JP6542682B2 - Door closer - Google Patents

Description

  The present invention relates to a door closer.

  In Patent Document 1 below, a recess is formed on the upper end surface of the door, and the door closer is attached to the door so that the door closer is accommodated in the recess, and a guide rail is attached to the lower surface of the upper frame of the door frame A configuration has been proposed in which one end of the link is attached to the rotation shaft of the door closer main body, and the other end of the link is provided with a turning piece guided by the guide rail. In the door closer of this configuration, as the door opens, the link rotates relative to the door closer body, and the pivoting piece moves in the guide rail, and the link closer from the door closer body rotates. The shaft is provided with an arm rotational force for rotating the link in the return direction. Therefore, the door automatically returns to the closed state.

  However, in such a configuration, the door closer becomes large and complicated in order to provide a large door closer body. And although the door closer body is embedded in the door, in order to be able to embed the door closer body, the door must also be thick. Also, a large force is required to open the door.

Utility model registration 2606465 gazette

  Therefore, the present invention is made in view of the above-mentioned conventional problems, and an object of the present invention is to provide a door closer which can be simplified and downsized, and can be opened by a light force.

  The present invention has been made to solve the above-mentioned problems, and a door closer according to the present invention is a door closer for closing a door rotating about a vertical axis, wherein one of the door frame or the door is closed. A guide rail to be attached, a slider guided to slide on the guide rail, and a link arm rotatably coupled to the other of the door frame or the door and the slider, the link arm when the door starts to open Is characterized in that the slider is provided with rotational force application means for applying an arm rotational force for rotating the link arm in a direction opposite to the predetermined direction with respect to the slider. Do.

  In the door closer of this configuration, for example, a guide rail is attached to the door frame, and the link arm is connected to the door and the slider. Since the slider is provided with the rotational force application means for applying the arm rotational force to the link arm, the door closer main body as in the prior art is not necessary, and the whole configuration can be simplified and miniaturized. Then, since the slider that is guided by the guide rail and slides is provided with the rotational force application means, the arm rotational force is applied to the link arm by the rotational force application means, and the arm rotational force applied to the link arm is It will act on the door through the rotary shaft connecting the link arm and the door. The arm rotational force acts in the direction orthogonal to the link arm. The component force when the arm rotational force is decomposed in the direction orthogonal to the straight line connecting the rotation axis connecting the link arm and the door and the rotation center of the door is the force for rotating the door. This force is referred to as a door rotational force.

  The slider, the link arm, and the door constitute a reciprocating slider crank mechanism within the rotational angle range of the door. Therefore, in the section during which the door opens from the closed state to the predetermined opening angle, the direction of the arm rotational force is gradually in the direction of the straight line connecting the rotation axis connecting the link arm and the door and the rotation center of the door As the door approaches a predetermined opening angle, a straight line connecting the rotation axis connecting the link arm and the door to the rotation center of the door, the rotation axis connecting the link arm and the door, and the link arm The angle between the slider and the axis of rotation connecting the slider is 90 degrees, and the direction of the arm rotational force coincides with the line connecting the axis of rotation connecting the link arm and the door to the center of rotation of the door It will be done. Therefore, the closing force, which is also a rotational moment for rotating the door in the closing direction, becomes smaller as it approaches the predetermined opening angle, and becomes zero at the predetermined opening angle. Then, when the door is further opened, the door rotational force acts in the direction to open the door, and a rotational moment acts on the door in the opening direction.

  In particular, it is preferable that the arm rotational force be smaller in the state in which the door is opened by a predetermined angle than in the closed state. If the arm rotational force is smaller at the door opening by a predetermined angle than at the closed state, the arm rotational force is much more than when the arm rotational force is constant or gradually increases with the opening operation of the door. The door can be opened with light force.

  Furthermore, the rotational force application means includes a drive arm that rotates integrally with the link arm around a rotation axis that rotatably couples the slider and the link arm, and the slide direction of the slider as the central line direction. And a coil spring for pressing the drive arm to apply an arm rotational force, and when the link arm rotates in the predetermined direction, the drive arm rotates so as to reduce the angle with the center line of the coil spring Is preferred. In this configuration, the coil spring applies a pressing force (spring force) to the drive arm so that a rotational moment acts on the drive arm in a direction opposite to the predetermined direction. That is, when the coil spring presses the drive arm, an arm rotational force acts on the link arm. Then, when the drive arm rotates with the opening operation of the door, the angle between the drive arm and the center line of the coil spring decreases, so the rotational moment generated on the drive arm decreases and acts on the link arm. Arm rotation force also decreases. Therefore, the door can be opened with a lighter force.

  Furthermore, it is preferable that the rotating shaft is provided at a position offset in the horizontal direction and the orthogonal direction with respect to the center line of the coil spring. The drive arm can be easily disposed on the slider by disposing the rotation axis connecting the slider and the link arm offset with respect to the center line of the coil spring.

  Also, the rotational force applying means includes a spring for generating an arm rotational force, and locking means for locking and unlocking the spring in a predetermined state, and the arm rotational force when the spring is locked in a predetermined state Preferably does not act on the link arm, but the arm rotational force acts on the link arm when the spring is unlocked. For example, when attaching or removing a door closer, work is performed with the door open. At this time, the arm rotation force is applied to the link arm by locking the spring in a predetermined state by the locking means. It does not work. Accordingly, the door closer can be easily attached and removed.

  In addition, if it illustrates about a typical preferable form, a rotational force provision means is the drive arm rotated integrally with a link arm centering | focusing on the rotating shaft which connects a slider and a link arm rotatably, Link Preferably, the coil spring includes a coil spring for pressing the drive arm to apply an arm rotational force to the arm, and the lock means locks the coil spring in a predetermined compression state. Furthermore, in a state where the lock means locks the coil spring in a predetermined compression state, a straight line connecting the rotation axis connecting the link arm and the door to the rotation center of the door, the rotation axis connecting the link arm and the door, and the link It is preferable that an angle between a straight line connecting an arm and a rotation axis connecting the slider be approximately 90 degrees. In addition, it is preferable that a damper that cushions the slider in a state of coming into contact with the slider before the door is fully closed and from there to the fully closed state is attached and fixed at a predetermined position of the guide rail.

  As described above, in the door closer according to the present invention, since the slider is provided with the rotational force applying means, the structure of the door closer can be simplified and miniaturized, and the door can be opened with a light force. it can.

The schematic diagram seen from the bottom side which shows typically the door closer in 1st embodiment of this invention. Sectional drawing seen from the front side which shows the slider of a door closer. The bottom view which shows the slider of the same door closer. The slider of the door closer is shown, (a) is a right side view, (b) is an AA sectional view of FIG. It is a figure which shows the use condition of the same door closer, Comprising: It is sectional drawing seen from the front side which shows the closing state (The opening angle of a door is the state of 0 degree). (A) And (b) is a principal part enlarged view of FIG. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the closed state (The open angle of a door is the state of 0 degree). It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state whose opening angle of a door is 90 degrees. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state whose opening angle of a door is 180 degrees. The principal part enlarged view of FIG. The principal part enlarged view of FIG. The principal part enlarged view of FIG. It is a schematic diagram which shows the force which acts on each part in the use condition of the same door closer, and (a) shows a closed door state (the open angle of a door is the state of 0 degree), (b) shows the open angle of a door 10 degrees Indicates the state of It is a schematic diagram which shows the force which acts on each part in the use condition of the same door closer, (a) shows the state where the opening angle of a door is 20 degrees, (b) shows the state where the opening angle of a door is 30 degrees . It is a schematic diagram which shows the force which acts on each part in the use condition of the same door closer, (a) shows the state where the opening angle of a door is 60 degrees, (b) shows the state where the opening angle of a door is 70 degrees. . It is a schematic diagram which shows the force which acts on each part in the use condition of the same door closer, (a) shows the state where the opening angle of a door is 80 degrees, (b) shows the state where the opening angle of a door is 90 degrees. . It is a schematic diagram which shows the force which acts on each part in the use condition of the same door closer, (a) shows the state where the opening angle of a door is 100 degrees, (b) shows the state where the opening angle of a door is 120 degrees. . It is a schematic diagram which shows the force which acts on each part in the use condition of the same door closer, (a) shows the state where the opening angle of a door is 150 degrees, (b) shows the state where the opening angle of a door is 180 degrees. . The bottom view which shows the slider of the door closer in 2nd embodiment of this invention. FIG. 20 is a cross-sectional view taken along the line B-B in FIG. EE sectional drawing of FIG. (A) is CC sectional drawing of FIG. 19, (b) is DD sectional drawing of FIG. Sectional drawing corresponding to FIG. 20 which shows the locked state of the slider of the door closer. Sectional drawing corresponding to FIG. 21 which shows the locked state of the slider of the door closer. The bottom view which shows the rail of the same door closer. (A) is FF sectional drawing of FIG. 25, (a) is GG sectional view of FIG. 25, (a) is HH sectional view of FIG. (A) And (b) is a principal part bottom view which shows the locked state of the slider of the door closer. It is a figure which shows the use condition of the same door closer, Comprising: Sectional drawing seen from the front side which shows a closed door state. It is a figure which shows the use condition of the same door closer, Comprising: The external view which looked at the door closer in a closed door state from the bottom side. It is a figure which shows the use condition of the same door closer, and the figure which looked at the slider and damper in the closing state from the bottom face side. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state whose opening angle of a door is 70 degrees. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state whose opening angle of a door is 90 degrees. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state whose opening angle of a door is 180 degrees. The principal part enlarged bottom view corresponding to FIG. The principal part enlarged bottom view corresponding to FIG. The principal part enlarged bottom view corresponding to FIG. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state in the middle of closing. It is a figure which shows the use condition of the door closer in other embodiment of this invention, Comprising: The bottom view which shows the state whose opening angle of a door is 70 degrees. It is a figure which shows the use condition of the same door closer, Comprising: The bottom view which shows the state whose opening angle of a door is 90 degrees.

