CN110965883B - Door closer with overload valve - Google Patents

Door closer with overload valve Download PDF

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Publication number
CN110965883B
CN110965883B CN201910939579.0A CN201910939579A CN110965883B CN 110965883 B CN110965883 B CN 110965883B CN 201910939579 A CN201910939579 A CN 201910939579A CN 110965883 B CN110965883 B CN 110965883B
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CN
China
Prior art keywords
door
chamber
piston
valve
door closer
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Active
Application number
CN201910939579.0A
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Chinese (zh)
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CN110965883A (en
Inventor
S·吉布斯
S·L·诺科特
B·P·麦卡锡
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Assa Abloy AB
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Assa Abloy AB
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Publication of CN110965883A publication Critical patent/CN110965883A/en
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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
    • E05F3/04—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
    • E05F3/102—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 with rack-and-pinion transmission between driving shaft and piston within the closer housing
    • 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
    • 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
    • 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

Landscapes

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

Abstract

The invention relates to a door closer, comprising: a first chamber and a second chamber in fluid communication via a main valve, the first chamber being defined by a piston, the piston being movable between a door open position in which the first chamber has a first volume and a door closed position in which the first chamber has a second volume, the first volume being greater than the second volume, and an overload valve configured such that if the pressure within the first chamber exceeds a threshold pressure, the overload valve allows fluid communication between the first chamber and the second chamber, wherein the piston has a protruding head and the first chamber has a corresponding recess on an opposite side of the protruding head, wherein in the door closed position the protruding head is at least partially received in the corresponding recess, the overload valve is at the protruding head of the piston.

