JP2010019053A - Door closer - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enable to adjust resistance of a door closer depending on a size of the door and a degree of an external force acting in the closing direction by making a relief valve selectively switchable. <P>SOLUTION: High-pressure and low-pressure chambers A and B are ordinarily shut off by the relief valve 39. The relief valve 39, which communicates the high-pressure chamber A and the low-pressure chamber B and discharges a hydraulic fluid in the high-pressure chamber A into the low-pressure chamber B, can be switched between the opening/closing operable state and the opening inoperable state when the external force in the closing direction acts on the door while the door is in process of closing, and is stored in a housing 3. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an improvement in a door closer (door self-closing device) that automatically and slowly closes an open door.

  Generally, a door closer includes a housing having a sealed space filled with hydraulic oil, and a piston urged by a coil spring is disposed in the sealed space of the housing so as to be able to reciprocate. The piston is provided with a check valve that divides the high pressure chamber and the low pressure chamber and communicates and blocks the high pressure chamber and the low pressure chamber. Further, a rack and pinion mechanism is assembled to the piston, and a rotating shaft is coupled to the pinion of the rack and pinion mechanism so as to rotate integrally therewith so as to penetrate the housing vertically. Further, one end of the link mechanism is connected to the upper end of the rotating shaft, and the other end of the link mechanism is connected to the upper frame side of the door opening of the building.

  When the door is opened, the rotational operation is transmitted to the rotary shaft through the link mechanism, and further converted into a linear motion of the piston through the rack and pinion mechanism. As a result, the piston moves in the sealed space of the housing to compress the coil spring, and hydraulic oil flows from the low pressure chamber to the high pressure chamber through the check valve, and the force that moves in the door closing direction is accumulated in the door closer. The door is opened while being done. When the hand is released from the door, the piston moves linearly in the opposite direction due to the repulsive force of the compressed coil spring. At this time, the high pressure chamber and the low pressure chamber are closed by a check valve, and the hydraulic oil in the high pressure chamber is closed. Does not flow into the low-pressure chamber through the check valve, but flows out into the low-pressure chamber through the speed adjustment valve, so that the door slowly and automatically closes. The closing speed of the door is adjusted by controlling the flow rate of the hydraulic oil flowing out from the high pressure chamber to the low pressure chamber with a speed adjustment valve.

  By the way, when an external force in the closing direction acts on the door by forcibly closing the door equipped with such a door closer while it is automatically closed slowly by the door closer, it flows out from the high pressure chamber to the low pressure chamber. Since the flow rate of the hydraulic fluid is controlled by the speed control valve and is constant, the internal pressure of the high pressure chamber increases excessively, the resistance of the door closer increases, and an unreasonable force is applied to the door hinges and the frame member of the door opening. These may be damaged.

In order to prevent such damage, in Patent Document 1, a relief valve is provided in the wall of the housing, and hydraulic oil whose pressure has been increased is discharged to the low pressure chamber through the relief valve to reduce the internal pressure of the high pressure chamber. As a result, the resistance of the door closer is not increased so that an excessive force is not applied to the door hinge and the frame member of the door opening, thereby preventing the damage.
Japanese Examined Patent Publication No. 41-17309 (right column on page 3, Fig. 9)

  However, even if a relief valve is provided as in Patent Document 1 so as not to increase the resistance of the door closer, the function of the relief valve may be unnecessary depending on the ease of use such as the type of door and the application location. It is uneconomical to provide two types of door specifications, one with a relief valve and one without a relief valve.

  Further, in the above-mentioned Patent Document 1, since only a separate route for discharging the hydraulic oil in the high pressure chamber to the low pressure chamber is provided and the flow rate discharged from the relief valve of the hydraulic oil is constant, the size of the door and the closing of the door The resistance of the door closer cannot be adjusted according to the degree of external force acting in the direction, and there is a concern that excessive force will be applied to the door hinge and the frame member of the door opening, and measures against damage are not perfect .

  The present invention has been made in view of such a point, and the object of the present invention is to make it possible to selectively switch the relief valve, and to reduce the size of the door and the external force acting in the closing direction. A second object is to make it possible to adjust the resistance of the door closer according to the degree.

  In order to achieve the above object, the present invention has a first feature that the relief valve is switched between a state in which the relief valve can be opened and closed and a state in which the relief valve cannot be opened. The second feature is that the oil discharge timing is changed.

  Specifically, the present invention includes a housing having a sealed space filled with hydraulic oil, and a reciprocating movement arranged in a state of being urged by a piston urging means in the sealed space. A piston partitioned into a low-pressure chamber; a check valve provided in the piston for communicating and blocking the high-pressure chamber and the low-pressure chamber; a rack and pinion mechanism incorporated in the piston; and a pinion of the rack and pinion mechanism A rotary shaft connected integrally with the housing so as to penetrate the housing up and down, one end connected to the upper end of the rotary shaft, and the other end connected to the upper frame side of the door opening of the building A link mechanism, and a speed adjustment valve that is attached to the housing and adjusts the closing speed of the door by controlling the flow rate of hydraulic oil flowing from the high pressure chamber to the low pressure chamber in conjunction with the movement of the piston. The opening operation of the door is converted into a linear movement of the piston through the link mechanism, the rotation shaft and the rack and pinion mechanism, and the piston is resisted against the biasing force of the piston biasing means. Move the hydraulic oil in the closed space in the shrinking direction of the low-pressure chamber, drain the hydraulic oil from the low-pressure chamber to the high-pressure chamber through the check valve, accumulate the force to move in the closing direction of the door, and release the hand from the door to release the piston. By moving the high pressure chamber in the sealed space of the housing in the sealed space of the housing by the biasing force of the piston biasing means, the hydraulic oil in the high pressure chamber flows out to the low pressure chamber via the speed control valve, and the door is closed slowly and automatically. The following measures were taken for the configured door closer.

