disposed to face the oil port c ', and a latching action adjusting valve 14 which may be adjusted from the outside is disposed to face the oil port d (FIG.4).
  • the second speed adjusting valve 13 and the latching action adjusting valve 14 are adjusted so that they would not interfere with each other.
  • the restriction of the second adjusting valve 13 is adjusted to a large level in a predetermined manner.
  • the restriction of the latching action adjusting valve 14 is adjusted to a small level in predetermined manner. As shown in FIGS.
  • the branch passages 11d and 15e are open to the piston front chamber 4 at the same height position so as to be opposed to each other, and the branch passages llc and 15d are open to the piston front chamber 4 at the same height position so as to be opposed to each other.
  • the pair of the branch passages lld and 15e are disposed at a position higher than that of the pair of the branch passages 11c and 15d.
  • the back check piston 16 is slidingly inserted into the back check cylinder 19b.
  • the back check piston 16 is biased to move in an axial direction toward the output shaft 1 by means of the back check spring 17 disposed in the back check cylinder 19b.
  • a fourth hydraulic passage 33 is formed in the end face of the back check piston 16.
  • a check valve 34 for the back check is disposed in the fourth hydraulic passage 33.
  • the check valve 34 prevents the working oil, held in the back check cylinder 19b, form flowing into the piston rear chamber 5.
  • a fifth hydraulic passage 35 (bypass) is formed in the wall of the back check cylinder 19b to communication the back check cylinder 19b with the piston rear chamber 5.
  • a back check safety valve 36 is disposed in the fifth hydraulic passage 35.
  • the back check safety valve 36 is provided so that a spherical valve body 36c is seated on a valve seat 19g by the spring force of a coil spring 36b (see FIG. 7) compressed by a screw plug 36a which may be adjusted from the outside by means of a screw driver, to close the fifth hydraulic passage 35.
  • the back check safety valve 36 is opened.
  • a back check safety valve having the same structure as the first speed adjusting valve 10 may be used.
  • the working oil filled in the piston front chamber 4 will be introduced into the second hydraulic passage 11 from the oil port a and may flow into the piston rear chamber 5 from the oil port a ' through the delayed action adjusting valve 9 which is provided to face the oil port a ' and which may be adjusted to have a restriction at a high level.
  • the oil ports b and b ' of the second hydraulic passage 11 are only in fluid communication with each other, the oil is introduced into the second hydraulic passage 11 from the oil port b and may flow into the piston rear chamber 5 from the oil port b' of the second hydraulic passage 11 from the first speed adjusting valve 10 which is provided so as to face oil port b and which has a restriction at a low level.
  • the oil ports c and c' of the third hydraulic passage 15 are only in fluid communication with each other, the oil will flow into the third hydraulic passage 15 through the oil port c and will flow into the piston front chamber 4 from the oil port c' through the second speed adjusting valve 13 which is provided so as to face the oil port c' and which may have a restriction at a predetermined high level.
  • the oil may flow into the third hydraulic passage 15 from the oil port d and will flow into the piston front chamber 4 from the oil port d' through the latching action adjusting valve 14 which is provided to face the oil port d and which may be adjusted to a low restriction.
  • the return movement of the piston 3 is classified into four-speed modes which correspond to the delayed action adjusting valve 9, the first speed adjusting valve 10, the second speed adjusting valve 13 and the latching action adjusting valve 14, respectively. The movement is converted into the adjusted return rotation of the output shaft 1 through the rotational motion-linear motion converting mechanism A.
  • the door may conduct respective actions such as the delayed action where the speed is kept at a low level, the first speed closing door action where the speed is kept at a high level, the second speed door closing action where the speed is kept at a low level and the latching action where the speed is kept at a remarkably low level in this order.
  • the back check valve 34 is kept opened, so that the working oil within the back check cylinder 19b may flow into the piston rear chamber 5 through the fourth hydraulic passage 33 and the back check valve 34.
  • the back check piston 16 may be retracted in the left direction while compressing the back check spring 17.
  • the back check valve 34 is not closed.
  • the movement of the piston 3 is effected so that the door is opened at the maximum door opening angle.
  • the pressure of the working oil within the back check cylinder 19b is increased, and the check valve 34 for back check provided in the back check piston 16 is closed.
  • the piston 16 will not be retracted due to the pressure of the working oil within the back check cylinder 19b.
  • the speed of the piston 3 is decelerated to stop, thereby terminating the door opening operation and avoiding the quick fully opening of the door so that it is possible to avoid the damage of components such as a glass member provided on the door.
  • the back check safety valve 36 interposed in the fifth hydraulic passage 35 is opened and the working oil within the back check cylinder 19b will escape into the piston rear chamber 5 through the fifth hydraulic passage 35 formed in the wall of the back check cylinder 19b. Even if the back check valve 34 is closed, it is possible to ensure the retraction of the back check piston 16. During the retraction of the back check piston 16, the back check safety valve 36 is opened and closed in response to the pressure of working oil in the back check cylinder 19b. Thus, the back check force is decelerated to avoid the over load imposed on the stationary parts of the door and the output shaft 1 and to avoid a damage of the floor hinge components such as the hinge case and door components.
  • a back check adjusting valve may be used instead of the back check safety valve 36.
  • the throttling level of the valve is determined at a high level so that the back check valve 34 is closed due to the pressure increase of the working oil in the back check cylinder 19b when the door is blown to the full-open angle.
  • the working oil in the back check cylinder 19b flows into the piston rear chamber 5 through the back check adjusting valve to ensure the retraction of the back check piston 16.
  • the working oil within the piston rear chamber will flow into the piston front chamber through the first hydraulic passage formed in the piston.
  • the working oil within the piston front chamber will flow into the piston rear chamber only through the second hydraulic passage formed in the cylinder wall and the delayed action adjusting valve.
  • the working oil within the piston front chamber will flow into the piston rear chamber only through the second hydraulic passage formed in the cylinder wall and the first speed adjusting valve.
  • the working oil within the piston front chamber will flow into the piston rear chamber only through the second hydraulic passage formed in the cylinder wall and the first speed adjusting valve.
  • the working oil within the piston front chamber will flow into the piston rear chamber only through the third hydraulic passage formed in the cylinder wall and the second speed adjusting valve.
  • the fourth stage action for closing the door i.e., the latching action
  • the working oil within the piston front chamber will flow into the piston rear chamber only through the third hydraulic passage and the latching action adjusting valve.
  • the rotational motion-linear motion converting mechanism abuts against the back check piston.
  • the back check valve is kept open, and the back check piston can be retracted because the working oil in the back check cylinder can flow into the piston rear chamber to cause the door to be fully opened.
  • the back check valve is closed, the door opening motion is stopped.
  • the back check safety valve is operated to avoid the breakage of each element of the floor hinge.