Description

Door closer with overload valve
Technical Field
The present invention relates to door closers. More particularly, but not exclusively, the present invention relates to a door closer with an overload valve.
Background
The door may be coupled with a door closer to enable the door to be biased toward a closed position. The door closer of the prior art comprises a spring biasing the door closer to a "door closed" position, and a hydraulic arrangement ensuring a controlled movement of the door closer between a "door open" position and a "door closed" position. In such door closers, controlled movement is achieved by controlling the rate at which hydraulic fluid moves between chambers located within the door closer as the door closer moves between "door open" and "door closed" positions.
There may be circumstances where it is desirable to force a door coupled with a door closer to move from an open position to a closed position at a faster rate than the door would be closed under control of the door closer alone. If the door closer is forced to move from the door open position to the door closed position, the pressure of the hydraulic fluid within the door closer may increase to a level that causes damage to the internal components of the door closer. Known door closers, such as the door closers disclosed in GB 2323125A, provide an overload valve, also known as a check valve, configured to attenuate the accumulation of hydraulic pressure in such a case. However, even with such an overload valve, the hydraulic pressure within the door closer may still reach a level that results in damage when the door to which the door closer is attached is forced closed.
The present invention seeks to alleviate the above problems.
Disclosure of Invention
The present invention provides a door closer comprising: a first chamber and a second chamber in fluid communication via a main valve, the first chamber being defined by a piston, the piston being movable between a door open position in which the first chamber has a first volume and a door closed position in which the first chamber has a second volume, the first volume being greater than the second volume, and an overload valve configured such that if the pressure within the first chamber exceeds a threshold pressure, the overload valve allows fluid communication between the first chamber and the second chamber, wherein the piston has a protruding head and the first chamber has a corresponding recess on an opposite side of the protruding head, wherein in the door closed position the protruding head is at least partially received in the corresponding recess, the overload valve is at the protruding head of the piston.
The threshold pressure may be greater than 100 newton meters. The threshold pressure may be 120 newton meters.
With this configuration, it has been observed that when the forcing piston is changed from the door open position to the door closed position, the fluid pressure required to engage the overload valve may be locally reached at the overload valve port, while the fluid pressure is lower elsewhere in the first chamber. Thus, the overload valve may be engaged to move fluid from the first chamber into the second chamber via the overload valve while subjecting the door closer components elsewhere in the first chamber to lower pressures than are typical in known door closers.
The door closer may comprise a biasing arrangement, such as a spring, arranged to bias the door closer towards the door closed position. The pressure exerted by the biasing arrangement on the first chamber is preferably less than the threshold pressure required to open the overload valve.
The protruding end portion may have a length and the recess may have a depth, the length of the protruding end portion being substantially equal to the depth of the recess. Such an arrangement allows the protruding end to be at least partially and possibly completely received within the recess.
The volume of the first chamber (second volume) may be minimal when the door closer is in the door closed position. The volume of the second chamber may be maximized when the door closer is in the door closed position.
The protruding end of the piston may be cylindrical and the corresponding recess may also be cylindrical. The first chamber, the second chamber and the piston may be substantially cylindrical, and the protruding end portion of the piston and the corresponding recess may also be cylindrical, having a diameter smaller than the diameters of the first chamber and the second chamber. The protruding end of the piston may be cubical and the corresponding recess may also be cubical. The first chamber, the second chamber and the piston may be substantially cubical, and the protruding end portion of the piston and the corresponding recess may also be cubical, having dimensions smaller than those of the first chamber and the second chamber.
The protruding end portion may have an end face, and the corresponding recess may have an end face that is flat, concave or convex. The shape of the end face of the protruding end portion and the corresponding recess may be arranged to further increase the local pressure exerted on the overload valve. For example, the end face of the protruding end portion may be convex, and the end face of the corresponding recess may be concave, such that the convex end face and the concave end face are substantially the same shape.
The overload valve may be centered on an end face of the protruding end portion of the piston. Positioning the overload valve in the center of the end face of the protruding end portion of the piston may further increase the local pressure exerted on the overload valve.
The length of the end of the protrusion may be greater than 10% of the distance between the first end and the second end of the first chamber when the piston is in the door open position. The length of the end of the protrusion may be greater than 15% of the distance between the first end and the second end of the first chamber when the piston is in the door open position. The length of the ends of the protrusions may be greater than 5 mm.
The main valve may be configured to be capable of being closed such that substantially no fluid is capable of moving between the first chamber and the second chamber via the main valve. Such an arrangement may allow the door closer to hold the door in the door open position. The door closer may be an electro-hydraulic door closer and the main valve may be configured to close in response to the presence of an electric field. This arrangement may allow the door retainer to hold the door in the door open position by generating an electric field and allow the door closer to close the door by removing the electric field. This arrangement may be used to allow the door to be automatically closed during a fire alarm.