  That is, according to the first aspect of the present invention, when the door is closed, the high pressure chamber and the low pressure chamber are shut off during normal times, and when an external force in the closing direction acts on the door while the door is closed. The relief valve that communicates the high-pressure chamber and the low-pressure chamber and discharges the hydraulic oil in the high-pressure chamber to the low-pressure chamber is provided so as to be switchable between a state that can be opened and closed and a state that cannot be opened. Features.

  The invention according to claim 2 is the invention according to claim 1, wherein an insertion hole is formed in the housing so as to connect the high-pressure chamber and the low-pressure chamber. The relief valve is inserted so that its position can be adjusted by advancing and retreating from the outside. The relief valve can be opened and closed, and the opening and closing operation timing can be freely changed according to the internal pressure of the high-pressure chamber by adjusting the position. It is comprised as follows.

  The invention according to claim 3 is the invention according to claim 2, wherein the relief valve is formed such that the communication path is opened at the tip, and the position of the shaft valve body can be adjusted by advancing and retreating operation. An opening / closing means for opening / closing the communication path; and an opening / closing biasing means for biasing the opening / closing means. The communication path is closed by pressing, and the high pressure chamber and the low pressure chamber are shut off. On the other hand, when an external force in the closing direction acts on the door while the door is closed, the opening / closing means is opened / closed by the internal pressure of the high pressure chamber. It is configured to open the communication path away from the valve body tip against the biasing force of the biasing means, and to connect the high pressure chamber and the low pressure chamber to discharge the hydraulic oil in the high pressure chamber to the low pressure chamber. It is characterized by.

  According to a fourth aspect of the present invention, in the third aspect of the present invention, when the relief valve cannot be opened, the valve body is advanced so that the opening / closing means contacts the bottom of the insertion hole. And the connection path of the valve body is closed by an opening / closing means.

  According to the first aspect of the present invention, when the external force in the closing direction is applied to the door by forcibly closing the door while the door is closed in a state where the relief valve can be opened and closed, the relief valve is connected to the high pressure chamber. Since the hydraulic oil in the high-pressure chamber is discharged to the low-pressure chamber through communication with the low-pressure chamber, a situation in which the internal pressure of the high-pressure chamber is excessively increased is avoided and the resistance of the door closer does not increase. An excessive force is not applied to the frame member of the part, and these are not damaged. On the other hand, in a state where the relief valve cannot be opened, even if an external force in the closing direction acts on the door while the door is being closed, the relief valve does not work and is equal to nothing. As described above, the relief valve can be made to function or not to function according to the convenience of use such as the type and application location of the door, and it is very economical because it is not necessary to prepare two types of doors.

  According to the second aspect of the invention, in the state where the relief valve can be opened and closed, the position of the relief valve is adjusted by an external advance / retreat operation, so that the relief valve opening / closing operation timing, that is, from the high pressure chamber to the low pressure chamber. The discharge timing of discharged hydraulic oil can be freely changed according to the internal pressure of the high pressure chamber, so that the resistance of the door closer can be adjusted appropriately even if the size of the door or the external force acting in the closing direction changes. A situation in which an excessive force is applied to the hinge member and the frame member of the door opening is surely prevented, and the prevention of breakage is ensured, thereby improving convenience.

  According to the third aspect of the present invention, when an external force in the closing direction acts on the door while the door is being closed while the relief valve can be opened and closed, the hydraulic oil in the high pressure chamber is discharged to the low pressure chamber. The opening and closing means of the relief valve is separated from the leading end of the connecting path of the valve body against the biasing force of the opening and closing biasing means by the internal pressure of the high pressure chamber and the connecting path is opened. Further, the urging force of the opening / closing urging means is easily performed by adjusting the position of the valve body.

  According to the invention of claim 4, since the opening / closing means of the relief valve is pressed by the valve body and is in contact with the bottom of the insertion hole, it does not move regardless of the internal pressure of the high-pressure chamber, and therefore the valve body is not connected. The path does not open and the function as a relief valve is lost.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  1-3, 101 shows the door opening part of a building, and this door opening part 101 is the space enclosed by the rectangle by the upper frame 102, a pair of right and left eaves frame 103, and a lower frame (not shown). The door 104 is attached to the one frame 103 via a hinge 105 so that the door opening 101 can be opened and closed. The door 104 is automatically and slowly closed from the open state by the door closer 1 according to the embodiment of the present invention.