Landscapes

  • Closing And Opening Devices For Wings, And Checks For Wings (AREA)

Claims (8)

  1. Un ferme-porte de sol comportant un arbre de sortie (1) relié à une porte et servant d'arbre rotatif de ladite porte, un mécanisme (A) de conversion de mouvement rotatif en mouvement linéaire pour convertir un mouvement rotatif de l'arbre de sortie (1) en un mouvement linéaire, un piston principal (3) reçu coulissant de manière étanche dans un boîtier (19) et relié audit arbre de sortie (1) par le mécanisme (A) de conversion de mouvement rotatif en mouvement linéaire pour contrôler le mouvement rotatif de l'arbre de sortie (1), un ressort de rappel (2) destiné à être déformé par le mouvement rotatif de l'arbre de sortie (1) sous l'effet d'une action d'ouverture de porte et pour accumuler une force de ressort en réponse au mouvement du piston principal, la force de ressort étant telle qu'elle ramène le piston principal à la position de fermeture de porte, et un circuit de commande hydraulique pour exercer une action de retardement de fermeture de porte à une vitesse extrêmement faible dans la plage allant d'un angle d'ouverture maximale de la porte à un angle prédéterminé de fermeture de la porte, une action de fermeture de porte à une première vitesse pour fermer la porte à une vitesse élevée, une action de fermeture de porte à une seconde vitesse pour fermer la porte à une vitesse faible, et une action de verrouillage pour fermer la porte à une vitesse extrêmement faible au voisinage de son état complètement fermé pour verrouiller la porte, caractérisé en ce que ledit circuit de commande hydraulique comprend :
    un premier passage hydraulique (7) formé dans ledit piston (3) pour faire communiquer entre elles une chambre (4) à l'avant du piston et une chambre (5) à l'arrière du piston, et dans lequel est montée une soupape de retenue (6) pour permettre à l'huile de travail de la chambre (5) à l'arrière du piston de circuler vers la chambre (4) à l'avant du piston pendant une action d'ouverture de porte, mais en empêchant l'huile de travail de circuler en sens inverse pendant une action de fermeture de porte ;
    un second passage hydraulique (11) formé dans ledit boîtier (19) d'une série de branches (11b, 11c, 11d, 11e) communiquant avec un passage principal commun (11a) pour commuter la communication entre la chambre (4) à l'avant du piston et la chambre (5) à l'arrière du piston au moyen d'orifices faisant communiquer chaque branche avec le cylindre de piston principal (19a), lesquels orifices sont sélectivement ouverts et fermés par ledit piston (3) en réponse au mouvement du piston (3) dans le boîtier (19) pendant ladite action de retardement de fermeture de porte et ladite action de fermeture de porte à la première vitesse, respectivement, ledit second passage hydraulique (11) comprenant une soupape de réglage d'action de retardement (9) et une soupape de réglage de première vitesse (10) montées dans des branches séparées de manière que la soupape de réglage correspondante règle exclusivement l'écoulement dans la partie correspondante du second passage hydraulique (11) en faisant alors communiquer entre elles la chambre à l'avant du piston et la chambre à l'arrière du piston pendant ladite action de retardement de fermeture de porte et pendant l'action de fermeture de porte à la première vitesse, respectivement ; et
    un troisième passage hydraulique (15) formé dans ledit boîtier (19) par une série de branches (15b, 15c, 15d, 15e) communiquant avec un passage principal commun (15a) pour commuter la communication entre la chambre (4) à l'avant du piston et la chambre (5) à l'arrière du piston en utilisant des orifices faisant communiquer chaque branche avec le cylindre de piston principal (19a), lesquels orifices sont sélectivement ouverts et fermés par ledit piston (3) en réponse au mouvement du piston (3) dans le boîtier (19) pendant ladite action de fermeture de porte à la seconde vitesse et ladite action de verrouillage, respectivement, ledit troisième passage hydraulique (15) comprenant une soupape de réglage de seconde vitesse (13) et une soupape de réglage de l'action de verrouillage (14) placées dans des branches séparées de manière que la soupape de réglage correspondante agisse pour régler exclusivement l'écoulement dans la partie correspondante du troisième passage hydraulique (15) faisant alors communiquer entre elles la chambre à l'avant du piston et la chambre à l'arrière du piston pendant ladite action de fermeture à la seconde vitesse et pendant ladite action de verrouillage de fermeture de porte, respectivement.