According to a second aspect, the present invention provides a door closer comprising: a first chamber and a second chamber in fluid communication via a main valve, the first chamber being defined by a piston, the piston being movable between a door open position in which the first chamber has a first volume and a door closed position in which the first chamber has a second volume, the first volume being greater than the second volume, and an overload valve configured such that if a pressure within the first chamber exceeds a threshold pressure, the overload valve allows fluid communication between the first chamber and the second chamber, wherein the piston has a recessed end and the first chamber has a respective protruding head on an opposite side of the recessed end, wherein in the door closed position the protruding head is at least partially received within the respective recess, the overload valve being in the recessed end of the piston.
According to a third aspect, the present invention provides a door comprising a door closer according to any one of the first or second aspects of the present invention.
According to a fourth aspect, the present invention provides a method of closing a door according to the third aspect of the invention, the door beginning in a door open position and a user applying pressure to the door such that a threshold pressure is exceeded and fluid is transferred through an overload valve of the door closer such that the door moves to a door closed position.
It will of course be appreciated that features described in relation to one aspect of the invention may be incorporated into other aspects of the invention. For example, the door closer of the second aspect of the invention may comprise any of the features described in relation to the first aspect of the invention. Those skilled in the art will appreciate that the second aspect of the invention provides a mirrored piston and recess arrangement as described in relation to the first aspect of the invention and that the features of the invention described with reference to the first aspect of the invention may be suitably reversed when applied to the second aspect of the invention. In addition, the method of the present invention may incorporate any of the features described with reference to the apparatus of the present invention, and vice versa.
Drawings
Embodiments of the present invention will now be described, by way of example only, with reference to the accompanying schematic drawings in which:
FIG. 1 is a schematic view of a door to which a door closer according to one embodiment of the invention is coupled, the schematic view showing the door in a fully open position;
FIG. 2 is a cross-sectional view of a door closer according to one embodiment of the invention, showing the door closer with the piston in a "door open" position;
FIG. 3 is a cross-sectional view of the door closer of FIG. 2 showing the door closer with the piston in a "door closed" position;
FIG. 4 is a cross-sectional view of the door closer of FIG. 2 showing the piston moving through different positions as the piston moves from the "door open" position to the "door closed" position;
FIG. 5 is an exploded view of the main valve assembly of the door closer;
FIG. 6 is a detailed cross-sectional view of the main valve assembly of the door closer;
FIG. 7 is a cross-sectional view of the door closer of FIG. 2 showing the arrangement of the overload valve in detail; and is also provided with
FIG. 8 is a detailed cross-sectional view of a main valve assembly of a door closer configured such that the door closer may be replenished with hydraulic fluid.
Detailed Description
Fig. 1 shows a door 100 coupled to a door closer 1 and mounted within a door frame 101 according to an embodiment of the invention. The door 100 is shown in its fully open position in fig. 1, wherein the door is positioned at an angle a of 130 degrees from the fully closed position of the door (corresponding to a door fully closed position of 0 degrees for angle a, indicated by reference numeral 100' in fig. 1).
The door closer 1 shown in more detail in fig. 2 and 3 is an electro-hydraulic door closer and comprises a body 3 having a hollow cylindrical internal cross section divided into a first chamber 5 and a second chamber 7 by a piston 9 which is movable along the body 3 to vary the relative volumes of the first chamber 5 and the second chamber 7. The first chamber 5 and the second chamber 7 are in fluid communication with each other via a soft-shut valve 11 coupled in series with a main valve assembly 20. The main valve assembly 20 is operable to prevent fluid flow through the main valve assembly 20 such that fluid flow between the first chamber and the second chamber can be prevented to allow a door coupled with the door closer to be held in an open or closed position.
The piston 9 defines a first wall of the first chamber and the main valve assembly 20 defines a second, opposite wall of the first chamber such that when the piston 9 is driven along the main body 3 towards the main valve assembly 20, the volume of the first chamber decreases and hydraulic fluid moves from the first chamber 5 to the soft-closed valve 11 via the main valve assembly 20 and then into the second chamber 7. The door closer is thus arranged such that fluid can move between the first chamber 5 and the second chamber 7 via the main valve assembly 20 and the soft closing valve 11 in each position of the piston 9, provided that the main valve assembly 20 is open. The door closer also comprises a door speed valve 16 and a latch control valve 17 through which fluid can flow between the first chamber 5 and the second chamber 7, depending on the position of the piston 9 within the body 3, as will be described in more detail below.
When the door closer 1 is coupled to a door, the piston 9 is movable between a "door open" position in which the door is fully open at an angle a of 130 degrees as shown in fig. 1, and a "door closed" position; in the "door closed" position, the door is fully closed (corresponding to angle a of 0 degrees in fig. 1). In fig. 2, the door closer 1 is shown, wherein the piston 9 is in a "door open" position, wherein the piston 9 is positioned such that the volume of the first chamber 5 is maximized and the volume of the second chamber 7 is minimized. In fig. 3, the door closer 1 is shown, wherein the piston 9 is in a "door closed" position, wherein the piston 9 is positioned such that the volume of the first chamber 5 is at a minimum and the volume of the second chamber 7 is at a maximum. The door closer 1 comprises a spring 15 which is inside the body 3 and which abuts the piston 9 to bias the piston 9 into the "door closed" position. Such an arrangement ensures that when the door closer is coupled to the door, the door will always be biased towards the door closed position.