  The door closer 1 is a right-opening (right-handed) parallel type and includes a door closer body 2. The door closer body 2 includes a housing 3 having a sealed space 3a (see FIG. 4) filled with hydraulic oil (not shown). The housing 3 is connected to the door 104 via a mounting bracket 4 (see FIG. 3). Attached to the top. The mounting bracket 4 has a U-shaped hook portion 4a formed at one end (right end in FIG. 3) and an attachment piece portion 4b rising obliquely at the other end (left end in FIG. 3).

  The housing 3 is formed in a rectangular parallelepiped shape with six surfaces including a front wall 5, a rear wall 6, an upper surface wall 7, a lower surface wall 8, and a pair of left and right side walls 9, and on the rear wall 6 side, an upper surface wall 7 and a lower surface are formed. A recessed portion 10 (see FIG. 4) surrounded by the wall 8 and the left and right side walls 9 is formed. Further, a latch pin 11 is disposed on one end side (right end side in FIG. 4) of the recessed portion 10 so as to be bridged up and down by the upper surface wall 7 and the lower surface wall 8. Furthermore, two screw insertion holes 9a are vertically formed through the one side wall 9 (left side in FIG. 4) (see FIG. 6).

  In order to attach the door closer body 2 to the inside of the upper end of the door 104, first, the mounting bracket 4 is arranged at the upper end of the door 104, and the screws 12 (see FIGS. 1 and 2) are inserted through the four screws of the mounting bracket 4. The fitting 4 is attached inside the upper end of the door 104 by being inserted into a hole (not shown) and screwed into the door 104.

  Next, the door closer body 2 is disposed in front of the mounting bracket 4, the hook 4 a of the mounting bracket 4 is hooked on the latch pin 11 of the housing 3, and the mounting bracket 4 is disposed in the recessed portion 10 of the housing 3. From this state, the screw 13 (see FIG. 3) is screwed into the two screw insertion holes 9a of the housing 3 (the side wall 9 on the left side of FIG. 3) and the two screw holes (not shown) of the mounting bracket 4. Thus, the door closer main body 2 is attached to the inside of the upper end of the door 104 via the attachment fitting 4.

  In the housing 3 (sealed space 3a), as shown in FIG. 4, the piston 14 is reciprocated while being urged rightward in FIG. 4 by the spring force of the first coil spring 15 as piston urging means. The sealed space 3a is partitioned by the piston 14 into a high pressure chamber A (a small region on the right side in FIG. 4) and a low pressure chamber B (a large region on the left side in FIG. 4). In FIG. 4, reference numeral 16 denotes a spring seat fitting attached to the end face of the piston 14 on the first coil spring 15 side, and a communication hole 16 a is formed at the center of the spring seat fitting 16. Reference numeral 17 denotes a pair of left and right end plugs. These end plugs 17 are fitted into the fitting holes 9b by screwing the outer male screw portions 17a to the inner screw female portions 9c of the fitting holes 9b of the both side walls 9. It is inserted.

  A hollow portion 14 a is formed inside the piston 14, and the hollow portion 14 a communicates with the high pressure chamber A through a first passage 18 and communicates with the second passage 19 and the spring seat 16. It communicates with the low pressure chamber B via 16a. The first passage 18 includes a cavity portion side passage 18a and a high pressure chamber side passage 18b larger than the cavity portion side passage 18a, and a check valve 20 is interposed in the high pressure chamber side passage 18b. The high pressure chamber A and the low pressure chamber B are communicated and blocked by 20. That is, the hollow portion 14a constitutes a part of the low pressure chamber B. The check valve 20 includes a valve main body 21 fitted in the high pressure chamber side passage 18b. In the valve main body 21, a ball housing portion 21a communicates with the hollow portion side passage 18a and the high pressure chamber A. The ball 22 is movably accommodated in the ball accommodating portion 21a. In the closed state of the door, the check valve 20 presses the ball 22 against the inner wall of the ball accommodating portion 21a communicating with the cavity-side passage 18a by the internal pressure of the high-pressure chamber A to close the cavity-side passage 18a. The hydraulic oil is prevented from flowing out to the low pressure chamber B side.

  A rack and pinion mechanism 23 is incorporated in the cavity 14 a of the piston 14. The rack and pinion mechanism 23 includes a rack 24 formed on the inner wall of the hollow portion 14a, and a pinion 25 that meshes with the rack 24. In the pinion 25, a rotating shaft 26 penetrates the housing 3 up and down. It is connected so as to rotate together so as to be inserted. 1 and 2, reference numeral 27 denotes a cylindrical cup that covers the lower end of the rotating shaft 26.

  One end of a link mechanism 28 is connected to the upper end of the rotating shaft 26, and the other end of the link mechanism 28 is connected to the upper frame 102 side of the door opening 101 of the building. Specifically, the link mechanism 28 includes a main arm 29 and a connecting arm 30, one end of the main arm 29 is connected to the upper end of the rotating shaft 26, and the other end of the main arm 29 One end of the connecting arm 30 is rotatably connected around the shaft 31. On the other hand, the base end of the stay (triangular plate) 32 is attached to the upper frame 102 of the door opening 101 by screwing four screws 33 (see FIG. 3) into the upper frame 102. The other end of the connecting arm 30 is connected to the tip so as to be rotatable around the shaft 34.