  Hereinafter, a door closer according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 18. FIG. 1 is a schematic view of the door closer according to the present embodiment as viewed from the bottom side. The door closer in this embodiment is used for a door 90 that rotates about a vertical axis, and has a fixed guide rail 1, a slider 2 that is guided to slide by the guide rail 1, and one end portion A link arm 3 is rotatably connected to the door 90 and has the other end rotatably connected to the slider 2. The link arm 3 and the door 90 are rotatably connected via a first rotation shaft 82, and the link arm 3 and the slider 2 are rotatably connected via a second rotation shaft 20. The door 90 rotates in the horizontal direction about the rotation center 91a to open and close.

  When the door 90 opens in the direction indicated by the arrow 101, the link arm 3 rotates in the direction indicated by the arrow 201, and the slider 2 moves in the direction indicated by the arrow 301. Conversely, when the door 90 closes in the direction indicated by the arrow 102, the link arm 3 rotates in the direction indicated by the arrow 202, and the slider 2 moves in the direction indicated by the arrow 302. Thus, the door closer together with the door 90 constitutes a reciprocating slider crank mechanism (link mechanism). When the opening angle of the door 90 is approximately 90 degrees and the straight line 4 connecting the first rotation shaft 82 and the rotation center 91 a of the door 90 is in a state perpendicular to the sliding direction of the slider 2, the link arm 3 The rotation angle in the direction of the arrow 201 is maximized. And when the door 90 opens beyond about 90 degrees, as the door 90 opens beyond about 90 degrees, the link arm 3 is in the opposite direction to the direction of the arrow 201 in reverse. It rotates in the direction of arrow 202. Thus, the link arm 3 rotates in the direction of the arrow 201 with respect to the slider 2 in the section until the door 90 reaches the predetermined opening angle from the closing state when the door is opened, and the door 90 opens in the predetermined direction when the door is closed. The link arm 3 rotates in the direction of the arrow 202 with respect to the slider 2 in the section from the angle to the closing state. Here, the predetermined opening angle of the door 90 means the link arm 3 (a straight line connecting the first rotation shaft 82 and the second rotation shaft 20), the first rotation shaft 82, and the rotation center 91a of the door 90. Is the opening angle of the door 90 when the straight line 4 connecting the two is at a right angle. The door closer is provided with a rotational force application means (not shown in FIG. 1) in the slider 2. The rotational force application means applies an arm rotational force 51 to the link arm 3 to rotate the link arm 3 in the direction of the arrow 202, which is the direction opposite to the direction of the arrow 201.

  An example of a specific configuration of the door closer will be described below. FIG. 5 is a view from the front side, and FIG. 7 is a view from the bottom side. As shown in FIGS. 5, 7 and 8, the door 90 rotates about a vertical axis. The thickness direction of the door 90 is referred to as the front-rear direction, and the side where the door 90 is opened is referred to as the front side (front side) and the side where the door 90 is closed is referred to as the back side (rear side).

  The door 90 is rotatably attached to the vertical frame 92 of the door frame via a hinge 94 and rotates in the horizontal direction. The portion hatched in FIG. In the present embodiment, the door 90 is configured to be able to rotate up to 180 degrees, and the hinge 94 is configured to be capable of rotating 180 degrees correspondingly, and has the first and second rotation centers 91a and 91b. However, FIG. 7 shows only the first rotation center 91a. The first rotation center 91 a is a rotation center in a section where the opening angle of the door 90 is from 0 degrees to 90 degrees. The second rotation center 91 b is a rotation center in a section where the opening angle is from 90 degrees to 180 degrees, which will be described later. FIG. 7 is a view of the upper frame portion 93 as viewed from the lower side, but in the figure, the door 90 rotates clockwise when it is opened.

  As shown in FIG. 5, a shallow concave notch 95 is formed on the upper end surface of the door 90. The depth of the notch 95 corresponds to the thickness of the link arm 3 and is such a depth that the link arm 3 gets into the notch 95 and most of it is hidden. The notch 95 has a long shape along the radial direction of rotation of the door 90 and has a length sufficient to accommodate the entire link arm 3. The radial direction of rotation of the door 90 is the longitudinal direction of the upper end surface of the door 90. Further, the notch 95 is formed on the upper end surface of the door 90 on the side closer to the first rotation center 91 a of the door 90 (the proximal end side of the door 90).

  The link arm 3 is attached to the door 90 so as to be accommodated in the notch 95 in the closed state as shown in FIG. The link arm 3 is smaller in thickness with respect to its width and thus in the shape of a long plate, the thickness is about the same as the depth of the notch 95, the width is smaller than the thickness of the door 90, and , The length is shorter than the total length of the notch 95. As shown in FIG. 5, one end of the link arm 3 is rotatably connected to a portion of the notch 95 of the door 90 on the side closer to the first rotation center 91 a of the door 90.

  Specifically, as shown in FIG. 6 (b), in the notch 95 of the door 90, the portion near the first rotation center 91 a of the door 90 is embedded so as to be embedded in the bottom of the notch 95. The plate 80 is attached by screws 81, and the upper surface of the support plate 80 is substantially flush with the bottom surface of the notch 95. A first rotation shaft 82 is attached to the support plate 80, and one end of the link arm 3 is rotatably supported by the first rotation shaft 82. The lower part of the first rotation shaft 82 is screwed to the support plate 80, the upper part protrudes upward from the support plate 80, and the axis thereof is in the vertical direction. Further, the first rotation shaft 82 has a flanged structure, that is, a flange portion 82a is integrally formed at the upper end portion thereof, and the link arm 3 is pulled upward from the first rotation shaft 82. The hook portion 82a prevents the detachment. A washer 83 is interposed between the link arm 3 and the support plate 80. In addition, a counterbore 3a is formed on the upper surface of one end of the link arm 3, and the lower most part of the flange portion 82a of the first rotation shaft 82 is inserted into the counterbore 3a. The amount by which the flange portion 82a of the first rotation shaft 82 protrudes upward from the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of the upper surface of The link arm 3 is rotatably supported by the first rotation shaft 82, and a bush 85 made of metal or resin is interposed between the link arm 3 and the first rotation shaft 82.

  As shown in FIG. 6A, the other end of the link arm 3 is attached to the lower end of the second rotation shaft 20, and the link arm 3 rotates integrally with the second rotation shaft 20. Specifically, the lower end portion of the second rotation shaft 20 is D-cut on the peripheral surface 180 degrees opposite to each other as described later, and the other end portion of the link arm 3 corresponds to the shape thereof. A non-circular through hole which is not a round hole is formed, and the lower end portion of the second rotating shaft 20 is inserted through the non-circular through hole, and the lower end surface of the second rotating shaft 20 is screwed with a washer 21 interposed therebetween. 22 is screwed in from the lower side to prevent the link arm 3 from falling downward. The screw 22 and the washer 21 are not shown in FIG. 7 or the like as viewed from the bottom side. Thus, the link arm 3 rotates integrally with the second rotation shaft 20 about the second rotation shaft 20. In addition, the counterbore hole 3b is formed in the lower surface of the link arm 3, and the protrusion amount below the head of the screw 22 is suppressed by this counterbore hole 3b.