When the user moves the piston 9 from the "door closed" position to the "door open" position, the pinion of the rack and pinion arrangement 13 is rotated in a self-explanatory manner by a mechanical linkage (not shown), rotating in a clockwise direction as seen in fig. 2 and 3, and driving the piston 9 from left to right as seen in fig. 2 and 3 against the resilient bias of the spring 15, thereby reducing the volume of the second chamber 7 and increasing the volume of the first chamber 5. When this occurs, the change in the relative dimensions of the first and second chambers forces the hydraulic fluid contained within the second chamber 7 to move to the first chamber 5 via the soft shut-off valve 11 and the main valve assembly 20 and (depending on the position of the piston 9) the gate speed valve 16 and the latch control valve 17. Once the door coupled to the door closer 1 is fully open, the main valve assembly 20 may be operated to maintain the piston 9 in a "door open" position, as will be described in more detail below.
When the piston is in the "door open" position and the main valve assembly 20 is open, the door closer 1 moves the door to which the door closer 1 is coupled from a fully open position corresponding to an angle a of 130 degrees to a fully closed position corresponding to an angle a of 0 degrees under the control of the door closer. The speed at which the piston 9 moves varies according to the angle a of the door from the fully closed position. The piston 9 is pushed by the elastic bias of the spring 15 through four phases: a soft closing phase corresponding to the door moving between an angle a of 130 degrees to 75 degrees from the door closing position; a door speed stage corresponding to the door moving between an angle a of 75 degrees to 10 degrees from the door closed position; and a latch speed phase corresponding to movement of the door between an angle a of 10 degrees to 0 degrees from the door closed position. The operation of the door closer 1 when the piston 9 is moved from the "door open" position to the "door closed" position by each of these stages will now be described with reference to fig. 4.
As can be seen from fig. 4, the first chamber 5 feeds a speed control valve 16 and a latch control valve 17 (each of which is coupled to a feedback valve 18) so that fluid can move from the speed control valve 16 and the latch control valve 17 into the return valve 18 and the second chamber. However, as shown in fig. 4, with the piston 9 in the "door open" position, the feedback valve 18 is blocked by the piston 9. When the piston 9 moves towards the opposite wall 240 of the chamber (the opposite wall 240 being formed by the main valve assembly 20), as shown in fig. 4, between positions a and B, the piston 9 moves from right to left through the soft closing phase. In the soft closing phase, hydraulic fluid can only flow through the main valve 20 and the soft closing valve 11, but not through either the speed control valve 16 or the latch control valve 17, as the return valve 18 is blocked by the piston 9. Thus, during the soft closing phase, the main valve assembly 20 is operated to prevent any fluid flow between the first chamber 5 and the second chamber 7.
As shown in fig. 4, the piston 9 moves through the gate speed phase between position B and position C. When the piston 9 reaches position B, the piston 9 now no longer blocks the return valve 18, so when the piston 9 moves beyond position B, the piston pushes hydraulic fluid from the first chamber 5 into the second chamber 7 via the speed control valve 16 and the latch control valve 17 and via the main valve assembly 20 and the soft shut-off valve 11. The speed at which the door closes during the door speed phase is controlled by adjusting a speed control screw 161 that can be moved into or out of the return valve 18 to block fluid flow through the return valve 18.
The piston 9 moves through the latch speed phase between position C and position D (which corresponds to the "door closed" position), as shown in fig. 4. When the piston 9 reaches the position C, the piston 9 blocks the speed control valve 16 so that hydraulic fluid can only move between the first chamber 5 and the second chamber 7 via the latch control valve 17, the main valve assembly 20 and the soft shut-off valve 11. The closing speed of the door during the latching phase can be controlled by adjusting the latch control screw 171, which can be moved into or out of the return valve 18 in the same manner as the speed control screw 161.
A main valve assembly 20 (an exploded view of which is shown in fig. 5) is positioned at the end of the body 3 opposite the piston 9 and forms an opposite wall 240 of the first chamber 5. As seen in fig. 5 and 6, the main valve assembly 20 includes a main valve body 201, a valve pin housing 203 that houses a valve member 205 in the form of a valve pin 205 within an interior cavity 207 of the valve pin housing 203, and a pin piston 209 contained within an interior cavity 211 of a pin piston housing 210. The pin piston 209 is arranged to move the valve pin 205 within the valve pin housing 203. The valve pin housing 203 includes a first port 221 at a first end of the valve pin housing 203 and a second port 223 in a wall of the valve pin housing 203. The valve pin housing 203 is arranged such that all hydraulic fluid flowing between the first chamber 5 and the second chamber 7 must flow through the interior cavity 207 of the valve pin housing 203 via port 221 and port 223.
The pin 205 is generally cylindrical in shape and has a first portion 217 of a first diameter and a second portion 219 of a second, larger diameter. The diameter of the second portion 219 is substantially equal to the inner diameter of the interior cavity 207 of the valve pin housing 203 such that movement of the valve pin 205 within the valve pin housing 203 is restricted in a direction along the longitudinal axis of the valve pin housing 203, as indicated by the arrow labeled "Y" in fig. 6. Valve pin 205 has a first tapered end 211 and an opposite second flat end 213. The first end 211 is the leading end of the pin 205 at the first portion 217 and the second end 213 is the trailing end of the pin at the second portion 219.
The first port 221 is aligned with the longitudinal axis of the valve pin housing 203 and the valve pin 205 is positioned within the pin chamber such that the conical first end 211 of the pin faces the first port 221. The first valve port 221 is formed by a tapered recess shaped to receive the first end 211 of the pin 205 such that the pin 205 may be moved along the axis of the pin chamber from an open position to a closed position where the tapered first end 211 of the pin 205 is located within the tapered recess, as shown in fig. 6. In this position, valve pin 205 closes valve port 221 and prevents fluid flow through main valve assembly 20.