  On the other side wall 9 of the housing 3 (on the right side in FIGS. 3 and 4), three speed adjusting valves 35 are located outside the end plug 17, two on the upper left and upper right in FIG. Has been inserted. As shown in FIG. 7, these speed adjusting valves 35 have a positive engagement groove 35a for inserting and engaging an operation tool such as a screwdriver at the base end, a male screw portion 35b at the middle portion, and a shaft portion at the distal end side. 35c has a shaft shape in which a notch 35d is formed at the tip of the shaft portion 35c, and a sealing O-ring 36 is fitted on the base end side of the male screw portion 35b.

  On the other hand, three first insertion holes 37 (see FIG. 7) are provided in the high pressure chamber A via the first communication passage 38a at the position corresponding to the speed adjustment valve 35 on the side wall 9 on the right side of FIGS. Are connected to the low pressure chamber B through a second communication passage 38b and a flow path (not shown), and the inner wall of the first insertion hole 37 is connected to the male of the speed adjustment valve 35. A female screw portion 37a into which the screw portion 35b is screwed is formed.

  Then, the speed adjusting valve 35 is inserted into the first insertion hole 37, and the male screw part 35b is screwed into the female screw part 37a. In this state, the gap formed around the shaft part 35c and the notch part The first communication path 38a and the second communication path 38b are communicated with each other through 35d, whereby the high pressure chamber A and the low pressure chamber B are communicated, and the speed adjustment valve 35 is axially operated by an operating tool such as a driver. The flow rate of the hydraulic oil flowing out from the high pressure chamber A to the low pressure chamber B in conjunction with the movement of the piston 14 is changed by changing the position of the notch portion 35d by screwing back and forth. Is controlled so as to adjust the closing speed of the door 104.

  The side wall 9 on the right side of FIG. 3 and FIG. 4 of the housing 3 is in a state in which the relief valve 39 can be opened and closed so as to be located on the lower right side in FIG. It is inserted so that it can be switched. 8 to 10 show an arrangement in which the relief valve 39 is switched to a state in which the relief valve 39 can be opened and closed. As shown in FIG. 8, the relief valve 39 includes a shaft-shaped valve body 40, a ball 41, and a bowl-shaped seat portion that supports the ball 41 at one end of a shaft portion 42a. A shaft-shaped ball seat 42 on which the projection 42b is formed and a second coil spring 43 as an opening / closing biasing means are provided. The ball 41 and the ball receiving seat 42 constitute an opening / closing means. The valve body 40 has a positive engagement groove 40a for inserting and engaging an operation tool such as a screwdriver at the proximal end, and a male threaded portion 40b formed in the middle, respectively, and the base side of the distal end side and the male threaded portion 40b. O-rings 44 for sealing are respectively fitted on the end sides. The valve main body 40 is formed with a communication path 40 c that opens at the tip, and the communication path 40 c opens in the middle of the valve main body 40 to the side.

  On the other hand, the second insertion hole 45 (see FIG. 8) communicates with the high pressure chamber A via the third communication passage 46a at the portion corresponding to the relief valve 39 of the side wall 9 on the right side of FIGS. In addition, the male threaded portion 40b of the valve body 40 is screwed into the inner wall of the second insertion hole 45 so as to communicate with the low pressure chamber B through a fourth communication passage 46b and a flow path (not shown). A female screw portion 45a is formed.

  Then, the second coil spring 43 is inserted into the bottom 45b side of the second insertion hole 45, and the shaft portion 42a of the ball seat 42 is inserted into the second coil spring 43, so that the seat portion 42b is inserted into the second coil spring 43. Further, the ball 41 is inserted into the second insertion hole 45, and the valve body 40 is inserted into the second insertion hole 45 so that the male screw portion 40b is inserted into the female insertion portion 45. The ball 41 is interposed between the seat portion 42b and the tip of the valve body 40 by screwing into the screw portion 45a and adjusting the insertion position by advancing and retreating operation with an external operation tool such as a screwdriver. In this state, the ball 41 is urged through the ball receiving seat 42 by the spring force of the second coil spring 43, and is sandwiched between the ball receiving seat 42 and the valve main body 40 to close the communication path 40c of the valve main body 40. The third communication passage 46a (the high pressure chamber A) and the fourth communication passage 46b (the low pressure chamber B) are blocked (see FIGS. 8 and 9).

  On the other hand, when the internal pressure of the high-pressure chamber A rises, the ball 41 is pressed leftward in FIGS. 8 and 9 to compress the second coil spring 43, and the ball 41 is resisted against the spring force of the second coil spring 43. The communication path 40c of the valve body 40 is opened away from the tip of the valve body 40, and the third communication path 46a and the fourth communication path 46b are connected via the connection path 40c of the valve body 40 and the second insertion hole 45. Thus, the high pressure chamber A and the low pressure chamber B communicate with each other (see FIG. 10).