  The guide rail 1 is attached to the upper frame portion 93 of the door frame, and in the attached state, the longitudinal direction of the guide rail 1 is along the longitudinal direction of the upper frame portion 93. Specifically, the guide rail 1 is attached to the inside of the upper frame 93 so as to be built in the upper frame 93, and the lower surface of the guide rail 1 and the lower surface of the upper frame 93 are substantially flush with each other. Become. In the closed state, the longitudinal direction of the guide rail 1 coincides with the rotational radius direction of the door 90. The guide rail 1 has a rectangular tubular shape as a whole, and both ends are open in the present embodiment. A portion of the lower plate portion 1a of the guide rail 1, in particular, approximately half of the front side of the lower plate portion 1a is cut open and the lower portion of the second rotation shaft 20 protrudes downward from the opening portion It is possible. The guide rail 1 is longer than the slider 2 and longer than the link arm 3. The guide rail 1 is preferably made of metal, and is preferably formed into a rectangular cylindrical shape by bending a sheet metal, or a rectangular cylindrical extruded material is used.

  Next, the slider 2 will be described. The structure of the slider 2 is shown in FIGS. The slider 2 includes a housing 23 which is guided to slide on the inner surface of the guide rail 1. The housing 23 is preferably formed of a synthetic resin having excellent slidability, in particular, a self-lubricating resin. The second rotary shaft 20 is rotatably supported by the housing 23. The second rotation shaft 20 has an axis in the vertical direction, and its upper end is supported by the housing 23 via the bush 24 as also illustrated in FIG. 6A. On the other hand, the lower end portion of the second rotation shaft 20 is supported via a bush 26 on a support base 25 attached to the housing 23 from below by a screw 19. The second rotation shaft 20 is located substantially at the center of the housing 23 in the longitudinal direction. Further, the second rotation shaft 20 is not positioned at the center in the front-rear direction of the housing 23 in the bottom view or the plan view, but is positioned at the front side or the rear side in the present embodiment. , Offset to the front side (front side). The bushes 24 and 26 are preferably made of synthetic resin having excellent slidability, particularly self-lubricating resin.

  The housing 23 has a long shape along the longitudinal direction of the guide rail 1, and the second rotation shaft 20 is located substantially at the center of the longitudinal direction. Further, coil springs 27 a and 27 b are incorporated at one end side of the housing 23 in the longitudinal direction, and a damper 28 is incorporated at the other end side of the housing 23 in the longitudinal direction. The longitudinal direction of the housing 23 may be referred to as the left and right direction, and one end side in the longitudinal direction may be referred to as the right side and the other end side as the left side. In relation to the door 90, the coil springs 27a and 27b are located on the base end side of the door 90 which is the side close to the first rotation center 91a, and the damper 28 is far from the first rotation center 91a of the door 90. It is located on the tip side which is the side.

  A drive arm 29 extending to one end of the housing 23 and a braking arm 30 extending to the other end of the housing 23 are integrally formed on the second rotation shaft 20. That is, the second rotation shaft 20, the drive arm 29, and the braking arm 30 are formed as one member. The second rotary shaft 20, the drive arm 29, and the braking arm 30 are preferably made of metal. The drive arm 29 and the braking arm 30 rotate integrally with the second rotation shaft 20. Specifically, the drive arm 29 and the braking arm 30 swing within a predetermined angle range around the second rotation shaft 20. The driving arm 29 and the braking arm 30 both extend radially outward from the second rotation shaft 20, but both are not opposite to each other at 180 degrees, but in a bottom view or a plan view. A predetermined angle less than 90 degrees is deviated with respect to the arrangement form facing 180 degrees so as to become a letter shape. Therefore, the angle between the drive arm 29 and the braking arm 30 is, for example, not less than 135 degrees and less than 180 degrees. In the present embodiment, the second rotation shaft 20, the drive arm 29, and the braking arm 30 are formed as one member, but may be separately attached and integrated after being formed separately. .

  The drive arm 29 extends from the second rotation shaft 20 toward the coil springs 27a and 27b, and a connecting pin 31 extending in the vertical direction is attached and fixed to the tip of the drive arm 29. Hereinafter, the connection pin 31 is referred to as a drive side connection pin 31. The drive arm 29 is bifurcated into two branches at its tip end side, and the drive side connection pin 31 is attached so as to connect the tips of the pair of upper and lower bifurcated portions 29a up and down. . Between the second rotary shaft 20 and the coil springs 27a and 27b, a spring receiving block 32 for receiving a pressing force (spring force) from the coil springs 27a and 27b and transmitting it to the drive arm 29 is provided. . The spring receiving block 32 is guided by the inner surface of the housing 23 and is movable along the longitudinal direction of the housing 23. That is, the spring receiving block 32 slides on the inner surface of the housing 23. An elongated hole 33 is formed in the spring receiving block 32, and the drive pin 31 is inserted through the elongated hole 33. The long holes 33 formed in the spring receiving block 32 will be hereinafter referred to as long holes 33 on the drive side. The drive arm 29 and the spring support block 32 are rotatably coupled about an axis in the vertical direction by the coupling pin 31 on the drive side.

  The other end side of the spring receiving block 32 is a thin plate-like portion 32a in the vertical direction, the plate-like portion 32a is located between the forked portions 29a of the drive arm 29, and the plate-like portion 32a. A long hole 33 on the drive side is formed. The drive-side long hole 33 extends at a predetermined angle with respect to the longitudinal direction of the housing 23 in a bottom view or a plan view. Although the second rotary shaft 20 is arranged to be offset to the front side, the end on the front side of the long hole 33 on the drive side is close to the second rotary shaft 20, and the end on the rear side is second It inclines so as to be far from the second rotation axis 20. A circular recess is formed on one end surface of the spring receiving block 32, and the other ends of the coil springs 27a and 27b are fitted into the recess.

  The coil springs 27a and 27b are for rotating the link arm 3 in the direction of the arrow 202 shown in FIG. The coil springs 27a and 27b are compression springs, and the expansion and contraction direction thereof is the longitudinal direction of the housing 23, the longitudinal direction of the guide rail 1, and hence the sliding direction of the slider 2. As described above, the second rotation shaft 20 is offset to the front side with respect to the center of the housing 23 (slider 2) in the front-rear direction. On the other hand, the center line of the coil springs 27a and 27b is located at the center of the housing 23 in the front-rear direction. Therefore, the second rotation shaft 20 is displaced in the front-rear direction with respect to the center line of the coil springs 27a and 27b, and specifically, on the front side (front side) with respect to the center line of the coil springs 27a and 27b. Misaligned.

  The configuration of the coil springs 27a and 27b may be various, but in the present embodiment, the coil springs 27a and 27b have a double configuration including first and second coil springs 27a and 27b having different diameters, and the first and second coil springs 27a and 27b Are arranged coaxially inside and outside so as to make the center lines of each other identical. That is, the second coil spring 27b having a small diameter is inserted inside the first coil spring 27a having a large diameter. The wire diameter of the first coil spring 27a located outside is larger than that of the second coil spring 27b located inside.

  One end side predetermined regions of the coil springs 27a and 27b are inserted into the cylindrical coil holder 34. The coil holder 34 has a tubular shape with one end closed and the other end opened, and the center line (axis) thereof coincides with the center of the housing 23 in the front-rear direction, and thus the coil holder 34 The coil springs 27a and 27b are coaxially located. A holder insertion hole is formed on one end side of the housing 23, and the holder insertion hole opens at one end surface of the housing 23. The coil holder 34 is rotatably inserted into the holder insertion hole, and the outer peripheral surface of the coil holder 34 is in contact with the inner peripheral surface of the holder insertion hole. A cross-shaped groove 34a is formed on one end surface of the coil holder 34 as shown in FIG. 4A, and the coil holder 34 is formed by engaging the tip of a tool such as a flathead screwdriver with the groove 34a. It can be rotated about an axis. A male screw portion is formed on the outer peripheral surface on the other end side of the coil holder 34, and a nut 35 is screwed into the male screw portion. The nut 35 is fixed to the inner surface of the housing 23 so as not to move. Therefore, when the coil holder 34 is rotated about its axis, the coil holder 34 rotates and moves along its axial direction. Thereby, the separation distance between the spring receiving block 32 and the coil holder 34 can be extended and adjusted, and the initial compression amount of the coil springs 27a and 27b interposed between the two can be adjusted. A disc-like spacer 36 is interposed between one end of the coil springs 27 a and 27 b and the coil holder 34. In the present embodiment, the drive arm 29, the connection pin 31 on the drive side, the spring receiving block 32, and the coil springs 27a and 27b constitute a rotational force applying means. Further, the nut 35 and the coil holder 34 constitute a rotational force adjustment means for adjusting the magnitude of the arm rotational force 51.