Valve pin 205 is moved into contact with valve port 221 by valve piston 209, which is arranged to move under the influence of the magnetic field generated by 24V coil 225. This type of electromagnetic piston arrangement will be well understood by those skilled in the art. However, the pin piston 209 of the present embodiment of the invention also includes an adjustable member 227 in the form of a flat head screw that is movable along the longitudinal axis of the pin piston 209 such that the adjustable length of the adjustable member 227 protrudes from the end of the pin piston 209 in order to adjust the overall length of the piston. Upon application of an electromagnetic field, the piston moves toward the pin and the distal end of the adjustable member 227 abuts the flat end of the pin 205. The pin piston 209 then moves the pin 205 to a position where the first end 211 of the pin 205 is received within the inlet, thereby preventing fluid flow through the main valve.
The door closer also comprises an overload valve 91 which allows hydraulic fluid to flow directly from the first chamber 5 into the second chamber 7 via the overload valve 91, bypassing the main valve assembly 20, the soft closing valve 11, the speed control valve, and the latch control valve. The overload valve 91, shown in detail in fig. 7, comprises a valve spring 913 biasing a ball abutment 912 to a position where the ball abutment 912 blocks the valve port 911 such that in normal use no fluid can flow between the first chamber 5 and the second chamber 7 via the overload valve 91. If the piston 9 is forced to move from the open position to the closed position, the hydraulic pressure in the first chamber 5 increases to a level that causes the ball abutment 912 to push against the elastic bias of the spring 913, thereby opening said valve port 911 so that hydraulic fluid can flow from the first chamber 5 into the second chamber 7 via the overload valve. The overload valve described is known and reduces the risk of damaging the door closer due to over-pressurization of the first chamber 5.
As can be seen in fig. 2 and 3, the piston 9 forms a first end of the first chamber 5 which is cylindrical, and the main valve assembly 20 forms a second end of the opposite side of the first chamber 5, whereby the volume of the first chamber 5 is variable by moving the piston 9 towards or away from the main valve assembly 20. The piston 9 comprises a cylindrical protruding end 915 protruding into the first chamber 5, the axis of the cylindrical end 915 being aligned with the axis X of the first chamber 5, such that the protruding end 915 is intermediate within the first chamber. The overload valve 91 is located within the protruding end 915 such that the overload valve port 911 is positioned in the center of the protruding end 915, aligned with the axis X of the first chamber 5.
At the second end of the first chamber 5, the main valve assembly 20 comprises a cylindrical recess 202 having substantially the same dimensions as the protruding end 915, such that the recess 202 is dimensioned to receive the cylindrical protruding end 915 when the piston 9 is moved to the door closed position.
It has been found advantageous to configure the door closer 1 to locate the overload valve port 911 on the protruding end 915 of the piston 9, and to arrange the second wall of the chamber with a recess 202 configured to receive the protruding end 915 of the piston 9 when the piston 9 is moved to the door closed position. With this configuration, it has been observed that when the piston 9 is pushed from the door open position to the door closed position, the fluid pressure required to engage the overload valve 91 may be locally reached at the overload valve port 911, while the fluid pressure is lower elsewhere within the first chamber 5. Thus, the overload valve 91 can be engaged while subjecting the first chamber 5 and the main valve assembly 20 to lower hydraulic pressures than is typical in known door closers.
In some cases, the amount of hydraulic fluid within the door closer 1 may need to be replenished. Thus, the main valve assembly is provided with a vacuum valve 225 at the distal end of the pin piston housing 210, on the opposite side of the main valve assembly 20 main body 201, as shown in fig. 6. The vacuum valve 225 includes a threaded bore 227 in fluid communication with the pin piston cavity 211 via an orifice 228 at an end of the bore 227, the threaded bore 227 having a tapered section adjacent the orifice 228 such that the diameter of the orifice 228 is less than the diameter of the main section of the bore 277. To seal the vacuum valve 225, a ball abutment 230 having a diameter greater than the diameter of the aperture 228 is first placed into the aperture 227, and then a grub screw 229 is screwed into the aperture 227 to urge the ball abutment 230 along the aperture 227 and into abutment with the sloped inner wall 231 of the tapered section of the aperture 227 adjacent the aperture 228. Thus, when sealing the vacuum valve 225, the orifice 228 is blocked with the ball abutment 230.
To supplement the door closer 1 with hydraulic fluid, the latch control valve 17 is removed and a hydraulic fluid source 173 is placed at the latch control valve 172 such that the hydraulic fluid source 173 is in fluid communication with either the first chamber 5 or the second chamber 7 depending on the position of the piston, as shown in fig. 8. The ball abutment 230 and the flat head screw 229 are then removed from the hole 227 and a tube 400 is placed around the end of the pin piston housing 210 as shown in fig. 8. Vacuum is then applied to the aperture 227 using, for example, a syringe or pump connected to the tube 400 to draw all air contained within the door closer 1 in the direction of the arrow labeled "Z" in fig. 8. Application of a vacuum at the vacuum valve 225 causes hydraulic fluid to be drawn from the hydraulic fluid source 173 in the direction of the arrow labeled "W" in fig. 8, thereby replacing all entrapped air within the door closer 1 with hydraulic fluid. Once the hydraulic fluid in the door closer 1 is replenished to the proper level, ball abutment 230 and grub screw 229 are replaced within bore 227 to seal vacuum valve 225.
In the foregoing description, integers or elements are mentioned which have known, obvious or foreseeable equivalents, then such equivalents are herein incorporated as if individually set forth. Reference should be made to the claims for determining the true scope of the present invention, which should be construed to encompass any such equivalents. The reader will also appreciate that integers or features of the invention that are described as preferable, advantageous, convenient or the like are optional and do not limit the scope of the independent claims. Furthermore, it should be understood that such optional integers or features, while potentially beneficial in some embodiments of the invention, may be undesirable in other embodiments and thus may not be present.