  Further, as shown in FIG. 12, which is in a state in which the relief valve 39 cannot be opened, the relief valve 39 is screwed in the left direction in the drawing to disconnect the communication path 40c from the third communication path 46a. The ball seat 42 is pressed by the valve body 40 so that the tip of the shaft portion 42a is brought into contact with the bottom 45b of the second insertion hole 45. In this state, the ball 41 is sandwiched between the ball seat 42 and the valve body 40. Then, the communication path 40c of the valve body 40 can be closed with the ball 41 so that the hydraulic oil in the high pressure chamber A is not discharged to the low pressure chamber B. Not limited to this, the spring force of the second coil spring 43 is made variable by adjusting the position of the valve body 40 from the outside, and the opening / closing operation timing of the relief valve 39, that is, the opening / closing timing of the communication path 40 c is set to the internal pressure of the high-pressure chamber A. It can be easily changed according to the situation.

  In the door closer 1 configured as described above, when the door 104 is opened in the direction of the arrow X1 (clockwise) in FIG. 3, the rotation operation is transmitted to the rotation shaft 26 via the link mechanism 28, and the rotation shaft 26 is 3 rotates in the direction of arrow X2 (counterclockwise, clockwise in FIG. 4). As a result, the pinion 25 rotates in the direction of the arrow X2 (clockwise) in FIG. 4, and the piston 14 moves the first coil spring 15 against the spring force of the first coil spring 15 via the rack and pinion mechanism 23. While compressing, it moves linearly in the closed space 3a of the housing 3 in the direction of reducing the low-pressure chamber B, that is, in the direction of arrow X3 (leftward) in FIG. As a result, the hydraulic oil in the low pressure chamber B moves the ball 22 toward the high pressure chamber A through the communication hole 16a, the second passage 19, the cavity portion 14a and the first passage 18 of the spring seat 16 to open the first passage 18. Then, it flows out into the high pressure chamber A (see FIG. 7). Then, the door 104 is opened while accumulating the force for moving in the closing direction.

  When the hand is released from the door 104, the compressed first coil spring 15 is extended by the repulsive force during normal times, and the piston 14 is moved into the high-pressure chamber in the sealed space 3a of the housing 3 by the spring force of the first coil spring 15. A linearly moves in the A reduction direction, that is, in the arrow Y3 direction (right direction) in FIG. At this time, the first passage 18 is closed by the ball 22 of the check valve 20 being pressed against the inner wall of the ball accommodating portion 21 a by the internal pressure of the high pressure chamber A, so that the hydraulic oil in the high pressure chamber A passes through the first passage 18. Then, it does not flow out into the low pressure chamber B, but flows out into the low pressure chamber B through the speed adjustment valve 35 and a flow path (not shown) (see FIG. 9). As a result, the pinion 25 rotates in the direction of arrow Y2 (counterclockwise) in FIG. 4 and the rotation shaft 26 rotates in the direction of arrow Y2 (clockwise) in FIG. 3, and this rotational force is transmitted to the link mechanism 28. The door 104 slowly and automatically closes in the direction of arrow Y1 (counterclockwise) in FIG. At this time, in a state in which the relief valve 39 can be opened and closed, as shown in FIG. 9, the ball 41 is pressed against the tip of the valve body 40 by the spring force of the second coil spring 43 to close the communication path 40 c, A and low pressure chamber B are shut off. At this time, the flow rate of the hydraulic oil flowing out from the high pressure chamber A to the low pressure chamber B through the speed adjustment valve 35 is f, and the pressure of the high pressure chamber A is P0 (see FIG. 9). The pressure change is shown in FIG.

  On the other hand, when an external force in the closing direction acts on the door 104 by forcibly closing the door 104 in the middle of closing, the internal pressure of the high pressure chamber A rises, and the relief valve 39 is in a state where the opening and closing operation is possible. As shown in FIG. 10, the ball 41 is moved away from the tip of the valve body 40 against the spring force of the second coil spring 43 by the increased internal pressure of the high pressure chamber A, and the communication path 40 c is opened. The hydraulic oil in the high pressure chamber A is discharged to the low pressure chamber B through the relief valve 39 through communication with the low pressure chamber B. At this time, the hydraulic oil flows from both the speed adjustment valve 35 and the relief valve 39 from the high pressure chamber A to the low pressure chamber B. That is, the flow rate of the hydraulic oil flowing out from the high pressure chamber A to the low pressure chamber B is an amount obtained by adding the flow rate F of hydraulic fluid flowing out through the relief valve 39 to the flow rate f of hydraulic fluid flowing out through the speed adjustment valve 35. (F + F) (see FIG. 10). When the pressure of the high pressure chamber A at that time is P1, P1> P0, and the pressure change is shown in FIG. Incidentally, when there is no relief valve 39 or when the relief valve 39 does not function and cannot be opened, the flow rate of the hydraulic oil flowing out from the high pressure chamber A to the low pressure chamber B is the flow rate of the hydraulic oil flowing out through the speed adjustment valve 35. Only by f, the pressure of the hydraulic oil in the high pressure chamber A rises to P2 higher than P1. The pressure change is shown in FIG.