  The braking arm 30 extends toward the damper 28 located opposite to the coil springs 27a and 27b with respect to the second rotation shaft 20. A connecting pin 37 extending in the vertical direction is attached and fixed to the tip of the braking arm 30. Hereinafter, the connection pin 37 is referred to as a connection pin 37 on the braking side. The braking arm 30 is bifurcated into a fork-shaped predetermined area, and a braking pin 37 is attached on the braking side so as to connect the upper and lower ends of the pair of forks 30a in the vertical direction. . Between the second rotary shaft 20 and the damper 28, an extraction block 38 is provided for moving the damper 28 back and forth and transmitting the braking force of the damper 28 to the braking arm 30. The withdrawal block 38 is guided by the inner surface of the housing 23 and is movable along the longitudinal direction of the housing 23. That is, the withdrawal block 38 slides on the inner surface of the housing 23. A long hole 39 is formed in the withdrawal block 38, and the connection pin 37 on the braking side is inserted through the long hole 39. The elongated holes 39 formed in the advancing and retracting block 38 are hereinafter referred to as the elongated holes 39 on the braking side. The braking arm 30 and the advancing and retracting block 38 are rotatably coupled about an axis in the vertical direction by the coupling pin 37 on the braking side.

  One end side of the withdrawal block 38 is a thin plate-like portion 38a in the vertical direction, the plate-like portion 38a is located between the forked portions 30a of the braking arm 30, and the plate-like portion 38a is braked A side slot 39 is formed on the side. The long hole 39 on the braking side extends at a predetermined angle with respect to the longitudinal direction of the housing 23 in a bottom view or a plan view. The second rotary shaft 20 is arranged to be offset to the front side, but the long hole 39 on the braking side is close to the second rotary shaft 20 at the front end and the rear end is the second one. It inclines so as to be far from the second rotation axis 20. That is, in the bottom view or the plan view, the long hole 33 on the drive side and the long hole 39 on the braking side are in a left-right symmetrical relationship with the second rotation shaft 20 as the center. The tip end portion of the main shaft 28a of the damper 28 is attached to the other end of the withdrawal block 38, and the withdrawal block 38 and the main shaft 28a of the damper 28 integrally reciprocate along the longitudinal direction of the housing 23.

  The damper 28 is for braking the rotation of the second rotation shaft 20, and since the link arm 3 rotates integrally with the second rotation shaft 20, the rotation of the link arm 3 is braked. It is also for. The damper 28 is disposed on the same line as the center line of the coil springs 27a and 27b. The damper 28 is incorporated in the housing 23, and the other end protrudes out of the housing 23. The main shaft 28a of the damper 28 extends toward one end of the housing 23 and is configured to be able to move out with respect to the damper main body 28b. While pulling it out from the damper main body 28b requires a small force, it pushes back to the damper main body 28b Sometimes the load increases, ie the braking force works. The main shaft 28 a of the damper 28 is inserted into the other end of the advancing and retracting block 38, and its tip end is exposed in a recess formed on the upper surface of the exiting and retracting block 38 and is retained by the washer 40. Further, a spacer 41 is interposed between the tip end surface of the main shaft 28 a of the damper 28 and the wall surface of the recess of the retracting block 38. Thus, the main shaft 28 a of the damper 28 is attached and fixed to the retracting block 38, and moves integrally with the retracting block 38. In the present embodiment, the braking arm 30, the connection pin 37 on the braking side, the retracting block 38, and the damper 28 apply a braking force to the link arm 3 when the link arm 3 rotates in the direction of the arrow 202 in FIG. The braking force application means is configured.

  Next, the movement of each part of the door closer when the door 90 is opened will be described. 7 to 9 show the overall movement of the door closer when the door 90 is opened, and FIGS. 10 to 12 show enlarged views in the vicinity of the second rotation shaft 20. 7 and 10 show a closed state in which the opening angle is 0 degrees, FIGS. 8 and 11 show a state in which the opening angle is 90 degrees, and FIGS. 9 and 12 show a state in which the opening angle is 180 degrees.

  In the closed state shown in FIG. 7, the slider 2 is at a position farthest from the first rotation center 91 a of the door 90, and the link arm 3 is in a state along the door 90, specifically in a state parallel to the door 90 is there. In the closed state, as shown in FIG. 10, the braking arm 30 is in the state of being rotated most to the front side, and is in the state along the longitudinal direction of the housing 23. More specifically, the braking arm 30 and the second The rotational axes 20 of the front and rear direction are substantially the same in the longitudinal direction. The connection pin 37 on the braking side is located at the front end of the long hole 39 on the braking side. Therefore, the advancing and retracting block 38 is pushed to the other end side by the braking arm 30 and located at the most other end side, and the main shaft 28a of the damper 28 is pushed back to the damper main body 28b.

  On the other hand, the drive arm 29 is in the state of being rotated most to the rear side, and is in the state of being maximally inclined to the rear side with respect to the longitudinal direction of the housing 23. At this time, the angle between the drive arm 29 and the center line of the coil springs 27a and 27b, which is the angle between the drive arm 29 and the longitudinal direction of the housing 23, is the largest. The drive-side connection pin 31 is located at the rear end of the long hole 33 on the drive side. Therefore, the spring receiving block 32 is pulled to the other end side by the drive arm 29 and is positioned at the other end most, and the coil springs 27a and 27b are in the initial state in which the amount of compression is the smallest. The amount of compression of the coil springs 27a and 27b in this initial state can be adjusted in size by rotating the coil holder 34.

  The door 90 rotates about the first rotation center 91a while the opening angle of the door 90 is from 0 degrees to 90 degrees. When the door 90 is opened from the closed state, the link arm 3 is pivoted to the front side about the second rotation shaft 20 in conjunction with the opening operation of the door 90. In the view from the bottom side, the link arm 3 rotates counterclockwise. When the opening angle of the door 90 is 90 degrees, as shown in FIG. 8, the rotation angle of the link arm 3 is close to the maximum. In the present embodiment, the first rotation shaft 82 is located at the center of the door 90 in the front-rear direction, while the first rotation center 91 a of the door 90 is offset on the front side (front side) of the door 90 Specifically, the first rotation shaft 82 and the first rotation center 91a of the door 90 are connected even when the opening angle of the door 90 becomes 90 degrees, because it is located at the end on the front side. The angle between the straight line 4 and the link arm 3 is not 90 degrees but an angle slightly smaller than that (approximately 80 degrees in the present embodiment). Therefore, when the opening angle of the door 90 is 90 degrees, the rotation angle of the link arm 3 is not maximum but is close to the maximum. Along with the rotational movement of the link arm 3, the slider 2 is gradually slid toward one end while being guided by the guide rail 1.

  When the opening angle of the door 90 is 90 degrees, as shown in FIG. 11, the braking arm 30 is in the state of being rotated most to the back side, and is in the state of being maximally inclined to the back side with respect to the longitudinal direction of the housing 23 It is in. The connection pin 37 on the braking side is located at the rear end of the long hole 39 on the braking side. Accordingly, the advancing and retracting block 38 is pulled to one end by the braking arm 30 and positioned at the one end, and the main shaft 28a of the damper 28 is in the state of being drawn out from the damper main body 28b.

  On the other hand, when the opening angle of the door 90 is 90 degrees, the drive arm 29 is in the state of being rotated most to the front side and is in the state along the longitudinal direction of the housing 23. The positions of the second rotary shaft 20 in the front-rear direction are substantially the same. At this time, the angle between the drive arm 29 and the center line of the coil springs 27a and 27b is the smallest and substantially zero. That is, the drive arm 29 is substantially parallel to the center line of the coil springs 27a and 27b. Since the drive arm 29 rotates integrally with the link arm 3, when the link arm 3 rotates to the front side, the drive arm 29 also rotates to the front side. Therefore, in the section where the door 90 opens from the closed state and the link arm 3 rotates to the front side, the angle between the drive arm 29 and the center line of the coil springs 27a and 27b gradually decreases. In the state where the opening angle of the door 90 is 90 degrees, the connection pin 31 on the drive side is located at the front end of the long hole 33 on the drive side. Therefore, the spring receiving block 32 is pushed to one end by the drive arm 29 and positioned at the one end, and the coil springs 27a and 27b are in the state where the compression amount is the largest.