Claims (9)

1. A door closer, the door closer comprising:
a first chamber and a second chamber, the first chamber and the second chamber being in fluid communication via a main valve,
the first chamber being defined by a piston movable between a door open position in which the first chamber has a first volume and a door closed position in which the first chamber has a second volume, the first volume being greater than the second volume,
and an overload valve configured such that if within the first chamberPressure of more than 100N/m 2 The overload valve allows fluid communication between the first chamber and the second chamber,
wherein the piston has a protruding head and the first chamber has a corresponding recess on the opposite side of the protruding head,
wherein in the door closed position the protruding head is at least partially received in the corresponding recess, the overload valve being at the protruding head of the piston,
wherein the main valve is configured to be closable such that substantially no fluid is movable between the first and second chambers via the main valve, and
wherein the door closer is an electro-hydraulic door closer and the main valve is configured to be closable in response to the presence of an electric field such that the door closer is configured to hold a door in a door open position when the electric field is generated and to allow closing of the door when the electric field is removed.
2. The door closer of claim 1 wherein the protruding head has a length and the recess has a depth, the protruding head length being substantially equal to the recess depth.
3. A door closer according to any preceding claim, wherein the protruding head of the piston is cylindrical and the corresponding recess is also cylindrical.
4. A door closer according to claim 3, wherein the protruding head has an end face and the corresponding recess has an end face, the end face being planar, concave or convex.
5. The door closer of claim 4 wherein the overload valve is centered on the end face of the protruding head of the piston.
6. The door closer of claim 5 wherein the protruding head has a length greater than 10% of a distance between the first and second ends of the first chamber when the piston is in the door open position.
7. A door closer, the door closer comprising:
a first chamber and a second chamber, the first chamber and the second chamber being in fluid communication via a main valve,
the first chamber being defined by a piston movable between a door open position in which the first chamber has a first volume and a door closed position in which the first chamber has a second volume, the first volume being greater than the second volume,
and an overload valve configured such that if the pressure in the first chamber exceeds 100N/m 2 The overload valve allows fluid communication between the first chamber and the second chamber,
wherein the piston has a recessed end and the first chamber has a corresponding protruding head on the opposite side of the recessed end,
wherein in the door closed position the protruding head is at least partially received within the corresponding recess, the overload valve being in the recessed end of the piston,
wherein the main valve is configured to be closable such that substantially no fluid is movable between the first and second chambers via the main valve, and
wherein the door closer is an electro-hydraulic door closer and the main valve is configured to be closable in response to the presence of an electric field such that the door closer is configured to hold a door in a door open position when the electric field is generated and to allow closing of the door when the electric field is removed.
8. A door comprising a door closer according to any one of the preceding claims.
9. A method of closing a door, the door being in accordance with claim 8, the door initially being in the door open position and a user applying pressure to the door such that the threshold pressure is exceeded and fluid is transferred through an overload valve of the door closer such that the door moves to a door closed position.
CN201910939579.0A 2018-09-28 2019-09-30 Door closer with overload valve Active CN110965883B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1815834.5A GB2580013B (en) 2018-09-28 2018-09-28 Door-closer with overload valve
GB1815834.5 2018-09-28