  As described above, in the above embodiment, the relief valve 39 is provided in the housing 3 in addition to the speed adjustment valve 35, and the door 104 is forcibly closed while the door 104 is being closed. In this state, when the relief valve 39 can be opened and closed, the ball 41 of the relief valve 39 is separated from the distal end of the communication path 40c of the valve body 40 against the spring force of the second coil spring 43, and the communication path 40c is opened, and the hydraulic oil in the high pressure chamber A is discharged to the low pressure chamber B through the relief valve 39, so that the internal pressure of the high pressure chamber A is prevented from excessively increasing and the resistance of the door closer 1 is not increased. As a result, it is possible to prevent damage to the hinge 105 of the door 104 and the upper frame 102 of the door opening 101 without applying an excessive force.

  Further, in the above embodiment, the position of the valve body 40 of the relief valve 39 is adjusted from the outside by an advancing / retreating operation to change the spring force of the second coil spring 43, thereby opening / closing timing of the communication path 49, that is, the high pressure chamber A. Since the discharge timing of the hydraulic oil discharged to the low pressure chamber B can be freely changed according to the internal pressure of the high pressure chamber A, the resistance of the door closer 1 can be changed even if the size of the door 104 or the external force acting in the closing direction changes. Therefore, it is possible to reliably prevent a situation in which an excessive force is applied to the hinge 105 of the door 104 or the upper frame 102 of the door opening 101, and to prevent the breakage of the door 104, thereby improving convenience.

  Furthermore, in the above-described embodiment, when the relief valve 39 cannot be opened, the tip of the shaft portion 42a of the ball seat 42 of the relief valve 39 is positioned at the bottom 45a of the second insertion hole 45 as shown in FIG. In order to stop the function of the relief valve 39 so that the ball 41 does not move regardless of the internal pressure of the high pressure chamber A, an external force in the closing direction acts on the door while the door 104 is being closed. However, the relief valve 39 does not work and is in an equal state. Therefore, the relief valve 39 can be made to function or not to function depending on the type of the door 104, the application location, etc., and it is very economical because the two types of doors 104 need not be prepared.

(Reference Example 1)
13 to 15 show the door closer 1 according to the first reference example. In this reference example 1, the check valve 20 is provided with the function of the relief valve 39 employed in the embodiment, and the others are the same as in the embodiment, so the same components are denoted by the same reference numerals. Detailed description thereof will be omitted, and only different points will be described below.

  That is, the high pressure chamber side passage 18b constituting the first passage 18 of the piston 14 is expanded to the cavity portion side passage 18a side than the embodiment, and the check valve 20 is movably inserted along the high pressure chamber side passage 18b. At the same time, a drop-off prevention plate 47 in which a through hole 47a is formed is attached to the end surface of the high-pressure chamber side passage 18b on the high-pressure chamber A side, and the coil spring 48 is further compressed in the high-pressure chamber-side passage 18b. The check valve 20 is pressed against the drop-off prevention plate 47. Further, a stepped portion 21b is formed on the outer periphery of the end of the valve body 21 on the high pressure chamber A side over the entire periphery. On the other hand, on the high pressure chamber A side of the piston 14, a bypass passage 49 is formed so as to communicate the high pressure chamber side passage 18b and the cavity portion 14a. In the figure, reference numeral 50 denotes a sealing O-ring externally fitted to the valve body 41 of the check valve 37.

  In the normal state, the check valve 20 presses the ball 22 against the inner wall of the ball accommodating portion 21a that leads to the cavity-side passage 18a against the spring force of the coil spring 48 with the internal pressure of the high-pressure chamber A when the door is closed. The cavity side passage 18a is closed so that the hydraulic oil on the high pressure chamber A side does not flow out to the low pressure chamber B side.

  FIG. 13 shows the position of the ball 22 when the door 22 is opened from the closed state, the ball 22 moves to the high pressure chamber A side, connects the high pressure chamber A and the low pressure chamber B, and opens the first passage 18. The hydraulic oil in the low pressure chamber B is flowing out into the high pressure chamber A.

  FIG. 14 shows the flow of hydraulic oil during normal times when the hand is released from the opened door 104. That is, during normal times, the first coil spring 15 that is compressed in the door open state is expanded by the repulsive force, and the piston 14 is contracted in the sealed space 3 a of the housing 3 by the spring force of the first coil spring 15. Move straight in the direction (right direction in FIG. 14). At this time, the first passage 18 is closed by the ball 22 of the check valve 20 being pressed against the inner wall of the ball accommodating portion 21a by the internal pressure of the high pressure chamber A. The end of the bypass passage 49 on the high pressure chamber A side is closed by the valve body 21. Accordingly, the hydraulic oil in the high pressure chamber A does not flow out to the low pressure chamber B through the first passage 18 and the bypass passage 49, but flows out to the low pressure chamber B through the speed adjustment valve 35 and a flow path (not shown).

  On the other hand, when an external force in the closing direction acts on the door 104 by forcibly closing the door 104 while it is closed, the spring force of the coil spring 48 is applied to the valve body 21 by the increased internal pressure of the high pressure chamber A. Against the low pressure chamber B side, the end of the bypass passage 49 on the high pressure chamber A side is opened, and the lower step 21b of the check valve 20 and the bypass passage 49 are connected to each other to connect the high pressure chamber A and the low pressure chamber. The hydraulic oil in the high pressure chamber A is discharged to the low pressure chamber B through the bypass passage 49 (see FIG. 15).