  In the section where the opening angle exceeds 90 degrees, the door 90 rotates about the second rotation center 91b, and the door 90 rotates up to 180 degrees as shown in FIG. In the section where the opening angle is 90 degrees to 180 degrees, the link arm 3 is rotated slightly toward the front side at the beginning and reaches the maximum rotation state, and then, it rotates toward the back side. Specifically, the link arm 3 is slightly rotated toward the front side when the opening angle is between 90 degrees and 100 degrees, and is in the state of being rotated to the front side at an opening angle of 100 degrees, and then 100 degrees to The link arm 3 is rotated by a predetermined angle to the front side with respect to the slider 2 when the opening angle of the door 90 is 180 degrees, although it rotates toward the back side between 180 degrees. In addition, the slider 2 slides toward one end with the opening operation of the door 90 even in the section where the opening angle is 90 degrees to 180 degrees.

  Since the link arm 3 rotates toward the back side in the section where the opening angle is 100 degrees to 180 degrees, the braking arm 30 and the drive arm 29 also rotate in the opposite direction. Then, when the opening angle of the door 90 is 180 degrees, as shown in FIG. 12, the connection pin 37 on the braking side and the connection pin 31 on the drive side are both at positions approximately coincident with the center lines of the coil springs 27a and 27b.

  Next, the force acting on the drive arm 29 and the link arm 3 at each opening angle of the door 90 will be described using schematic diagrams. The relationship of the action of the force at each opening angle is schematically shown in FIG. 13 to FIG. In order to facilitate understanding, the door 90 is illustrated as being rotated about the first rotation center 91a even when the opening angle is 100 degrees to 180 degrees. Moreover, in FIG.13 (b)-FIG. 18, it combines with the position of the door 90 whose opening angle is 0 degree, and has shown in figure with the dashed-two dotted line.

  In FIG. 13A, in the closed state where the opening angle of the door 90 is 0 degree, the drive arm 29 receives the pressing force 50 by the coil springs 27a and 27b from the right side in the figure. The direction of the pressing force 50 of the coil springs 27a and 27b is the direction of the center line of the coil springs 27a and 27b, but the drive arm 29 is inclined at a predetermined angle to the back side with respect to the center line of the coil springs 27a and 27b in the closed state. Because of this, a clockwise rotational moment acts on the drive arm 29 around the second rotational shaft 20 in the figure, and a clockwise rotational moment also acts on the link arm 3. A rotational force (a force for rotating the link arm 3) acts on the first rotation shaft 82 from the link arm 3. This rotational force is referred to as an arm rotational force 51. The arm rotational force 51 is perpendicular to a straight line connecting the first rotation shaft 82 and the second rotation shaft 20. In FIGS. 13 to 18, for the sake of simplicity, it is assumed that the magnitude of the arm rotational force 51 is assumed to be constant. The arm rotational force 51 acts on the door 90 via the first rotation shaft 82. The door rotational force 52 acting as a force for rotating the door 90 acts on the door 90 as a component of the arm rotational force 51. The direction of the door rotation force 52 is a direction perpendicular to the straight line 4 connecting the first rotation shaft 82 and the first rotation center 91 a of the door 90. In the closed state, since the direction of the door rotational force 52 is the closing direction, the closing force is applied to the door 90, and the closed state is maintained.

  When the door 90 is opened, the link arm 3 rotates to the front side about the second rotation shaft 20, so the door rotational force 52 gradually becomes as shown in FIG. 13 (b) to FIG. 15 (a). Become smaller. That is, the closing force gradually decreases. Then, when the opening angle of the door 90 becomes 70 degrees as shown in FIG. 15B, a straight line connecting the first rotation shaft 82 and the second rotation shaft 20, the first rotation shaft 82 and the door 90 The angle between the first rotation center 91 a and the straight line 4 is approximately 90 degrees, and the door rotation force 52 is approximately zero. Further, as shown in FIG. 16A, when the opening angle of the door 90 becomes 80 degrees, the direction of the door rotational force 52 reverses to the opening direction, and the opening force acts on the door 90. Thereafter, as shown in FIGS. 16 (b) to 18 (b), the door rotation force 52 gradually increases as the opening angle of the door 90 increases.

  As described above, when the door 90 is opened from the closed state, when the opening angle of the door 90 is 70 degrees, the closing force is substantially zero, so the door 90 can be opened with a light force. In addition, when the door 90 is opened by a predetermined opening angle or more (70 degrees or more in the present embodiment), an opening force acts on the door 90, so the door 90 does not return to the closed state. The door 90 is kept open. That is, the door closer in this embodiment has a stopper function for maintaining the door 90 in the open state.

  In addition, when the door 90 is opened from the closed state, the rotational moment acting on the drive arm 29 by the pressing force 50 applied to the drive arm 29 from the coil springs 27a and 27b has the maximum closed state and the opening of the door 90 It becomes smaller as the angle gets larger. Although the absolute value of the pressing force 50 acting on the drive arm 29 from the coil springs 27a, 27b becomes slightly larger because the compression amount of the coil springs 27a, 27b becomes larger than the closed state, the center line of the coil springs 27a, 27b and the drive arm 29 The rotation moment acting on the drive arm 29 becomes smaller because the angle between them gradually decreases. In FIG. 13 and the like, it is assumed that the arm rotational force 51 is constant, and the length of the arrow of the arm rotational force 51 is illustrated as being constant. However, the arm rotational force 51 is actually, for example, the door 90 rather than the closed state. Since the angle between the drive arm 29 and the center line of the coil springs 27a and 27b is substantially zero when the opening angle of the door 90 is smaller when the opening angle of the door 90 is 90 degrees, in particular, the arm rotational force 51 Is approximately zero. Therefore, when the opening angle of the door 90 is around 90 degrees, the door can be opened with a very light force. Further, as described above, when the opening angle of the door 90 is 70 degrees, the door rotational force 52 becomes almost 0, so the door 90 can be opened with a particularly light force when the opening angle of the door 90 is 70 degrees to 90 degrees. .

  On the contrary, in the section where the opening angle of the door 90 exceeds 90 degrees and particularly 100 degrees to 180 degrees, the compression amount of the coil springs 27a and 27b decreases slightly as the door 90 opens, but the driving arm 29 and As the angle between the coil springs 27a and 27b and the center line of the coil springs 27a and 27b increases, the rotational moment acting on the drive arm 29 increases and the arm rotational force 51 increases. Therefore, a large opening force can be obtained when the opening angle of the door 90 is near 180 degrees, and a stable door opening state can be obtained.

  As described above, the door closer in the present embodiment is provided with the rotational force application means for applying the arm rotational force 51 to the link arm 3 in the slider 2, so the door closer main body as in the prior art is not necessary. It will be simple. In addition, since miniaturization can be achieved, aesthetics are also improved. In particular, the structure is simple because the arm rotational force 51 is applied to the link arm 3 by converting the pressing force 50 of the coil springs 27 a and 27 b into the rotational moment around the second rotation shaft 20 via the drive arm 29. Can be manufactured inexpensively. Furthermore, since the coil springs 27a and 27b and the damper 28 are distributed on both sides of the second rotation shaft 20, and the second rotation shaft 20, the coil springs 27a and 27b, and the damper 28 are arranged in a straight line. , The slider 2 can be slimmed. Moreover, since the drive arm 29 and the braking arm 30 are integrally provided on both sides of the second rotation shaft 20 and the drive arm 29 and the braking arm 30 are swung, the structure is not complicated, and the drive is performed. The arm 29 and the braking arm 30 can be easily interlocked. Furthermore, since the second rotation shaft 20 is offset to the front side rather than the center in the front-rear direction, the drive arm 29 and the braking arm 30 can be disposed without excessively increasing the dimension of the slider 2 in the front-rear direction.

  And since the slider 2, the link arm 3 and the door 90 constitute a reciprocating slider crank mechanism, the door 90 can be opened with a light force. Moreover, since the door rotational force 52 becomes 0 when the door 90 is opened to a predetermined opening angle, the door 90 can be opened easily, and when the door 90 is opened beyond the predetermined opening angle, the door rotational force 52 is reversed. Since it acts on the open side, a stopper function can also be obtained and held in the open state. Furthermore, in a predetermined section at the initial stage of opening, the drive arm 29 is rotated to the front side along with the opening operation and the angle between the center line of the coil springs 27a and 27b becomes smaller. It also becomes smaller. Therefore, the door 90 can be opened with a lighter force.