  2. Un ferme-porte de sol selon la revendication 1, dans lequel ledit premier passage hydraulique (7) communique avec un espace prévu dans le piston principal (3) pour recevoir une extrémité d'une bielle de liaison (30) qui fait partie du mécanisme de conversion de mouvement rotatif en mouvement linéaire.
  3. Un ferme-porte de sol selon la revendication 1, dans lequel les second et troisième passages hydrauliques (11, 15) sont formés indépendamment l'un de l'autre dans une paroi du cylindre de piston principal destiné à recevoir en coulissement le piston principal (3).
  4. Un ferme-porte de sol selon la revendication 3, dans lequel le second passage hydraulique (11) comprend des première, seconde, troisième et quatrième branches (11b, 11c, 11d, 11e) qui sont disposées, dans cet ordre, à partir de la chambre (4) à l'avant du piston, la première branche (llb) comportant une soupape de réglage de première vitesse (10), la quatrième branche (11e) comportant une soupape de réglage d'action de retardement (9).
  5. Un ferme-porte de sol selon la revendication 3, dans lequel le troisième passage hydraulique (15) comprend des première, seconde, troisième et quatrième branches (15b, 15c, 15d, 15e) qui sont disposées, dans cet ordre, à partir de la chambre (4) à l'avant du piston, la première branche (15b) comportant une soupape de réglage de l'action de verrouillage (14), la quatrième branche (15e) comportant une soupape de réglage de seconde vitesse (13).
  6. Un ferme-porte de sol selon la revendication 3, dans lequel le troisième passage hydraulique (15) est décalé par rapport au second passage hydraulique (11) vers une culasse (20) du cylindre de piston principal (19a).
  7. Un ferme-porte de sol selon l'une quelconque des revendications précédentes, comprenant un mécanisme de frein pour décélérer la vitesse d'ouverture de la porte dans une plage allant d'un angle d'ouverture de porte prédéterminé à l'angle maximal d'ouverture de porte ;
    ledit mécanisme de frein comprenant :
    un cylindre de frein (19b) prévu dans une position à l'opposé du piston (3) par rapport au mécanisme (A) de conversion de mouvement rotatif en mouvement linéaire ;
    un piston de frein (16) ;
    un élément élastique (17) pour solliciter le piston de frein (16) vers l'arbre de sortie (1) ;
    un passage hydraulique de frein (33) formé dans le piston de frein (16), dans lequel est montée une soupape de retenue (34) pour fermer le passage hydraulique de frein (33) quand la porte est ouverte rapidement, et pour amener le mécanisme (A) de conversion de mouvement rotatif en mouvement linéaire en contact avec le piston de frein (16) afin de faire rentrer ainsi le piston de frein (16) ;
    un passage de dérivation de frein (35) pour faire communiquer le cylindre de frein (19a) avec la chambre (5) à l'arrière du piston ; et
    un moyen de restriction de frein (35) pour commander l'huile de travail dans le passage de dérivation de frein (35).
  8. Un ferme-porte de sol selon la revendication 7, dans lequel le moyen de restriction de frein (35) comprend une soupape de sûreté (36) ou une soupape de réglage.
EP92310782A 1991-11-29 1992-11-25 Ferme-porte de sol Expired - Lifetime EP0545624B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP10598791U JP2557382Y2 (ja) 1991-11-29 1991-11-29 フロアーヒンジ
JP105987/91U 1991-11-29
JP10912991U JP2557385Y2 (ja) 1991-12-10 1991-12-10 フロアーヒンジ
JP109129/91U 1991-12-10