  According to the reference example 1, the number of parts is reduced by the amount that does not require a relief valve as compared with Patent Document 1 and the embodiment, and there is an advantage that the cost of the door closer 1 can be reduced. In the first reference example, since the check valve 20 performs the function of the relief valve 39, when an external force in the closing direction acts on the door 104 by forcibly closing the door 104 during closing, the high pressure chamber The increase in the internal pressure of A can be effectively suppressed, and damage to the hinge 105 of the door 104 and the upper frame 102 of the door opening 101 due to excessive force can be prevented as in the embodiment. .

(Reference Example 2)
16 and 17 show the door closer 1 according to the second reference example. In the reference example 2, a relief valve 51 having the same basic configuration as the relief valve 39 of the embodiment is inserted into the piston 14. The rest is the same as in the embodiment, so the same components are denoted by the same reference numerals, detailed description thereof is omitted, and only different points will be described below.

  That is, in this reference example 2, the relief valve 51 has a shaft-like shape in which a hook-shaped seat portion is formed to extend at one end of the shaft portion in the same manner as the shaft-shaped valve body 52, the ball 53, and the ball seat 42 of the embodiment. The valve body 52 is formed with a connecting passage 56 extending therethrough in the axial direction.

  On the other hand, an insertion hole 57 is formed in the piston 14, and the oil passage 58 extends continuously in a direction orthogonal to the insertion hole 57 and is connected to the hollow portion side passage 18 a of the first passage 18. The relief valve 51 is inserted into the insertion hole 57.

  When the door is closed, the relief valve 51 presses the ball 53 against the valve main body 52 against the spring force of the coil spring 55 by the internal pressure of the high pressure chamber A when the door is closed, and closes the communication path 56. Side hydraulic oil is prevented from flowing out to the low pressure chamber B side. The first passage 18 is closed by the ball 22 of the check valve 20 being pressed against the inner wall of the ball accommodating portion 21a by the internal pressure of the high pressure chamber A.

  When the door 104 is opened from this state, the ball 22 of the check valve 20 moves to the high-pressure chamber A side, opens the first passage 18, and connects the high-pressure chamber A and the low-pressure chamber B to operate the hydraulic oil in the low-pressure chamber B. Flows out into the high pressure chamber A. The communication path 56 of the relief valve 51 remains closed.

  FIG. 16 shows the flow of hydraulic oil during normal times when the hand is released from the opened door 104. That is, during normal times, the first coil spring 15 that is compressed in the door open state is expanded by the repulsive force, and the piston 14 is contracted in the sealed space 3 a of the housing 3 by the spring force of the first coil spring 15. Move in a straight line in the direction (right direction in FIG. 16). At this time, the first passage 18 is closed by the ball 22 of the check valve 20 being pressed against the inner wall of the ball accommodating portion 21a by the internal pressure of the high pressure chamber A. The communication path 56 of the relief valve 51 is still closed. Therefore, the hydraulic oil in the high pressure chamber A does not flow out to the low pressure chamber B through the first passage 18 and the communication path 56, but flows out to the low pressure chamber B through the speed adjustment valve 35 and a flow path (not shown) (see FIG. 16).

  On the other hand, when an external force in the closing direction is applied to the door 104 by forcibly closing the door 104 while it is closed, the spring force of the coil spring 55 is applied to the valve body 21 by the increased internal pressure of the high pressure chamber A. The high pressure chamber A is moved to the low pressure chamber B side to open the communication path 56, and the high pressure chamber A and the low pressure chamber B are communicated through the oil path 58 to discharge the hydraulic oil in the high pressure chamber A to the low pressure chamber B. (See FIG. 17).

  According to this reference example 2, although the position of the relief valve 39 cannot be adjusted as in Patent Document 1, the presence of the relief valve 51 allows the external force in the closing direction to be closed by forcibly closing the door 104 while it is being closed. When acting on the door 104, the pressure increase of the hydraulic oil in the high pressure chamber A is effectively suppressed, and damage to the hinge 105 of the door 104 and the upper frame 102 of the door opening 101 due to excessive force is prevented. It is the same as that of embodiment about what can be done.

  In the above embodiment, the opening / closing means of the relief valve 39 is configured by the ball 41 and the ball receiving seat 42, but the opening / closing means is configured only by the shaft member corresponding to the ball receiving seat 42 without the ball 41, You may make it open and close the connection path 40c of the valve main body 40 with this shaft member.

  In the above embodiment, the relief valve 39 is inserted into the second insertion hole 45 of the side wall 9 of the housing 3. However, the hydraulic oil in the high pressure chamber A can be discharged to the low pressure chamber B, and depending on the internal pressure. As long as the position can be adjusted, the insertion position of the relief valve 39 is not limited.

  The present invention is useful for a door closer (door self-closing device) that slowly and automatically closes an open door.