  Further, since the slider 2, the link arm 3 and the door 90 constitute a reciprocating slider crank mechanism and the slider 2 and the link arm 3 are always operated in conjunction with the opening and closing operation of the door 90, there are few failures. There is no collision noise. That is, in the above-mentioned patent document 1, since a rotation piece collides with a receiving piece, in the case of the collision, a collision sound is generated. In addition, in the event of a collision, the member is likely to break down. On the other hand, in the door closer of this embodiment, the slider 2 and the link arm 3 are always operated in conjunction with the opening and closing operation of the door 90, and the door rotational force 52 is automatically turned to the open side to open the door 90. Since the open state is maintained, it is possible to prevent a failure and a collision noise.

  In the above embodiment, the coil springs 27a and 27b are provided on one end side in the longitudinal direction of the housing 23 and the damper 28 is provided on the other end side in the longitudinal direction. However, this arrangement may be reversed.

  In addition, although the configuration in which the guide rail 1 and the slider 2 are disposed in the upper frame portion 93 has been described, conversely, the guide rail 1 and the slider 2 may be disposed in the door 90. Preferably, the guide rail 1 and the slider 2 are disposed in the inside.

  Furthermore, although the pressing force 50 of the coil springs 27a and 27b is transmitted to the drive arm 29 via the spring receiving block 32 and the connection pin 31 on the drive side, it is transmitted to the drive arm 29 using various cams instead. May be Further, the arm rotational force 51 is applied to the link arm 3 using conversion means for converting the pressing force 50 of the coil springs 27 a and 27 b into the rotational moment around the second rotation shaft 20 without using the drive arm 29. Alternatively, the arm rotational force 51 may be applied using a configuration including a rack and a pinion gear. Alternatively, the arm rotational force 51 may be applied to the link arm 3 by providing a torsion spring on the second rotation shaft 20 or the like. Thus, the configuration of the rotational force application means can be variously changed.

  Further, the guide rail 1 may be provided with a restricting means for restricting the movement of the slider 2 to one end beyond the predetermined position. As described above, when the guide rail 1 is provided with the restricting means, the movement amount of the slider 2 can be limited, and the upper limit of the opening angle of the door 90 can be determined. In the above example, the door 90 is opened beyond 90 degrees, but if, for example, the upper limit of the opening angle of the door 90 is desired to be 90 degrees, the slider 2 is positioned at a position corresponding to the upper opening angle. By restricting the movement by the restricting means, the door 90 can be prevented from opening beyond 90 degrees.

  Next, a door closer according to a second embodiment of the present invention will be described with reference to FIGS. The description of the same configuration as that of the first embodiment will be omitted. The door closer of the second embodiment differs from the door closer of the first embodiment in the configuration of the slider 2 and also in the configuration of the guide rail 1. The structure of the slider 2 is shown in FIGS. FIGS. 19 to 22 show the state of the slider 2 corresponding to the door 90 in the closed state.

  The second rotation shaft 20 is provided at a position eccentric to one end side with respect to the longitudinal center of the housing 23. A drive arm 29 is integrally formed on the second rotation shaft 20 as shown in FIGS. 21 and 22A. The drive arm 29 extends in a direction perpendicular to the longitudinal direction of the housing 23. The second rotation shaft 20 is disposed to be offset to the front side, and the drive arm 29 extends rearward from the second rotation shaft 20. A connecting pin 31 is attached and fixed to the tip end of the drive arm 29 so as to penetrate the drive arm 29 vertically. A bush 120 is externally fitted to the upper and lower portions of the connecting pin 31 projecting upward and downward from the drive arm 29, respectively, and the rocking slider 124 is connected via the bush 120. The bush 120 is preferably made of a synthetic resin excellent in slidability, particularly a self-lubricating resin. Although the swinging slider 124 reciprocates, the bush 120 should be made of synthetic resin so that the swinging slider 124 and the connecting pin 31 do not hit each other when the swinging slider 124 reciprocates so that noise does not occur. preferable.

  An accommodation recess 121 having a rectangular shape in cross section opening downward is formed in a part on one end side of the housing 23, and a longitudinal direction of the housing 23 is communicated with the accommodation recess 121 in a part on the other end side of the housing 23. A through hole 122 having a circular cross-sectional shape extending along the length of A lid 123 is screwed to the housing 23 from the lower side, and the lid 123 closes substantially the entire accommodation recess 121. The upper end portion of the second rotation shaft 20 is supported by the housing 23 via the bush 24, and the lower end portion of the second rotation shaft 20 is supported by the lid 123 via the bush 26. The rocking slider 124 is slidably inserted into the housing recess 121 of the housing 23 along the longitudinal direction of the housing 23. The swinging slider 124 is in the form of a rectangular parallelepiped elongated along the longitudinal direction of the housing 23, and is accommodated in the housing 23 so as to slide on the inner surface of the housing 23 as shown in FIG. 22 (b). The rocking slider 124 is preferably made of metal. At the central portion in the longitudinal direction of the front surface of the rocking slider 124, as shown in FIG. 20 and FIG. The notch recess 125 has a shape that penetrates up and down, and the swing slider 124 is concave or gated in plan view or bottom view by the notch recess 125.

  As shown in FIG. 20, the second rotary shaft 20 is vertically inserted through the notch recess 125 of the swing slider 124. Further, in the portion of the rocking slider 124 located on the rear side of the cutout recess 125, a hole 126 communicating with the cutout recess 125 and opening on the rear surface is formed to penetrate in the front and rear direction. The longitudinal center of the rocking slider 124 is divided up and down by the punching hole 126 as in the above. In the portion of the rocking slider 124 which is divided into upper and lower parts by the extraction hole 126, elongated holes 127 which penetrate through the upper and lower parts are formed. The long hole 127 is long along the front-rear direction, and the upper and lower portions of the connecting pin 31 are engaged with the long hole 127. The connection pin 31 is preferably made of metal.

  The swinging slider 124 is guided by the inner surface of the housing 23 and can reciprocate within a predetermined length range along the longitudinal direction of the housing 23. On the inner surface of the upper wall portion of the housing 23 which is also the bottom surface of the housing recess 121, a guide projection 128 projecting downward is formed along the longitudinal direction of the housing 23. The guide ridges 128 are divided into right and left portions at the central portion in the longitudinal direction. Therefore, the guide ridges 128 are formed in the same straight line as each other. A guide groove 129 with which the guide protrusion 128 is engaged is formed on the upper surface of the swing slider 124 over the entire length. Similarly, a guide groove 129 is also formed on the lower surface of the swing slider 124 over the entire length, and a pair of guide pins 130 are screwed into the lid 123 from the inner surface side, and the head of the guide pin 130 is shaken. The guide groove 129 on the lower surface of the moving slider 124 is engaged. Therefore, when the second rotating shaft 20 rotates with the opening and closing operation of the door 90 and the drive arm 29 rotates about the second rotating shaft 20, the swinging slider 124 forms the guide ridge 128 and the guide pin. It is guided by the head of 130 and slides along the longitudinal direction of the housing 23 while sliding on the inner surface of the housing 23. Further, screw holes 131 having a predetermined depth are formed on both end surfaces of the swing slider 124, respectively.

  As shown in FIG. 22A, support holes 132 for supporting the second rotation shaft 20 are formed in a pair of front and rear symmetrical arrangements in the upper wall portion of the housing 23. The second rotation shaft 20 is supported by the front support hole 132, but if the opening direction of the door 90 is reversed, the second rotation shaft 20 is inserted into the rear support hole 132. Just insert it. As described above, the housing 23 is a double-open type that can be used even if the opening direction of the door 90 is either left or right. Similarly, the swing slider 124 is also of the double-open type.

  A spring receiving block 133 is fixedly disposed in the vicinity of the left end portion of the housing recess 121. The spring receiving block 133 is preferably made of metal. The spring receiving block 133 is screwed to the housing 23 and the lid 123 from four directions. A coil spring 134 is incorporated on the left side of the spring receiving block 133. The coil spring 134 is inserted into the through hole 122 and its right end abuts on the spring receiving block 133. Further, a bolt 135 is inserted into the through hole 122, and the bolt 135 is screwed into the screw hole 131 on the left side of the swing slider 124, and the bolt 135 and the swing slider 124 slide integrally. . A spacer 136 is interposed between the head of the bolt 135 and the coil spring 134. The bolt 135 passes through the spacer 136, the coil spring 134 and the spring receiving block 133 and is screwed to the swing slider 124. The left end of the coil spring 134 is in contact with the spacer 136. The spacer 136 is circular with the same diameter as the through hole 122 and slides on the wall surface of the through hole 122. The spacer 136 is preferably made of metal. The coil spring 134 is a compression spring interposed between the spacer 136 and the spring receiving block 133. The state shown in FIGS. 19 to 21 corresponds to the closed state and is the reference state, and in the state of the slider 2 alone, the rocking slider 124 is in the state shown in FIGS. 19 to 21. And can move to the left until it abuts against the spring receiving block 133. When the rocking slider 124 and the bolt 135 move to the right from the closed state shown in FIGS. 19 to 21, the coil spring 134 is compressed accordingly and the spring force increases. In the closed state shown in FIGS. 19 to 21, the coil spring 134 is in a compressed state so as to obtain a predetermined compression amount, and the compressed amount in the closed state adjusts the screwing amount of the bolt 135 into the swinging slider 124 You can increase or decrease by doing this. In the vicinity of the left end of the housing 23, a plate 137 is inserted upward from the lower side. The plate 137 is preferably made of metal.

  Further, a lock screw 138 (locking means) can be detachably attached to the housing 23 for locking in a predetermined compression state in which the compression amount of the coil spring 134 is increased by a predetermined amount compared to the closed state. FIGS. 23 and 24 show a state where the lock screw 138 is attached, that is, a locked state. When the lock screw 138 is attached to the housing 23, the coil spring 134 is locked in a predetermined compression state, and when the lock screw 138 is removed, the locked state is released and the coil spring 134 returns to the closed state shown in FIGS. Specifically, the lock screw 138 is a so-called urea screw and can be easily screwed to the housing 23 by holding its head by hand. The lock screw 138 is screwed to the housing 23 from the lower side.

  Screw insertion holes 139 through which the lock screw 138 is inserted are formed in the lower wall portion of the housing 23 at two front and back positions, and a screw hole 140 into which the lock screw 138 is screwed is formed at the corresponding upper wall portion of the housing 23 It is formed in two places before and after. The lock screw 138 passes through the screw insertion hole 139 of the lower wall portion, vertically traverses the through hole 122, and is screwed into the screw hole 140 of the upper wall portion. When the head of the bolt 135 abuts from the right to the attached lock screw 138, the bolt 135 can not move to the left and the coil spring 134 is held in a predetermined compression state, and the coil spring is closed against the closed state (reference state). The spring force 134 is maintained at a predetermined amount large. By inserting the lock screw 138 in this manner, it is held in tension and holds the coil spring 134 in a compressed state more compressed than in the closed state. When the lock screw 138 is removed, the coil spring 134 expands, and the bolt 135, the spacer 136 and the swing slider 124 move by the spring force of the coil spring 134. The lock screw 138 is inserted into the screw insertion hole 139 and the screw hole 140 on the front side of the screw insertion holes 139 and the screw holes 140 at two front and rear locations. The rear screw insertion holes 139 and the screw holes 140 are used when the opening direction of the door 90 is reversed.

  Next, the guide rail 1 will be described. FIG. 25 is a view of the guide rail 1 viewed from the bottom side, but as also shown in FIG. 26, the guide rail 1 is a rectangular section of a thin plate in which the front portion of the lower plate portion 1a is opened. The mounting plate 151 is screwed to the outside of the upper plate portion as shown in FIG. 26 (b). The guide plate 1 is attached to the upper frame portion 93 by attaching the attachment plate 151 to the upper frame portion 93 of the door frame with the screws 152 as shown in FIG. 26C and FIG.

  Further, in the present embodiment, the damper 28 is attached and fixed to a predetermined position of the guide rail 1 separately from the slider 2. Therefore, a damper receiver 153 for attaching the damper 28 is screwed to a predetermined position of the guide rail 1. As shown in FIG. 26 (a), a circular guide hole 153a passes through the damper receiver 153, and a cylindrical damper main body 28b is inserted into the guide hole 153a from the right side. A flange portion 28c having a diameter larger than that of the damper main body 28b is circumferentially provided on the damper main body 28b. For example, as shown in FIG. 31, the flange 28c of the damper main body 28b abuts on the damper receiver 153 to make the damper main body 28b The guide hole 153a can not be further inserted, and the damper 28 is positioned at a predetermined position. Further, the damper 28 is mounted with its main shaft 28a facing right. The damper 28 is disposed on the left side of the slider 2, that is, on the side far from the first rotation center 91 a of the door 90 (the tip side of the door 90).

  Further, at the front edge portion of the lower plate portion 1a of the guide rail 1, a locking notch portion 154 for locking the lock screw 138 attached to the slider 2 in a predetermined position is formed. The head of the lock screw 138 attached to the slider 2 protrudes to the lower side of the housing 23. Since approximately half of the front side (front side) of the lower plate portion 1a of the guide rail 1 is notched and opened, the head of the lock screw 138 projecting downward from the housing 23 is the second rotary shaft 20 and Similarly, it can project downward from the opening of the guide rail 1. Then, as shown in FIG. 27, the head of the lock screw 138 is positioned in the locking notch 154 of the guide rail 1. The locking notches 154 have a predetermined length along the sliding direction of the slider 2, and the shapes of both left and right ends of the locking notches 154 correspond to the head of the lock screw 138, specifically In fact, it has an arc shape. The head of the lock screw 138 attached to the housing 23 can slide in the left and right direction by the length range of the locking notch 154, and the head of the locking screw 138 is of the locking notch 154 as shown in FIG. The slider 2 with the lock screw 138 attached from the position abutted to the left end until the head of the lock screw 138 abuts the right end of the locking notch 154 as shown in FIG. It can slide in the guide rail 1. The guide rail 1 is also a dual-purpose type corresponding to both the left and right opening, and the locking notches 154 are also formed in a pair in left-right symmetrical arrangement.

  The use condition of the door closer configured as described above is shown in FIGS. The entire door closer is shown in FIGS. 28 to 33 and 37, and enlarged views in the vicinity of the second rotation shaft 20 are shown in FIGS. 34 to 36. FIGS. 28 to 30 show the closed state, that is, the fully open state where the opening angle of the door 90 is 0 degree, FIGS. 31 and 34 show the state where the opening angle of the door 90 is 70 degrees, and FIGS. The opening angle 90 is 90 degrees, and FIGS. 33 and 36 show the door 90 opening angle 180 degrees. In FIG. 29, the slider 2 and the damper 28 are shown by a two-dot chain line. FIG. 37 shows a state where the door 90 is in the process of closing. As shown in FIG. 28, in the present embodiment, the upper end surface of the door 90 does not have the above-described notch 95, and the upper end surface of the door 90 is flat.

  As shown in FIG. 30, when the door 90 is in the fully closed state, that is, the opening angle is 0 degree, the slider 2 is in the same state as shown in FIGS. It is in a state of facing the rear side which is a direction orthogonal to the longitudinal direction of the housing 23. In the closed state, the plate 137 of the slider 2 is in contact with the main shaft 28 a of the damper 28, and the main shaft 28 a is pressed by the plate 137 of the slider 2 toward the damper main body 28 b.

  When the door 90 is opened from the closed state, the link arm 3 is pivoted to the front side about the second rotation shaft 20 in conjunction with the opening operation of the door 90. The second rotation shaft 20 is also rotated by the pivoting operation of the link arm 3, and the drive arm 29 is also pivoted counterclockwise as viewed from the bottom side. As the drive arm 29 pivots to the right, the rocking slider 124 moves to the right relative to the slider 2 to compress the coil spring 134.

  As shown in FIGS. 31 and 34, when the opening angle of the door 90 becomes 70 degrees, a straight line 160 (link arm 3) connecting the first rotation shaft 82 and the second rotation shaft 20, and the first rotation shaft The angle θ between the line 82 and the straight line 4 connecting the first rotation center 91 a of the door 90 is approximately 90 degrees. Therefore, although the arm rotational force 51 (not shown in FIG. 31) acting on the link arm 3 from the coil spring 134 through the drive arm 29 and the second rotational shaft 20 is a large force, the first The direction of the arm rotational force 51 acting on the door 90 through the rotation shaft 82 is substantially the same as the straight line 4 connecting the first rotation shaft 82 and the first rotation center 91 a of the door 90. The door rotation force 52 (not shown in FIG. 31), which is a force for rotating the d.c., becomes approximately zero, as in the case of FIG. 15 (b) described above.

  When the door 90 is further opened from there, the direction of the door rotational force 52 is reverse to the opening direction, and the opening force acts on the door 90. As shown in FIGS. 32 and 35, when the opening angle of the door 90 is 90 degrees, the rotation angle of the link arm 3 is close to the maximum. Further, the door 90 can be opened beyond 90 degrees, and can be opened to an opening angle of 180 degrees as in FIGS. In the section where the opening angle is 90 degrees to 180 degrees, the link arm 3 is rotated slightly toward the front side at the beginning and reaches the maximum rotation state, and then, it rotates toward the back side. Similarly, since the drive arm 29 also pivots to the left side opposite to the opening operation, the rocking slider 124 also slides to the left along with it, and the compression amount of the coil spring 134 decreases.

  When closing the door 90, the opening force of the door 90 starts to act on the door 90 from about 70 degrees, and the closing force gradually increases as the door 90 is closed from there. In the present embodiment, the damper 28 is not built in the slider 2, and the damper 28 is fixedly disposed at a position away from the slider 2 and waits for the slider 2. As shown in FIG. 37, when the door 90 reaches a predetermined opening angle, specifically, when the opening angle reaches about 30 degrees, the slider 2 abuts on the damper 28 to start buffering. That is, the plate 137 of the slider 2 abuts on the main axis 28 a of the damper 28 standing by at the predetermined position of the guide rail 1 from the right side. Accordingly, the damper 28 works in the section from the opening angle to the fully closed state to brake the door 90 via the slider 2, so the door 90 is slowly closed and eventually becomes fully closed. As described above, in the present embodiment, since the damper 28 receives the movement of the slider 2 as a fixed type that is separate from the slider 2, it is easy to make the stroke of the main shaft 28 a of the damper 28 longer. That is, since the amount of movement of the slider 2 is large, the stroke of the main shaft 28a of the damper 28 can be lengthened. Therefore, the buffer capacity of the damper 28 can be easily increased, and even the heavy and large door 90 can be reliably buffered.

  On the other hand, as described above, when the opening angle of the door 90 becomes 70 degrees, the door rotational force 52 becomes almost zero and the closing force is almost not generated. Therefore, when attaching or removing the door closer, It is preferable that the opening angle of the door 90 be around 70 degrees, which facilitates the mounting and dismounting operation. As described above, the coil spring 134 can be locked in a predetermined compressed state by attaching the lock screw 138 to the slider 2, but the locked state corresponds to a state in which the opening angle of the door 90 is 70 degrees. Therefore, at the time of mounting, it is preferable to screw the lock screw 138 into the slider 2 inserted into the guide rail 1 to keep the slider 2 in the locked state, and it is preferable to keep the state in the shipping state.

  The guide rail 1 incorporating the slider 2 in the locked state is attached to the upper frame 93 of the door frame, and both ends of the link arm 3 with the door 90 and the second rotary shaft 20 of the slider 2 in the state opened at 70 degrees. Attach each one. The head of the lock screw 138 is shown in FIG. 31 by a two-dot chain line, but in the attached state, the head of the lock screw 138 is in contact with the left end of the locking notch 154 of the guide rail 1. . Therefore, the door 90 is slightly opened from that state, for example, about 10 degrees more and the lock screw 138 is removed. For example, the slider 2 is moved slightly to the right by opening from the state where the opening angle shown in FIG. 31 is 70 degrees to, for example, 80 degrees, and the head of the lock screw 138 is from the left end of the locking notch 154 The lock screw 138 is removed from the slider 2 in such a state as being released to the right. As also shown in FIG. 27, the locking notch 154 has a predetermined length, and the locking screw 138 can move in the locking notch 154 along the longitudinal direction within the locking notch 154, so the door closer is attached. In this state, the lock screw 138 can be easily removed by slightly opening the door 90. Similarly, when the door closer is removed, the coil spring 134 can be temporarily fixed in a predetermined compression state by attaching the lock screw 138 to the slider 2 with the door 90 opened at an angle of, for example, 80 degrees, which facilitates door closure. Can be removed.

  The upper limit of the opening angle of the door 90 may be determined by providing a restricting means on the guide rail 1 and restricting the amount of movement of the slider 2 to the right. For example, as shown in FIG. 38, the stopper 155 as the restricting means may be screwed to the guide rail 1. By forming a long hole along the longitudinal direction of the guide rail 1 in the stopper 155, the left and right positions of the stopper 155 can be adjusted. Then, for example, when it is desired to set the upper limit of the opening angle of the door 90 to 90 degrees, the stopper 155 may be fixed at a position corresponding thereto, and when the door 90 opens to 90 degrees as shown in FIG. The right end abuts against the stopper 155 to prevent further movement of the slider 2 to the right. As a result, the door 90 can not open beyond 90 degrees. Preferably, the portion of the stopper 155 with which the slider 2 abuts is made of, for example, rubber to reduce the impact at the time of door opening. Further, the configuration of the stopper 155 can be appropriately changed, and the screw holes for attaching the stopper to the guide rail 1 are spaced in the longitudinal direction of the guide rail 1 instead of the slide adjustment type configuration as shown in FIG. A plurality of locations may be formed, and for example, a rubber block as a stopper may be screwed into an arbitrary screw hole so that the upper limit of the opening angle of the door 90 can be variously selected or changed.

  The lock screw 138 may not be a urea screw, and other general purpose screws or the like can be used. Also, for example, the lock screw 138 may be in contact with the swing slider 124. The lock means may have a configuration other than the lock screw 138. The lock means is not configured to be attached to and detached from the slider 2, but may be attached to a predetermined position of the slider 2 so as to be switchable between the lock position and the lock release position. Further, the locking means may be provided in the first embodiment, and the invention can be applied to a configuration in which the damper 28 is incorporated in the slider 2.

DESCRIPTION OF SYMBOLS 1 guide rail 1a lower plate part 2 slider 3 link arm 3a counterbore 3b counterbore 4 straight line 19 connecting the first rotation axis and the first rotation center of the door screw 20 second rotation shaft 21 washer 22 screw 23 housing 24 bush 25 support base 26 bush 27 a first coil spring (torque applying means)
27b Second coil spring (rotational force application means)
28 Damper (means for applying braking force)
28a Main shaft 28b Damper main body 28c Flange part 29 Drive arm (rotational force applying means)
29a Bifurcated portion 30 braking arm (braking force application means)
30a bifurcated portion 31 drive side connection pin (rotational force applying means)
32 Spring support block (rotational force application means)
32a plate-like portion 33 long hole 34 on the drive side coil holder (rotational force adjusting means)
34a groove 35 nut (rotational force adjustment means)
36 Spacer 37 Connection pin on the braking side (braking force application means)
38 Exiting block (braking force application means)
38a plate-like portion 39 long hole 40 on the braking side washer 41 spacer 50 pressing force 51 arm rotational force 52 door rotational force 80 support plate 81 screw 82 first rotation shaft 82a flange 83 washer 85 bush 90 door 91a first rotation Center 91b Second rotation center 92 Vertical frame 93 Upper frame 94 Hinge 95 Notch 101 Opening direction 102 Closing direction 201 Rotation direction of link arm when door starts to open 202 Direction of closing door before closing state Link arm rotation direction 301 Slider movement direction 302 when opening door Movement direction of slider when closing door 120 Bushing 121 Housing recess 122 Through hole 123 Lid 124 Swing slider 125 Notched recess 126 Extraction hole 127 Long hole 128 Guide ridge 129 Guide groove 130 Guide pin 131 Screw hole 132 Support hole 133 Spring receiving block 134 coil spring 135 bolt 136 spacer 137 plate 138 lock screw (locking means)
139 screw insertion hole 140 screw hole 151 mounting plate 152 screw 153 damper receiver 153a guide hole 154 locking notch 155 stopper 160 straight line connecting the first rotation shaft and the second rotation shaft

Claims (5)

A door closer for closing a door rotating about a vertical axis,
A guide rail attached to one of the door frame and the door, a slider sliding guided by the guide rail, and a link arm rotatably connected to the other of the door frame or the door and the slider ,
As the door starts to open, the link arm rotates in the specified direction with respect to the slider,
A door closer provided with a rotational force applying means for applying an arm rotational force for rotating the link arm in a direction opposite to the predetermined direction.   The door closer according to claim 1, wherein the arm rotational force is smaller when the door is opened by a predetermined angle than when the door is closed. The rotational force application means includes a drive arm that rotates integrally with the link arm around a rotation axis that rotatably couples the slider and the link arm, a slide direction of the slider as a central line direction, and the link arm And a coil spring for pressing the drive arm to apply a rotational force,
The door closer according to claim 2, wherein when the link arm rotates in the predetermined direction, the drive arm rotates such that an angle between the link arm and the center line of the coil spring decreases.   The door closer according to claim 3, wherein the rotation axis is provided at a position offset in a horizontal direction and a direction perpendicular to a center line of the coil spring.   The rotational force applying means includes a spring for generating an arm rotational force, and a lock means for locking and unlocking the spring in a predetermined state, and the arm rotational force is linked when the spring is locked in a predetermined state The door closer according to claim 1, wherein the door closer does not act on the arm, and the arm rotational force acts on the link arm when the spring is unlocked.

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