Publications (2)

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CN110965883A CN110965883A (en) 2020-04-07
CN110965883B true CN110965883B (en) 2023-10-27

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JPH07259426A (en) * 1994-03-28 1995-10-09 Nippon Doaachietsuku Seizo Kk Door closer
DE29723094U1 (en) * 1997-02-20 1998-04-02 Stabilus Gmbh, 56070 Koblenz Piston-cylinder unit with a closing valve
CN2467720Y (en) * 2001-01-05 2001-12-26 上海东丰五金有限公司 Single-side opening half-turn floor spring
EP1518989A1 (en) * 2003-09-24 2005-03-30 Saint-Gobain Seva Built-in door closer
DE102005047339A1 (en) * 2005-07-05 2007-01-11 Dorma Gmbh + Co. Kg Door closing device for a fireproof door comprises a drive unit arranged in a housing and coupled with a door via an output shaft, an elastic force storage unit coupled with the drive unit and a hydraulic unit
CN201372656Y (en) * 2009-02-24 2009-12-30 肇庆市志成气动有限公司 Hydraulic mechanism with safety valve for door closer
CN102959168A (en) * 2010-06-25 2013-03-06 多玛两合有限公司 Door closer

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DE3001406A1 (en) * 1980-01-16 1981-07-23 Dorma-Baubeschlag Gmbh & Co Kg, 5828 Ennepetal SELF-ACTING DOOR CLOSER
DE8704569U1 (en) * 1987-03-27 1987-07-16 Gretsch-Unitas GmbH Baubeschläge, 7257 Ditzingen Door closer
EP0545624B1 (en) * 1991-11-29 1997-01-22 Ryobi Ltd. Floor hinge
KR940000715A (en) * 1992-06-08 1994-01-03 이문현 Enhanced Flow Hinge
JP6708852B2 (en) * 2016-06-23 2020-06-10 日本ドアーチエック製造株式会社 Door closer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07259426A (en) * 1994-03-28 1995-10-09 Nippon Doaachietsuku Seizo Kk Door closer
DE29723094U1 (en) * 1997-02-20 1998-04-02 Stabilus Gmbh, 56070 Koblenz Piston-cylinder unit with a closing valve
CN2467720Y (en) * 2001-01-05 2001-12-26 上海东丰五金有限公司 Single-side opening half-turn floor spring
EP1518989A1 (en) * 2003-09-24 2005-03-30 Saint-Gobain Seva Built-in door closer
DE102005047339A1 (en) * 2005-07-05 2007-01-11 Dorma Gmbh + Co. Kg Door closing device for a fireproof door comprises a drive unit arranged in a housing and coupled with a door via an output shaft, an elastic force storage unit coupled with the drive unit and a hydraulic unit
CN201372656Y (en) * 2009-02-24 2009-12-30 肇庆市志成气动有限公司 Hydraulic mechanism with safety valve for door closer
CN102959168A (en) * 2010-06-25 2013-03-06 多玛两合有限公司 Door closer

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Publication number Publication date
GB201815834D0 (en) 2018-11-14
GB2580013A (en) 2020-07-15
CN110965883A (en) 2020-04-07
GB2580013B (en) 2023-05-17

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