It is a front view of the state where the door closer concerning an embodiment was attached to a door. It is a right view of FIG. It is a top view of FIG. It is sectional drawing in the IV-IV line of FIG. FIG. 5 is a right side view of FIG. 4. FIG. 5 is a left side view of FIG. 4. It is sectional drawing in the VII-VII line of FIG. It is sectional drawing in the VIII-VIII line of FIG. It is sectional drawing in the IX-IX line | wire of FIG. 5 which shows the flow of the hydraulic oil accompanying the door closing operation at the normal time. FIG. 10 is a view corresponding to FIG. 9 illustrating a flow of hydraulic oil when an external force in the closing direction is applied to the door during the closing operation. The change in the internal pressure of the high pressure chamber when the door is closed is shown. (A) is a normal time, (b) is when the relief valve is operated, and (c) is a normal time of the conventional example. FIG. 9 is a view corresponding to FIG. 8 showing a state where the relief valve is not operated. FIG. 8 is a view corresponding to FIG. 7 of Reference Example 1. FIG. 10 is a diagram corresponding to FIG. 9 of Reference Example 1. FIG. 11 is a view corresponding to FIG. 10 of Reference Example 1. FIG. 10 is a diagram corresponding to FIG. 9 of Reference Example 2. FIG. 11 is a diagram corresponding to FIG. 10 of Reference Example 2.

Explanation of symbols

A High pressure chamber B Low pressure chamber 1 Door closer 3 Housing 3a Sealed space 14 Piston 15 First coil spring (piston biasing means)
20 Check valve 23 Rack and pinion mechanism 26 Rotating shaft 28 Link mechanism 35 Speed adjustment valve 39 Relief valve 40 Valve body 41 Ball (opening / closing means)
42 Ball seat (opening / closing means)
43 Second coil spring (open / close biasing means)
45 2nd insertion hole 45b Bottom 40c of 2nd insertion hole Communication path 101 Door opening part 102 Upper frame 104 Door

Claims (4)

A housing having a sealed space filled with hydraulic oil;
A piston that is reciprocally moved in a state of being biased by the piston biasing means in the sealed space, and that divides the sealed space into a high-pressure chamber and a low-pressure chamber;
A check valve provided in the piston for communicating / blocking the high pressure chamber and the low pressure chamber;
A rack and pinion mechanism incorporated in the piston;
A rotating shaft connected integrally to the pinion of the rack and pinion mechanism so as to penetrate the housing up and down;
A link mechanism having one end connected to the upper end of the rotating shaft and the other end connected to the upper frame side of the door opening of the building;
A speed adjustment valve that is inserted into the housing and adjusts the closing speed of the door by controlling the flow rate of hydraulic oil flowing out from the high pressure chamber to the low pressure chamber in conjunction with the movement of the piston;
When the door is opened, the rotational movement is converted into a linear movement of the piston via the link mechanism, the rotary shaft and the rack and pinion mechanism, and the piston is resisted against the biasing force of the piston biasing means. To move the hydraulic oil from the low-pressure chamber to the high-pressure chamber through the check valve, accumulate the force to move in the door closing direction, and release the hand from the door to move the piston to the piston. The urging force of the urging means moves in the high pressure chamber shrinking direction in the sealed space of the housing, and the hydraulic oil in the high pressure chamber flows out to the low pressure chamber via the speed adjustment valve, so that the door is slowly and automatically closed. A door closer,
During normal times, the housing shuts off the high pressure chamber and the low pressure chamber, and when an external force in the closing direction acts on the door while the door is closed, the high pressure chamber and the low pressure chamber communicate with each other. A door closer characterized in that a relief valve that discharges hydraulic oil from the high-pressure chamber to the low-pressure chamber is provided so as to be switchable between a state where it can be opened and closed and a state where it cannot be opened. The door closer according to claim 1,
An insertion hole is formed in the housing so as to connect the high pressure chamber and the low pressure chamber,
The relief valve is inserted into the insertion hole so that the position thereof can be adjusted by a forward / backward operation from the outside,
The door closer is configured so that the opening and closing operation timing can be freely changed according to the internal pressure of the high pressure chamber by adjusting the position in a state where the relief valve can be opened and closed. The door closer according to claim 2,
The relief valve includes a shaft-shaped valve body that is formed so that a communication path is opened at a tip and can be adjusted by advancing and retreating operation, an opening / closing means that opens and closes the communication path, and an opening / closing mechanism that biases the opening / closing means. Power means,
In a state where the opening / closing operation is possible, during normal times, the opening / closing means is pressed against the tip of the valve body by the urging force of the opening / closing urging means to close the communication path and shut off the high pressure chamber and the low pressure chamber, while the door is closed. When an external force in the closing direction acts on the door halfway, the opening / closing means is moved away from the valve body tip against the urging force of the opening / closing urging means by the internal pressure of the high pressure chamber, and the communication path is opened. The door closer is configured to communicate with the low pressure chamber and to discharge the hydraulic oil in the high pressure chamber to the low pressure chamber. The door closer according to claim 3,
In a state in which the relief valve cannot be opened, the relief valve is configured to advance the valve body, press the opening / closing means so as to contact the bottom of the insertion hole, and close the communication path of the valve body by the opening / closing means. A door closer.

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