Publications (3)

Publication Number Publication Date
EP0545624A2 EP0545624A2 (fr) 1993-06-09
EP0545624A3 EP0545624A3 (en) 1993-09-22
EP0545624B1 true EP0545624B1 (fr) 1997-01-22

Family

ID=26446201

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92310782A Expired - Lifetime EP0545624B1 (fr) 1991-11-29 1992-11-25 Ferme-porte de sol

Country Status (2)

Country Link
EP (1) EP0545624B1 (fr)
DE (1) DE69217008T2 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102159787B (zh) * 2008-09-15 2014-07-30 Sca卫生用品公司 铰链装置
WO2010033044A1 (fr) * 2008-09-18 2010-03-25 Vladimir Miletic Fermeture de porte
ME01877B (me) 2010-09-06 2014-12-20 In & Tec Srl Šarka za zatvaranje vrata, poželjno staklena vrata
EP3483373B1 (fr) * 2017-11-14 2021-01-27 dormakaba Deutschland GmbH Ferme-porte
CN108505864B (zh) * 2018-05-10 2024-01-23 东莞力督门控设备有限公司 油压式铰链关门装置
GB2580013B (en) * 2018-09-28 2023-05-17 Assa Abloy Ltd Door-closer with overload valve
EP3875719A1 (fr) 2020-03-06 2021-09-08 Abloy Oy Ferme-porte à actionnement de cames
CN112377064B (zh) * 2020-11-05 2022-05-03 重庆鑫洲人防工程设备有限公司 一种胶管式防爆波人防门

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2161293A1 (de) * 1971-12-10 1973-06-14 Dorma Baubeschlag Selbsttaetiger tuerschliesser
JPH0755254Y2 (ja) * 1989-07-06 1995-12-20 リョービ株式会社 フロアーヒンジの油圧制御機構
JP2854614B2 (ja) * 1989-07-21 1999-02-03 リョービ株式会社 ドアクローザ

Also Published As

Publication number Publication date
EP0545624A3 (en) 1993-09-22
DE69217008D1 (de) 1997-03-06
DE69217008T2 (de) 1997-05-28
EP0545624A2 (fr) 1993-06-09

Similar Documents

Publication Publication Date Title
EP0409445B1 (fr) Ferme-porte
US5385218A (en) Rack and pinion pneumatic actuator with counter-pressure control and damping device
US5572919A (en) Apparatus for controlling pressure in a cylinder chamber of a hydraulic pump-motor
US20070067950A1 (en) Door closer
CA2029257C (fr) Mecanisme de butee automatique
US6151753A (en) Door closer to generate a sudden change in the transmission ratio during the closing phase
EP0545624B1 (fr) Ferme-porte de sol
US3595264A (en) Load control and holding valve
US4564169A (en) Fluid actuator for stepwise regulation of valves
US6260236B1 (en) Door closer with hydraulic back checking
CA1169742A (fr) Distributeur hydraulique regenerateur
JP2603868B2 (ja) カウンタバランス弁
EP1159503B1 (fr) Ferme-porte
JPH01216106A (ja) 流体安全制動弁装置
GB2330869A (en) Movable member : fluid-pressure mover : pressure control
GB2054734A (en) Pneumatic door actuators
US5235896A (en) Hydraulic cylinder/piston mechanism
JP2557382Y2 (ja) フロアーヒンジ
EP0255781A2 (fr) Mécanisme d'actionnement pour porte
JP2557385Y2 (ja) フロアーヒンジ
GB2210678A (en) Control system for a hydraulic lift
CA2440171A1 (fr) Clapet de commande pour liquide
JPH07317428A (ja) 扉開閉装置
EP0939242B1 (fr) Dispositif commandant le mouvement
JP2004138245A (ja) 無段階型ロック装置

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

17P Request for examination filed

Effective date: 19930720

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB

17Q First examination report despatched

Effective date: 19951012

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REF Corresponds to:

Ref document number: 69217008

Country of ref document: DE

Date of ref document: 19970306

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: 746

Effective date: 19980702

REG Reference to a national code

Ref country code: FR

Ref legal event code: D6

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

Ref country code: GB

Payment date: 20001117

Year of fee payment: 9

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

Ref country code: FR

Payment date: 20001127

Year of fee payment: 9

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

Ref country code: DE

Payment date: 20001128

Year of fee payment: 9

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

Ref country code: GB

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

Effective date: 20011125

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: DE

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

Effective date: 20020702

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20011125

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

Ref country code: FR

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

Effective date: 20020730

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST