WO2006068005A1

WO2006068005A1 - Door closer

Info

Publication number: WO2006068005A1
Application number: PCT/JP2005/022843
Authority: WO
Inventors: Kohji Ishida
Original assignee: Ryobi Ltd.
Priority date: 2004-12-21
Filing date: 2005-12-13
Publication date: 2006-06-29
Also published as: JP2006176984A; JP4700960B2

Abstract

A door closer capable of securing a large door closing force in a wide range up to a fully closed position or a position immediately before the fully closed position without increasing a load thereon for opening a door. In closing the door, the elastic deformations of springs (8) and (9) produced by a door opening operation are partly maintained in a deformed state until the door is fully closed or immediately before the door is fully closed, and then the deformed state is released to reset the springs (8) and (9) to an initial state before the door opening operation. A boosting piston (10) is moved when the door is opened to elastically deform the springs (8) and (9) in association with a piston (7) so as to maintain and release, as a part of the elastic deformations, the elastically deformed parts of the springs (8) and (9) due to the movement of the boosting piston (10) in s deformed state until the door is fully closed or immediately before the door is fully closed when the door is closed.

Description

Specification

Door closer

Technical field

The present invention relates to a door closer that automatically closes a door by the elastic force of an elastic member that is elastically deformed when the door is opened.

Background art

[0002] This type of door closer is generally configured to generate a closing force by compressing a spring in a cylinder by a piston when the door is opened and urging the piston when the door is closed by its elastic force. By the way, for example, when the door is affected by the wind, it is difficult to close the door, so various improvements have been proposed (see the following patent document).

Patent Document 1: Japanese Patent Application Laid-Open No. 62-13677

Patent Document 2: Japanese Utility Model Publication No. 63-195088

Patent Document 3: Japanese Patent No. 2977527

Patent Document 4: Japanese Patent No. 3011701

Disclosure of the invention

Problems to be solved by the invention

[0003] However, in these improved proposals, the closing force increases only in a predetermined section when closing, so for example, the case where the open door is closed by the wind cannot be dealt with. .

[0004] On the other hand, it is possible to increase the closing force by setting a strong spring, but the stronger the panel, the greater the force required to open the door, especially at the beginning of opening. It becomes difficult to open the door.

[0005] Therefore, an object of the present invention is to provide a door closer that can secure a large closing force in a wide section until it is fully closed or just before it, while suppressing an increase in the burden of the opening operation.

Means for solving the problem

[0006] The present invention has been made to solve the above problems, and the door closer according to the present invention. Is a piston that reciprocates in the cylinder according to the opening / closing operation of the door, and elastically deforms according to the movement of the piston in the opening direction when the door is opened, and urges the piston in the closing direction when the door is closed by the elastic force. A door closer provided with an elastic member for providing a door with a closing force, and a part of the elastic deformation of the elastic member caused by the opening operation is maintained in the deformed state until the door is fully closed or immediately before the door is fully closed. And an elastic deformation control means for releasing the deformation state and resetting the elastic member to the initial state before the door opening operation.

[0007] In the door closer having the above structure, when the door is opened, the piston moves in the opening direction (one direction) in the cylinder in accordance with the opening operation, elastically deforms the elastic member, and elastically deforms when the door is closed. Due to the elastic force of the member, the piston moves in the cylinder in the closing direction (the other direction). When the door is closed, the piston receives an elastic force from the elastic member, so that the door is given a closing force and automatically closes. When the door is closed, the elastic deformation control means maintains a part of the elastic deformation of the elastic member caused by the opening operation in a deformed state until it is fully closed or just before it is fully closed. Therefore, a large closing force is ensured until it is fully closed or just before it is fully closed. On the other hand, the elastic deformation control means releases a part of the elastic deformation of the maintained elastic member after the fully closed state and resets the elastic member to the initial state before the door opening operation, so it is necessary for the door opening operation. The door can be opened with a relatively light force without requiring a larger opening force.

[0008] Further, the elastic deformation control means is provided with a reinforcing piston in the cylinder separately from the piston, and the reinforcing piston moves when the door is opened to elastically deform the elastic member in cooperation with the piston. Preferably, the control means maintains and releases the elastic deformation of the elastic member due to the movement of the reinforcing piston as a part of the elastic deformation in the deformed state until the door is fully closed or just before the door is fully closed. By providing the boosting piston separately from the piston, it is possible to easily maintain and release the elastic deformation by the boosting piston separately from the elastic deformation by the piston.

[0009] Preferably, the elastic member is a compression panel that is compressed when the door is opened, and the reinforcing piston compresses the compression panel from the side opposite to the piston. Various elastic members can be used, and among them, the panel is preferable because it is easy to design. And it may be a bow I tension panel that stretches as the piston moves when the door is opened, but it is fixed using a compression panel. If it is configured to be compressed from both sides so that it is sandwiched between the booster piston and the booster piston, it becomes easier to arrange and move the booster piston, compared to when the booster piston compresses the compression panel from the same direction as the piston. Thus, the movement of the boosting piston is less affected by the movement of the piston.

[0010] Further, it is preferable that the elastic deformation control means is provided with a cam as a driving means for the boosting piston when the door is opened. High degree.

[0011] Furthermore, when using a cam, the main shaft and the piston are connected so that the main shaft rotates forward and backward in conjunction with opening and closing of the door and the piston reciprocates in the cylinder as the main shaft rotates. It is preferable that the main shaft is provided with a cam and a pinion so that the main shaft rotates. By arranging the cam and pinion on the main shaft so that they rotate as a body, the movement of the piston and the movement of the boosting piston can be accurately synchronized. It will be accurate based on.

In addition, it is preferable that when the door is opened, the follower member is brought into contact with the cam to move the reinforcing piston, and when the door is closed, the driven member is separated from the cam by reverse rotation of the main shaft. By separating the driven member from the cam when the door is closed, unnecessary mechanical loss due to the driven member coming into contact with the cam does not occur in the main shaft, and the piston can be moved smoothly in the closing direction. As a result, an unnecessary decrease in the closing force can be suppressed.

[0013] Furthermore, when the cam is used, the cam surface of the cam is provided with a climbing wall portion in which the force for moving the reinforcing piston increases in a stepped manner in the moving section of the reinforcing piston. It is preferable. If the door is opened vigorously under the influence of wind, etc., the door may collide with the surrounding walls, etc. Therefore, the door opening operation can be continued by overcoming the wall from there.

[0014] Further, the elastic deformation control means includes position holding means for holding the reinforcing piston moved at the time of opening the door at the position until the door is fully closed or just before the door is closed. The volume of the boosting oil chamber is increased by movement of the boosting piston, and when the door is closed, the volume of the boosting oil chamber is maintained until it is fully closed or just before it is fully closed by the filled hydraulic oil. It is preferable that By providing a boosting oil chamber that increases the volume by moving the boosting piston when the door is opened as the position holding means, the boosting piston can be securely held in that position by the filled hydraulic oil, By removing the filled hydraulic oil from the boost oil chamber, the increased volume can be easily reduced and restored to its original state, and in particular, speed control of the restoration is easy.

[0015] Further, the elastic deformation control means includes a position holding means for holding the reinforcing piston moved at the time of opening the door in the position until the door is fully closed or immediately before the door is closed at the time of closing the door, and the reinforcing piston by the position holding means. It is preferable to provide a resetting mechanism that resets the reinforcing piston to the initial position before the door opening operation by releasing the position holding and resets the elastic member to the initial state before the door opening operation. By operating the reset mechanism, the position holding by the position holding means is released, and the reinforcing piston can easily return to the original position to reset the elastic member to the initial state.

[0016] Further, the reset mechanism is configured so that the time from the start of operation until the elastic member is reset to the initial state before the door opening operation can be adjusted, depending on the frequency of opening and closing of the door, etc. This is preferable because the time can be adjusted.

[0017] Still further, it is preferable that the elastic deformation control means includes a cam as a driving means for the reinforcing piston, and the cam is actuated immediately before full closure or immediately before full closure to operate the reset mechanism. The use of the cam facilitates the drive control of the boosting piston, and there is an advantage that the degree of freedom in design is high, and since the reset mechanism is operated by the cam, the reset mechanism is separately provided. It is necessary to operate with the mechanism.

[0018] Furthermore, it is preferable that a determination unit that makes it possible to visually recognize whether or not the reset mechanism is activated is provided. The timing when the reset mechanism operates is fully closed or just before it is fully closed, but it may vary depending on the shape of the door and the mounting variation. For this reason, the user can visually recognize from the outside whether or not the reset mechanism is operating, thereby preventing the door closer from malfunctioning due to the malfunction of the operation timing.

[0019] In particular, it is preferable that the discriminating unit is configured to be withdrawn from the outer surface of the door closer in response to the operation of the reset mechanism. The discriminating part can be easily discriminated by touching the discriminating part with the hand even if it is a dark place or an upper part that is difficult to see.

[0020] In addition, it is preferable that the reinforcing piston moves to a predetermined section after the door is opened by a predetermined amount from the fully closed state. The reinforcement piston may be configured to move from the start of opening the door to the fully closed force.When the door starts to move after the door has been opened from the fully closed position, the user's inertia force increases the user's inertia. The door can be opened with a more natural feeling.

[0021] In particular, the door closer includes a door closer main body that is attached to a rotating door and a bracket that is attached to the door frame. The door closer main body is provided with a cylinder, and the bracket and the door closer main body are connected via a link mechanism. In this case, it is preferable that the reinforcing piston moves to a predetermined section after the door is opened at a predetermined angle from the fully closed position. In a configuration in which the door closer and bracket are connected via a link mechanism, the force required for the user to open the door (opening force) gradually decreases from the beginning of opening, and reaches a substantially constant value at a predetermined opening angle. Converge. Therefore, by moving the reinforcement piston from the point where the opening force is reduced, the influence of the increase in the opening force due to the movement of the enhancement piston can be suppressed as much as possible, and the burden on the user can be reduced.

[0022] In addition, it is preferable to have an urging means for urging the reinforcing piston in the direction of movement when the door is opened. It is preferable that the urging force of the urging means is applied when the reinforcing piston moves when the door is opened. Therefore, the burden of opening the door to the user is reduced. Of course, the biasing means is weaker than the elastic member.

The invention's effect

[0023] As described above, a part of the elastic deformation of the elastic member at the time of opening the door is maintained until it is fully closed or just before it is fully closed. The door closes securely even if it is affected by wind. In addition, since the elastic deformation that has been maintained is released and the elastic member is reset to the initial state before the door opening operation, the door can be opened with a relatively light force without increasing the burden of the door opening operation.

Brief Description of Drawings

FIG. 1 is a front view showing an attached state of a door closer according to an embodiment of the present invention.

[Fig. 2] A plan view of the door closer attached with (a) in a fully closed state, (b) Indicates a slightly opened state from a fully closed state.

3] A plan view showing the door closer attached, (a) is a state where the door is further opened from the state of Fig. 2 (b) and the door is opened to nearly 90 °, and (b) is a state (a). It shows a state where the door is opened further than 90 ° and opened beyond 90 °.

4] An exploded perspective view of the main part of the door closer.

5] An exploded perspective view of the main part of the door closer.

6] A perspective view of components used in the door closer.

Garden 7] (a) is a perspective view of components used in the door closer, (b) is a sectional view of the components, and (c) is a sectional view of the components.

Sono 8] Cross-sectional view of the main part of the door closer as seen from the front.

Sono 9] A cross-sectional view of the main part of the door closer as seen from above.

FIG. 10 is a cross-sectional view taken along line AA in FIG.

11] A cross-sectional view of the main part of the door closer.

FIG. 12 is a cross-sectional view taken along the line BB in FIG.

13] Shows the state of the door closer before installation on the door in a cross-sectional view of the door closer as viewed from the plane. 14) Shows the state of the door closer as viewed from the upper side and shows the state when attached to the door. , Indicates the fully closed state (initial state) before the door opens.

15] Shows the state when the door is opened from the state shown in Fig. 14 with the door open at an angle corresponding to the rotation of the spindle by 14 °.

16] Shows the state when the door is opened from the state shown in Fig. 14 at an angle that corresponds to the rotation of the spindle by 44 °.

17] The state when the door is opened from the state shown in Fig. 14 is opened at an angle corresponding to the rotation of the spindle by 74 °.

18] The state when the door is opened from the state shown in Fig. 14 is opened at an angle corresponding to the rotation of the spindle by 149 °.

19] Shows the state when the door is closed with the door open at an angle corresponding to the rotation of the spindle by 74 ° based on the state shown in Fig. 14. [Fig. 20] Shows the state when the door is closed with the door open at an angle corresponding to the rotation of the spindle by 14 °, based on the state of Fig. 14.

FIG. 21 is a cross-sectional view of relevant parts corresponding to FIG. 14 and shows a state at the moment when it is fully closed.

[Fig.22] The relationship between the opening and closing force and the door opening angle when the door closer body 1 is attached to a rotating door. (A) shows the door closer and (b) shows the conventional door closing angle. Indicates the case of a door closer.

FIG. 23 is a cross-sectional view of a main part of a door closer according to another embodiment of the present invention, where (a) shows a state where the reset valve is not operating, and (b) shows a state where the reset valve is operating. Show.

FIG. 24 is a cross-sectional view of the principal part seen from the plane of the door closer according to another embodiment of the present invention, showing the state of the door opening operation.

FIG. 25 is a cross-sectional view of a main part when viewed from the plane of a door closer according to another embodiment of the present invention.

FIG. 26 is a cross-sectional view of the main part when viewed from the plane of the door closer according to another embodiment of the present invention.

FIG. 27 is a cross-sectional view of the main part seen from the plane of the door closer according to another embodiment of the present invention, showing the state of the door opening operation.

FIG. 28 is a cross-sectional view including a partial break line of a component used in a door closer according to another embodiment of the present invention.

FIG. 29 is a cross-sectional view of a principal part as seen from a plane in a use state of a door closer according to another embodiment of the present invention.

FIG. 30 is a cross-sectional view of the main part when viewed from the front in the usage state of the door closer.

Explanation of symbols

D ... Door, F ... Floor surface, F1 ... Installation recess, F2 ... Wall surface, W ... Door frame, 1 ... Door closer, 2 ... Bracket, 3 ... Cylinder, 4 ... Spindle, 5 ... Rack, 6 ... Pione, 7 ... Piston 8, 8, ... Panel (elastic member), 10 ... Reinforcing piston, 11 ... Cam, 12, 13 ... Link, 14 ... Mounting plate, 15 ... Housing, 16, 17 ... End plug, 18 ... Rack Rod, 19 ... pin, 21 ... first oil chamber, 2 2 ... second oil chamber, 23 ... third oil chamber (enhancement oil chamber), 24 ... pinion bush, 25 ... bearing, 26a, 26b '--sinore Tsubakimoto, 27 · · · · · · · · · · · · · · · · · · · · · · Ne (helping means), 41, 42, 43 ... spring (elastic member), 44 ... fixing member, 45 ... bolt, 70 ... through Oil passage, 71 ... Check valve, 72 ... Oil passage, 73 ... Speed control valve, 74 ... Oil passage, 75 ... Check valve, 76 ... Valve panel, 77 ... Oil passage Road, 78 ... Reset valve, 79 ... Valve panel, 80 ... Cam storage chamber, 81 ... Reset control valve, 82 ... Adjusting bush, 110 ... Cam surface, 110a ... Minimum diameter part, 110b ... Enhanced diameter part, 110c ... Stepped portion 110d: Overpassing wall portion 120 ... Connecting portion 121 ... First head portion 122 ... Second head portion 123 ... Roller 124 ... Pin 125 ... Coupling 126 ... Pin 127 ... No Cuck-up ring, 1 28… Seal member

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, an embodiment of a door closer according to the present invention will be described with reference to FIGS. 1 to 22.

As shown in FIGS. 1 to 3, the door closer according to the present embodiment is applied to the rotating door D. The door closer main body 1 is attached to the door D and generates a closing force on the door D, and the door. A bracket 2 attached to the frame W and a link mechanism that pivotally connects the door closer body 1 and the bracket 2 are provided.

4 and 5 show the force of the door closer body 1. The door closer body 1 is connected to the cylinder 3 filled with hydraulic oil and the bracket 2 via a link mechanism. A main shaft 4 that rotates in conjunction with the opening and closing of the main shaft 4, a piston 7 that is connected to the main shaft 4 via a rack 5 and a pinion 6 and reciprocates in the cylinder 3 as the main shaft 4 rotates forward and backward, When the door is opened, it is compressed by the movement of the piston 7 to one side (door opening direction), and when it is closed, the piston 7 is urged to the opposite side (door closing direction) to close the door D via the spindle 4 to the door D. Panels 8 and 9 (elastic members) for attaching mosquitoes are provided.

[0028] Further, in addition to the above-described configuration, the door closer in the present embodiment further deforms a part of the elastic deformation of the panels 8 and 9 caused by the opening operation until the door is fully closed or just before the door is fully closed. It is equipped with elastic deformation control means that maintains the state and then releases the deformation state and resets the panels 8 and 9 to the initial state before the opening operation. As will be described later, the elastic deformation control means is provided in the cylinder 3 separately from the piston 7 and cooperates with the piston 7 when the door is opened to elastically deform the vanes 8 and 9, and the reinforcing piston 10 and A cam 11 as a driving means for moving the boosting piston 10 when the door is opened, and a position holding means for holding the boosting piston 10 moved when the door is opened at the position until it is fully closed or just before it is fully closed And opening the reinforcing piston 10 by releasing the position holding of the reinforcing piston 10 by the position holding means. Equipped with a reset mechanism that resets the panel 8 and 9 to the initial state before opening and resets to the initial state before opening the door. This will be specifically described below.

As shown in FIGS. 1 to 3, the door closer body 1 and the bracket 2 are connected by a link mechanism having two links 12 and 13. That is, one end of the first link 12 is pivotally attached to the bracket 2, the other end of the first link 12 is pivotally attached to one end of the second link 13, and the other end of the second link 13 is The other end of the second link 13 is fixed so that it can rotate integrally with the upper end 4a of the main shaft 4 provided on the door closer 1 as shown in FIG. The main shaft 4 and the second link 13 rotate together. The length of the first link 12 can be adjusted. Then, when the door closer body 1 and the bracket 2 are attached to the door D and the door frame W, respectively, the first link 12 and the second link 13 as shown in Fig. 2 (a) in the fully closed state. The angle between is small and the behavior changes from Fig. 2 (b) to Fig. 3 (b) as the door opens. Meanwhile, the angle between the first link 12 and the second link 13 gradually increases. Further, the second link 13 rotates relative to the door closer body 1 around the main shaft 4 in a counterclockwise direction in plan view. Furthermore, Fig. 2 (b) shows the force when the door D is opened by about 15 ° .The first link 12 hardly rotates until the door D is opened by about 15 °. When the state shown in Fig. 2 (b) is passed, as shown in Fig. 3 (a) and Fig. 3 (b), it rotates around its one end as a fulcrum in plan view.

Incidentally, the door closer body 1 is configured to be attached to the door via the mounting plate 14, and the cylinder 3 having a circular cross section is formed on the front side of the mounting plate 14. The cylinder 3 is sealed by closing both end portions of the through-holes penetrating the housing 15 of the door closer body 1 in the longitudinal direction (horizontal direction) with end plugs 16 and 17, respectively. Filled with oil. Between the end plugs 16 and 17, a piston 7, a rack bar 18, springs 8 and 9, and a reinforcing piston 10 are arranged as shown in FIGS. 4, 5, 8, and 9.

First, when the door closer body 1 is not attached to the door as shown in FIGS. 8 and 9, the piston 7 is urged by the springs 8 and 9 so that one end plug 16 It is in the state which contact | abutted. The first oil chamber 21 having a predetermined volume is formed between the one end plug 16 and the piston 7 even in the state of force and contact. In this embodiment In this case, a concave portion is formed at the center of the inner surface of one end plug 16, and the piston 7 and one end plug 16 come into contact with each other at their peripheral portions. Accordingly, a first oil chamber 21 corresponding to the volume of the recess of one end plug 16 is formed between the piston 7 and one end plug 16.

Further, the piston 7 and the rack bar 18 are connected to each other by a pin 19. Specifically, one end of the rack bar 18 is connected to the piston 7, and the rack bar 18 extends from the piston 7 to the other end plug 17 side. The rack rod 18 has a columnar shape at one end and a semicircular shape at the other end, and a rack 5 is formed on the plane side of the predetermined region on the other end. Since the pinion 6 of the main shaft 4 is engaged with the rack 5, the rack rod 18 moves in the cylinder 3 in the axial direction by the rotation of the main shaft 4. That is, when the door is opened, the spindle 4 rotates counterclockwise (forward rotation) in FIG. 9, and the rack bar 18 moves to the right. Conversely, when the door is closed, the spindle 4 rotates (reverses) clockwise in the figure, and the rack bar 18 moves to the left. Thus, the rack bar 18 reciprocates in the cylinder 3 in conjunction with the opening and closing of the door.

Here, the main shaft 4 extends in the vertical direction and is a force orthogonal to the cylinder 3. The main shaft 4 is connected to the door closer body 1 through a pair of upper and lower pinion bushes 24 and bearings 25 (bearings). The housing 15 is rotatably supported. The upper end 4a of the main shaft 4 protrudes upward from the door closer body 1, and the second link 13 is attached to the upper end 4a. Further, seal members 26a and 26b are provided as shown in FIG. 10 so that the hydraulic oil in the cylinder 3 does not leak. A pinion 6 is formed in the central portion of the main shaft 4. As shown in FIG. 6, a pair of upper and lower cams 11 are mounted on the main shaft 4 so as to rotate at intervals in the vertical direction. The two cams 11 are integrated with the main shaft 4 by the teeth 11a formed at the center thereof engaging the upper and lower ends of the pinion 6, respectively. 5 is located. A washer 27 is interposed between the cam 11 and the bearing 25. The force with which a cam surface 110 having a predetermined shape is formed on the outer peripheral surface of the cam 11 will be described later.

On the other hand, the cylinder 3 has a force defined by the piston 7. Panels 8 and 9 are inserted on the opposite side of the first oil chamber 21 with respect to the piston 7. The springs 8 and 9 are compression panels and this embodiment In this state, two inner and outer coil panels are used, and the inner spring 9 is weaker than the outer spring 8, and both are located between the piston 7 and the reinforcing piston 10. The rack bar 18 passes through the springs 8 and 9.

The reinforcing piston 10 is positioned between the springs 8 and 9 and the other end plug 17. As shown in FIG. 7, the reinforcing piston 10 is connected in the axial direction so as to connect the first and second head portions 121 and 122 positioned at both ends in the axial direction and the head portions 121 and 122 spaced apart by a predetermined distance. And a connecting portion 120 extending in the direction. The spindle 4 is located between the head parts 121 and 122. The two head portions 121 and 122 as a whole have a columnar shape with a predetermined length, and a through hole 121a penetrating in the axial direction is formed in the center of the first head portion 121 as shown in FIG. The other end portion side of the rack bar 18 passes therethrough. Note that the top and bottom of the first head portion 121 are cut slightly flat. In addition, the first head portion 121 is provided with a pair of upper and lower rollers 123 (driven members). The two rollers 123 are pivotally supported by pins 124 extending in the vertical direction, and are respectively positioned above and below the through hole 121a. Then, the roller 123 slightly protrudes from the force notch 121b accommodated in the horizontal notch 121b to the second head 122 side as shown in FIG. And abuts against the cam surface 110 of the cam 11. Further, since the side of the notch 121b is also opened, the roller 123 can contact the cam surface 110 of the cam 11 through the opening (see FIGS. 14 and 15).

Furthermore, the connecting portion 120 extends from the first head portion 121 to the second head portion 122 side in a rod shape 120a and from the second head portion 122 to the first head portion 121 side. It consists of a crescent-shaped extended part 120b. The connecting portion 120 has a concave curved surface 120c corresponding to the arc-shaped outer peripheral surface of the rack bar 18 on the inner side. A plurality of rollers 125 are rotatably disposed on the rod-shaped portion 120a of the connecting portion 120 via pins 126, and the rollers 125 abut against the outer peripheral surface of the rack rod 18 and rotate to prevent the rack rod 18 from moving. Reduce frictional resistance. In this embodiment, three rollers 125 are provided at intervals in the axial direction. Further, a backup ring 127 and a seal member 128 are attached to the outer peripheral surface of the second head portion 122 to ensure a sealing property between the inner surface of the cylinder 3 and the cylinder 3 includes the piston 7 and the other end plug 17. Between the second oil chamber by the second head part 122 22 and third oil chamber 23. That is, the second oil chamber 22 is between the piston 7 and the second head portion 122 of the boosting piston 10, and the third oil chamber 23 is between the second head portion 122 and the other end plug 17. is there. A recess is also formed on the inner surface of the other end plug 17, so that the other end plug 17 and the second head portion 122 abut on the outer peripheral portion. Further, a projection 122a having a smaller diameter than the recess of the other end plug 17 is formed on the outer surface of the second head portion 122, and the projection 122a is located in the recess, so that the second head 122 is in the other end. The volume of the third oil chamber 23 is smaller than the volume of the recess in a state where it abuts against the end plug 17. The third oil chamber 23 is a boosting oil chamber as a position holding means for holding the boosting piston 10 moved when the door is opened in the position until it is fully closed or just before the door is closed. Thus, when the door is opened, the volume is increased by the movement of the reinforcing piston 10, and when the door is closed, the increased volume is maintained until fully closed or just before it is fully closed by the filled hydraulic oil.

Next, communication between the first to third oil chambers 21, 22 and 23 will be described. First, as shown in FIG. 9, the piston 7 is formed with an oil passage 70 penetrating in the axial direction, and the oil passage 70 is provided with a check valve 71. Specifically, the oil passage 70 is located at the center of the piston 7. Therefore, when the piston 7 moves to the right side when the door is opened, the hydraulic oil in the second oil chamber 22 flows to the first oil chamber 21 via the oil passage 70 of the piston 7.

[0038] In addition, the housing 15 of the door closer body 1 is formed with an oil passage 72 for communicating the first oil chamber 21 and the second oil chamber 22 as shown in FIG. When the piston 7 moves to the left side when the door is closed, the hydraulic oil flows from the first oil chamber 21 to the second oil chamber 22 via the oil passage 72 of the housing 15. Since the speed adjusting valve 73 is provided in the oil passage 72, the door closing speed can be adjusted by adjusting the flow rate of the oil passage 72 by the speed adjusting valve 73.

Further, as shown in FIG. 9, an oil passage 74 penetrating in the axial direction is formed at the second head portion 122 of the reinforcing piston 10, specifically, at the center thereof. A check valve 75 is also provided. The check valve 75 is urged in a direction to close the oil passage 74 by a valve panel 76 (urging member). As will be described later, when the reinforcing piston 10 moves to the left side when the door is opened, The check valve 75 moves to the right against the urging force of the valve panel 76 due to the pressure of the hydraulic oil in the oil chamber 22, and the oil passage 74 is opened, and the second oil chamber 22 to the third oil chamber 23 are opened. Hydraulic fluid flows into (See FIGS. 16 to 18). When the door is closed, the check valve 75 is closed (FIGS. 19 and 20).

[0040] Further, as described above, by releasing the position holding of the reinforcing piston 10 by the third oil chamber 23 as the position holding means, the reinforcing piston 10 is returned to the initial position before the door opening operation, and the panel 8 , 9 is provided, and a reset mechanism that resets to the initial state before the door opening operation is provided. In this embodiment, the reset mechanism flows hydraulic oil from the third oil chamber 23, specifically, the second oil chamber. As shown in FIG. 12, as a reset mechanism, an oil passage 7 7 that communicates the second oil chamber 22 and the third oil chamber 23 formed in the housing 15, and A reset valve 78 provided in the oil passage 77 to open and close the oil passage 77 is provided. Normally, the reset valve 78 closes the oil passage 77. For example, as shown in FIG. 19, the reset valve 78 is normally in a state in which the tip 78a of the reset valve 78 projects from the inside of the housing 15 into the cam housing chamber 80 by the valve spring 79 (biasing member). As shown in FIG. 21, when the cam surface 110 of the cam 11 moves (actuates) the reset valve 78 in the fully closed state, the oil passage 77 is in communication and the third oil chamber 23 to the second oil chamber 22 is reached. And hydraulic oil flows. Specifically, as shown in FIG. 12, the cam surface 110 force S abuts against the tip 78a of the reset valve 78 and pushes the reset valve 78 into the housing 15 against the biasing force of the valve spring 79 (however, As a result, the oil passage 77 closed by the reset valve 78 is opened and hydraulic oil flows.

[0041] The oil passage 77 is further provided with a reset adjustment valve 81. By operating the reset adjustment valve 81, the flow rate when the oil passage 77 is opened when the reset valve 78 is activated. Can be adjusted. That is, the time required for the third oil chamber 23 to return the increased volume to the original state can be adjusted by the reset control valve 81. When the cam surface 110 is separated from the reset valve 78, the reset valve 78 is again protruded by the valve panel 79 and closes the oil passage 77.

[0042] The operation of the door closer configured as described above will be described mainly with reference to FIGS. When the door closer body 1 cannot be attached to the door, as shown in FIG. 13, the piston 7 comes into contact with the other end plug 16, and the roller 123 of the reinforcing piston 10 has the smallest diameter of the cam surface 110. The reinforcing piston 10 is in the rightmost position in contact with the portion 110a, and the second head portion 122 is in contact with the other end plug 17, and the reset valve 78 is pushed in by the cam surface 110 to be an oil passage. 77 is open. Therefore, the first oil Chamber 21 and third oil chamber 23 are in a minimum state, while second oil chamber 22 is in a maximum state. Panels 8 and 9 are in their most extended state, and their elastic deformation (compression amount) is at their minimum.

On the other hand, the state in which the door closer body 1 is attached to the fully closed door is the state shown in FIG. 14, and the main shaft 4 is slightly rotated counterclockwise from the state shown in FIG. Moves to the right by a predetermined amount and moves away from one end plug 16, and the springs 8 and 9 are slightly compressed in accordance with the amount of movement of the piston 7 to the right. The cam 11 also rotates integrally with the main shaft 4. The minimum diameter portion 110a remains in contact with the force roller 123. Therefore, the reinforcing piston 10 remains in the initial position, and the second head portion 122 is also in the other position. It remains in contact with the other end plug 17. Further, the reset valve 78 remains in contact with the cam surface 110, and although the amount pushed is smaller than that in FIG. 13, the oil passage 77 is still open. The reason why the piston 7 is slightly moved to the right side in the state where the door closer body 1 is attached to the fully closed door is to cause a predetermined closing force when fully closed. Therefore, it is possible to prevent the door from being inadvertently opened and to ensure airtightness. If the position of the spindle 4 and the cam 11 in the state shown in FIG. 13 is set to 0 ° as a reference, the state shown in FIG. 14 is, for example, 16 ° rotated counterclockwise, and the door is fully closed. The angle is at 0 °. This 16 ° value is set according to the conditions such as the installation location.

[0044] The force that starts opening the door from such a fully closed state, the main shaft 4 rotates in proportion to the opening angle of the door, and the piston 7 moves to the right side together with the rack rod 18. Therefore, in the opening operation, the moving amount of the piston 7 is proportional to the opening angle of the door, and the amount by which the piston 7 compresses the panels 8 and 9 (elastic deformation amount) is also proportional to the opening angle of the door. Specifically, the state of FIG. 15 is a state in which the main shaft 4 is rotated by 14 ° from the state of FIG. 14, that is, the door is opened from the fully closed state by an angle corresponding to the rotation of the main shaft 4 by 14 °. As the main shaft 4 rotates by 14 °, the piston 7 moves to the right, compressing the springs 8 and 9 by that amount. Since the roller 123 of the boosting piston 10 is still in contact with the minimum diameter portion 110a, the boosting piston 10 has not moved, and the third oil chamber 23 remains minimum. However, since the cam surface 110 is separated from the reset valve 78, the reset valve 78 protrudes into the cam housing chamber 80, and therefore the oil passage 77 is closed. Then, after the state shown in FIG. 15, the roller 123 of the reinforcing piston 10 moves the contact portion from the minimum diameter portion 110a of the cam surface 110 to the increasing diameter portion 11 Ob side. The minimum diameter portion 110a has a constant diameter, but this increased diameter portion 110b is a region where the diameter gradually increases. From the opening angle of the main shaft 4 as shown in FIG. 4 from the opening angle of 60 ° up to the opening angle of 74 ° rotation and the auxiliary enhancement region of 75 ° from the opening angle in Fig. 17 to the opening angle of 149 ° rotation of the main shaft 4 as shown in Fig. 18 Composed. In the main reinforcement region where the angle of the main shaft 4 is 14 ° to 74 °, as shown in FIGS. 15 to 17, the roller 123 is brought into contact with the main enhancement region of the increased diameter portion 110b of the cam surface 110, thereby Moves all the way to the left. Due to the movement of the boosting piston 10 to the left side, the check valve 75 of the boosting piston 10 receives pressure from the second oil chamber 22 and stakes it to the urging force of the valve panel 76 and moves to the right side. Open the oil passage 74 of the head part 122. Therefore, the hydraulic oil flows from the second oil chamber 22 to the third oil chamber 23 through the oil passage 74 of the second head portion 122. Further, the reinforcing piston 10 compresses the springs 8 and 9 by pressing the springs 8 and 9 from the side opposite to the piston 7 by the first head portion 121. As described above, the amount of movement of the piston 7 is proportional to the rotation of the main shaft 4, that is, the door opening angle. Therefore, the compression amount of the springs 8 and 9 by this piston 7 alone is proportional to the force S and the reinforcing piston 10 is When moved to the left, the panels 8 and 9 are also compressed by the movement of the reinforcing piston 10. That is, while the roller 123 is in contact with the increased diameter portion 110b of the cam surface 110 (between FIGS. 15 to 18), the springs 8 and 9 are compressed by the piston 7 and the increasing piston 10 from both sides. Therefore, the degree of increase in the compression amount (elastic deformation amount) of the panels 8 and 9 is larger than the time when the roller 123 is in contact with the minimum diameter portion 110a of the cam surface 110 (the period in which only the piston 7 is compressed). Is also big. Further, the degree of increase in the compression amount of the panels 8 and 9 while the roller 123 is in contact with the main reinforcing region of the reinforcing diameter portion 110b of the cam surface 110 (between FIGS. 15 to 17) is proportional (however, The proportionality coefficient may be larger than that during contact with the minimum diameter portion 110a), but in the present embodiment, the proportional coefficient is set so as to increase at an accelerated rate. The increase in the first half of the period (30 °) is large, and the increase in the second half (30 °) of Figures 16 to 17 is smaller.

Further, from FIG. 17 to FIG. 18, that is, from the state where the main shaft 4 is rotated by 74 ° from the fully closed state to the state where the main shaft 4 is similarly rotated by 149 °, the roller 123 contacts the sub-enhancement region. This secondary increase In the strong region, the amount by which the reinforcing piston 10 is moved to the left is much smaller than in the main reinforcing region. Accordingly, it is possible to eliminate the secondary enhancement region and make the diameter constant, but the secondary enhancement region is provided and the enhancement piston 10 is slightly moved to the left for the following reason. That is, the volume of the third oil chamber 23 is increased at once by moving the boosting piston 10 to the left at a time in the main enhancement region, but if there is a slight amount of air in the third oil chamber 23, Air may be compressed by pressure. Therefore, after injecting the hydraulic oil into the third oil chamber 23 at a time in the main augmentation region, the augmentation piston 10 is moved slightly to the left in the secondary augmentation region, so that the inside of the third oil chamber 23 The air compression is compensated. In addition, since the roller 123 immediately separates from the cam surface 110 when the door starts to close from the state shown in FIG. 18, the resistance caused by the contact of the roller 123 with the cam surface 110 does not occur when the door is closed. It will be.

[0047] As shown in FIG. 18, when the door is opened from the fully closed state at an angle corresponding to the rotation of the main shaft 4 by 149 °, the movement amount L of the piston 7 to the right side and the left side of the reinforcing piston 10 to the left side are increased. Force with total amount of movement S (L + S) is the total amount of compression (elastic deformation amount) of springs 8 and 9 From there, subtract initial compression amount M in the fully closed state in Fig. 14 (L + S — M) is the amount of compression of the panels 8 and 9 caused by the opening operation. As described above, the initial compression amount M is slightly set and changed, but in any case, the panels 8 and 9 have been compressed by the amount of compression S generated by the movement of the boosting piston 10. Therefore, compared with the case of piston 7 alone, the closing force is increased accordingly. During the opening operation, the reset valve 78 is separated from the cam surface 110 and protrudes, so that the oil passage 77 remains closed by the reset valve 78.

[0048] Next, the closing operation will be described. When the main shaft 4 in Fig. 18 is rotated 149 ° from the fully closed position and the door is released by releasing the hand, the piston 7 is urged to the left, which is the closing direction, by the elastic force of the compressed panels 8 and 9. Therefore, the piston 7 moves to the left by the elastic force, and the rack rod 18 also moves to the left along with it, and the spindle 4 rotates clockwise. Therefore, a closing force is applied to the door, and the door automatically performs a closing operation. Then, from the state in which the main shaft 4 in FIG. 18 is rotated by 149 ° from the fully closed state, the main shaft 4 in FIG. In the rotated state, the door 4 is closed so that the spindle 4 in Fig. 20 has rotated 14 ° from the fully closed position. During this time, the piston 7 gradually moves to the left side due to the elastic force of the springs 8 and 9, but the hydraulic oil is transferred from the first oil chamber 21 to the second oil chamber 22 through the oil passage 72 in the housing 15. As a result, the first oil chamber 21 gradually decreases. As described above, the flow rate of the oil passage 72 at this time can be adjusted by the speed adjustment valve 73, and thus the closing speed can also be adjusted.

On the other hand, the reset valve 78 does not come into contact with the cam surface 110 and protrudes into the force housing chamber 80 as shown in FIG. Is closed. For this reason, the inflow of hydraulic oil from the third oil chamber 23 to the second oil chamber 22 is blocked, and the third oil chamber 23 maintains its increased volume. As the third oil chamber 23 maintains its state, the boosting piston 10 cannot move to the left side. Therefore, the cam surface 110 is separated from the roller 123, and the compression amount of the panels 8 and 9 by the reinforcing piston 10 is maintained as it is. That is, from FIG. 18 to FIG. 20, the compression amount of the springs 8 and 9 by the piston 7 decreases in proportion to the closing operation, but the reinforcing piston 10 maintains its position by the third oil chamber 23. The compression of the panels 8 and 9 by the reinforcing piston 10 does not decrease and remains constant. Therefore, the closing operation is performed while the compression amount of the springs 8 and 9 is kept larger by the compression amount by the boosting piston 10 compared to the piston 7 alone, and the closing door is larger than that of the piston 7 alone. Power is obtained.

[0050] This large closing force is maintained in a wide section until the fully closed state with an opening angle of 0 ° shown in FIG. Then, in FIG. 21, the door is just fully closed. At that moment, the stepped portion 110c directed toward the small diameter provided at the tip of the increased diameter portion 110b of the cam surface 110 comes into contact with the reset valve 78. When the step 110c of the cam surface 110 abuts against the reset valve 78 and pushes the reset valve 78 slightly, the reset valve 78 operates to open the oil passage 77. As a result, the hydraulic oil in the third oil chamber 23 starts to flow into the second oil chamber 22 via the oil passage 77 of the housing 15. As the hydraulic oil flows out from the third oil chamber 23, the boosting piston 10 also starts to move to the right. The reset flow control valve 81 is provided in the oil passage 77 of the housing 15 and the flow rate of the hydraulic oil is adjusted, so that the hydraulic oil gradually flows out from the third oil chamber 23, and the boosting piston 10 Will gradually move to the right. Then, the springs 8, 9 and the reinforcing piston 10 return to the initial state before the door opening operation as shown in FIG. Note that the flow rate of the hydraulic oil from the third oil chamber 23 can be adjusted by the reset control valve 81, as shown in FIG. The time required from the time when the fully closed state is reset to the initial state of FIG. 14 can be set to about 2 to 3 seconds, for example, but can be set longer or shorter than this. As described above, in the door closer according to the present embodiment, of the compression deformation of the panels 8 and 9 compressed in the opening operation, the compression due to the movement of the reinforcing piston 10 is completely closed when the door is closed. As a result, the door closing force is larger than when the panels 8 and 9 are compressed with only the piston 7 without the piston 10 for reinforcement. In addition, since the compression by the reinforcing piston 10 is maintained until the fully closed state, the closing force increased by the reinforcing piston 10 continues to act in a wide range until the fully closed state. Therefore, unlike the conventional case that generates a large closing force only when closing, the door does not close due to the influence of wind at a large opening angle, and it can be surely closed until it is fully closed. . In addition, the piston 10 for reinforcement is provided separately from the piston 7 and the structure for maintaining the compressive deformation of the panels 8 and 9 corresponding to the movement of the piston 10 for enhancement is generated. Part (S) of the compression deformation (L + S- M) of panels 8 and 9 can be easily maintained. Further, the volume of the third oil chamber 23 is increased by moving the augmenting piston 10 to the left side, and the volume of the third oil chamber 23 is maintained by preventing the hydraulic oil from flowing out by the reset valve 78. Therefore, it is possible to maintain a part of the compression deformation of the panels 8 and 9 with a simple configuration using hydraulic oil, and when the reset force is reset, the hydraulic oil is supplied to the third oil chamber by the operation of the reset valve 78. Since it only needs to flow out from 23, the mechanism for resetting to the initial state can be made extremely simple and reliable. Since the reinforcement piston 10 is moved by the cam surface 110 of the cam 11 rotating integrally with the main shaft 4, the movement control is easy. That is, by changing the shape of the cam surface 110 in various ways, it is possible to set various amounts of movement and timing of the enhancement piston 10. In addition, since the cam 11 is integrated with the main shaft 4, the phase of the pinion 6 and the cam surface 110 can be adjusted reliably, and the movement of the piston 7 and the movement of the boosting piston 10 can be reliably linked. it can. Furthermore, since the reset valve 78 is automatically pressed and operated by the return operation of the cam surface 110, a separate mechanism for operating the reset valve 78 is unnecessary, and the force is also reduced. The operation timing of the reset valve 78 can be designed easily in conjunction with the movement of the boosting piston 10. In this embodiment, the force S that activates the reset valve 78 at the fully closed timing, for example, fully closed The reset valve 78 may be operated such that the stepped portion 110c of the cam surface 110 contacts the reset valve 78 at the immediately preceding timing. In addition, by operating the reset control valve 81, the time from the start of the operation of the reset valve 78 to the reset to the initial state before the door opening operation can be easily adjusted.

[0052] While a large closing force can be obtained in the closing operation, after the fully closing operation, the compression deformation of the panels 8 and 9 is automatically reset every time the closing operation is performed until the initial state before the opening operation. Therefore, when opening the door again from the fully closed state, the force required to open the door is small.

Furthermore, in this embodiment, the fully closed cover is particularly effective in the door closer using the link mechanism because the reinforcing piston 10 operates after the door has opened a predetermined angle. That is, in a configuration in which the bracket 2 and the door closer body 1 are connected to each other through a link mechanism used for a rotating door, the force that must be applied to the door for the opening operation is usually fully closed. Gradually decreases from the predetermined opening angle, and the degree of decrease decreases from the predetermined opening angle and converges to a substantially constant force. The required degree of force reduction is the largest in the range of the predetermined angle from the fully closed position. Therefore, if the panel 8 and 9 are compressed by the boosting piston 10 after the opening angle where the force is greatly reduced, The force for opening the door, which is relatively increased by compressing the panels 8 and 9 with the piston 10 for reinforcement, does not place a heavy burden on the user. it can.

[0054] A conceptual illustration of the relationship between the force required to open the door (opening force) and the closing force applied to the door by the elastic force of the panels 8 and 9 when the door is closed and the door opening angle is shown. FIG. 22 shows the case of the conventional configuration in which FIG. 22 (b) compresses only with the piston 7, and FIG. 22 (a) shows the case of the configuration of the present embodiment. The opening force and closing force are both plotted as the force acting on the door. In the configuration where panels 8 and 9 are compressed using only piston 7, as shown in Fig. 22 (b), the opening force decreases greatly from the beginning of opening to a predetermined angle and converges to a substantially constant opening force (line T2 ) When the door is closed, the closing force is lower than the opening force due to mechanical loss such as frictional resistance (line C2). On the other hand, in the case of the present embodiment, as shown in FIG. 22 (a), it once increases after decreasing as shown by line T1, but the increased maximum value indicates the opening force required at the start of opening the door. Don't exceed it. As described above, in this embodiment, the spindle 4 is rotated 14 ° from the fully closed state. The section between the main shaft 4 rotated by 74 ° from the fully closed state is the main reinforcing diameter portion 110b, and the reinforcing piston 10 is moved to the left at a stretch in the first half (14 ° force is also 44 °). What uses this principle. In Fig. 22 (a), the conventional door opening force is indicated by a two-dot chain line (line T2). Also in the case of Fig. 22 (a), the change in the closing force at the time of closing is not different from the conventional one, but its absolute value is larger than the conventional one. This is because the compression by the boosting piston 10 is maintained when the door is closed, and the same closing force as that obtained by changing the springs 8 and 9 to a stronger one can be obtained. In this way, it is possible to obtain a large door closing force while suppressing an increase in burden when the door is opened.

[0055] It should be noted that a determination unit that makes it possible to visually recognize whether or not the reset valve 78 is activated may be provided based on the external force of the door closer body 1. For example, as shown in FIG. 23, the base end portion 78b of the reset valve 78 is extended so as to pass through the adjustment bushing 82. In FIG. 23 (a), the tip 78a of the reset valve 78 is not pushed by the cam 11, and the reset valve 78 receives the urging force of the valve spring 79 and protrudes into the cam housing chamber 80. In this case, the base end portion 78b of the reset valve 78 does not protrude outward from the adjustment bushing 82. On the other hand, in FIG. 23 (b), the tip 78a of the reset valve 78 is pushed by the cam 11, and the reset valve 78 is pushed against the urging force of the valve panel 79, and the reset valve 78 is activated. In this case, the base end portion 78b of the reset valve 78 protrudes outward from the adjusting bush 82 by a predetermined amount. In this way, the user can determine whether the reset valve 78 is operated depending on whether or not the base end portion 78b of the reset valve 78 protrudes outward from the end face of the adjustment bushing 82, with the base end portion 78b of the reset valve 78 serving as a determination unit. The presence or absence can be determined. In general, the timing at which the reset valve 78 is actuated is preferably fully closed or just before it is fully closed. The timing at which the reset valve 78 is actuated may vary depending on variations in the shape and installation of the door. In such a case, if the presence / absence of the operation of the reset valve 78 can be visually recognized from the outside by moving the base 78b of the reset valve 78, the user can surely know the operation timing of the reset valve 78, It is possible to prevent malfunction of the door closer.

[0056] However, the base end portion 78b of the reset valve 78 is not limited to the case where the base end portion 78b of the reset valve 78 protrudes outward from the end surface of the adjustment bushing 82, and the base end portion 78b of the reset valve 78 protrudes from the outer surface of the door closer body 1. Then, the user can easily determine whether or not the reset valve 78 is activated similarly. Also, The configuration of the discriminating portion is not limited to the base end portion 78b of the reset valve 78, and may be anything that can be moved out of the outer surface of the door closer body 1 in conjunction with the sliding movement of the reset valve 78, for example, different from the reset valve 78. Even if it is a body member, the interlocking structure is simplified by integrating with the reset valve 78 like the base end portion 78b of the reset valve 78. Further, the configuration is not limited to the configuration in which the determination unit moves out of the outer surface of the door closer body 1, and any configuration that works in conjunction with the reset valve 78 and whose behavior is visible from the outside is sufficient. Therefore, in addition to mechanically interlocking the reset valve 78 and the determining unit, an electrically interlocked configuration may be used. In any case, by providing a determination unit that interlocks with the reset valve 78 so that the operation of the reset valve 78 can be visually recognized from the outside by the determination unit, the user can determine the operation timing of the reset valve 78. It is possible to accurately grasp and prevent malfunction of the door closer due to timing failure. In addition, when using a configuration other than the reset valve 78 as a reset mechanism for draining the hydraulic oil from the third oil chamber 23, it is of course sufficient to provide a discriminating section that allows the reset mechanism to be visually confirmed from the outside. In such a case, a configuration in which the reset mechanism and the determination unit are interlocked is preferable. It should be noted that it is possible to provide a means for making it possible to determine whether or not the reset mechanism is activated by sound, particularly in some places.

[0057] Further, an urging means for urging the reinforcing piston 10 in the direction of movement (left side) may be provided to assist the movement of the reinforcing piston 10 in the opening operation. For example, as shown in FIG. 24, an auxiliary panel 40 (compression coil panel) that biases the boosting piston 10 to the left in the third oil chamber 23 (between the other end plug 17 and the boosting piston 10). May be provided as a biasing means. By inserting the auxiliary spring 40 into the third oil chamber 23 in this way, the elastic force of the auxiliary panel 40 is increased when the reinforcing piston 10 is moved by the cam 11 during the opening operation. The reinforcing piston 10 moves to the left side easily. That is, the burden on the user when the reinforcing piston 10 moves in the opening operation is reduced. However, it is a matter of course that the auxiliary spring 40 inserted into the third oil chamber 23 is weaker than the main springs 8 and 9 compressed by the piston 7, so that the boosting piston is operated after the reset valve 78 is operated. Even when 10 returns to its original state, it returns without problems.

[0058] The springs 8 and 9 compressed by the piston 7 can be variously changed, and two large and small coaxially are provided between the piston 7 and the reinforcing piston 10 as in the above embodiment. In addition to the configuration, the panel can be three or more or vice versa. For example, as shown in FIG. 25, a panel 41 is provided between the piston 7 and the first head portion 121 of the reinforcement piston 10, and the tip of the rack bar 18 and the second head of the reinforcement piston 10 are provided. The spring 42 may be provided between the head portion 122 and the head portion 122. Furthermore, as shown in FIG. 26, the rack bar 18 and the panel 43 may be arranged in parallel, that is, in a non-coaxial arrangement. As described above, the number, strength, arrangement, shape, configuration, and the like of the panel compressed by the pinion 6 can be appropriately changed.

Furthermore, the shape of the cam surface 110 of the cam 11 can be variously changed. For example, as shown in FIG. 27, a climbing wall portion 110d in which the force for moving the boosting piston 10 increases stepwise is provided on the reinforcing diameter portion 110b of the cam surface 110, which is the moving section of the boosting piston 10. Anyway. That is, when the roller 123 that rotates in contact with the cam surface 110 contacts the climbing wall portion 110d, the rotation of the cam 11, that is, the rotation of the main shaft 4, is greatly suppressed at that point. Therefore, the door opening operation is temporarily stopped at that point, and for example, it is prevented that the door is vigorously opened due to wind or the like and collides with a wall or the like. If the roller 123 gets over the wall 110d, the door can be opened with a small force. Further, the climbing wall portion l id is formed as a concave curved surface that engages with the outer peripheral surface of the roller 123.

In addition, the incorporation of the cam 11 into the main shaft 4 can also be changed. In the configuration described above, the cam 11 is connected to the main shaft 4 by incorporating the pair of upper and lower cams 11 into the main shaft 4 and engaging with the pinion 6. For example, as shown in FIG. 28, the fixing member 44 is positioned between the upper and lower cams 11, and the upper and lower cams 11 are fixed to the fixing member 44 by screws or the like. Preferably, it may be detachably fixed. In this way, by fixing the fixing member 44 to the main shaft 4 and connecting the upper and lower cams 11 by the fixing member 44, the cam 11 and the main shaft 4 can be more firmly integrated, and the cam when the main shaft 4 rotates. Since the cam surface 110 with less blurring 11 functions as designed, the boosting piston 10 can be moved accurately and smoothly. In addition to assembling the separate cam 11 to the main shaft 4, the main shaft 4 and the cam 11 may be integrally formed by molding. In addition, although the cam 11 is arranged up and down, the shape, configuration, arrangement, etc. of the cam 11 may be changed in various ways. In addition, a single cam 11 is provided at the substantially central portion of the pinion 6 and a single roller 123 that contacts the cam 11 may be used. A notch for avoiding the cam 11 is formed along the axial direction of the rack bar 18 in the substantially central portion of the rack 5, and the cam 11 is straddled with the rack 5 up and down, and the upper and lower portions are the upper and lower portions of the pinion 6. It may be configured so as to be combined with each other. In any case, by using the cam 11 to control the movement of the boosting piston 10, there is an advantage that it can be accurately controlled with a simple mechanism. When the door is opened, the reinforcing piston 10 is moved on the cam surface 110, while when the door is closed, the position of the reinforcing piston 10 is maintained and the cam 11 rotates in the opposite direction to that when the door is opened. The roller 123 as a driven member is separated from 110, and unnecessary mechanical loss such as frictional resistance when the door is closed can be suppressed.

[0061] Furthermore, the configuration in which the door closer body 1 is attached to the rotating door has been described, but the door closer can also be applied to a so-called floor hinge. That is, it is a configuration in which a closing door is directly attached from the main shaft 4 to the central axis of the rotating door. In this case, for example, as shown in FIGS. The door closer body 1 can be installed in the door. The door closer body 1 is inserted into the installation recess F1 provided on the floor surface F, and the bolt 45 is used as a tension member between the wall surface F2 of the installation recess F1 and the outer surface of the door closer body 1. Since the bolt 45 is screwed to the outer surface of the door closer body 1 and protrudes to the side, the door closer body 1 can be easily installed by adjusting the protruding amount by tightening and loosening the bolt 45. Can be fixed.

[0062] Further, the force may be configured such that the reinforcing piston 10 is moved only in a predetermined section of the entire opening operation section. Alternatively, the reinforcing piston 10 may be moved in the entire opening operation section. Even in this case, as described above, the reinforcing piston 10 may be configured to move from the beginning of opening, in addition to the predetermined section after opening at a predetermined angle from the fully closed state. However, in a configuration in which the door closer body 1 is attached to the rotating door and the door closer body 1 and the bracket 2 are connected by a link mechanism, the boosting piston 10 moves to a predetermined section after opening at a predetermined angle from the fully closed position. It is preferable to make it as described above. In the case of a configuration in which the door closing force is directly attached to the central axis of the rotating door like a so-called floor hinge, the degree of increase in the door opening force is substantially constant regardless of the opening angle. The same effect can be obtained by moving the reinforcing piston 10 in any section, but the door can be moved by moving the reinforcing piston 10 after the door is opened to some extent. The inertial force assists the force for moving the reinforcing piston 10 and gives the user a natural feeling.

It should be noted that the configuration may be such that the reinforcing piston 10 is not provided, and in the above-described embodiment, the example applied to the rotating door has been described, but the present invention can also be applied to a sliding door.

Claims

The scope of the claims

[1] A piston that reciprocates in the cylinder according to the opening / closing operation of the door, and elastically deforming according to the movement of the piston in the opening direction when the door is opened, and biasing the piston in the closing direction when the door is closed by the elastic force A door closer provided with an elastic member for providing a door with a closing force, and a part of the elastic deformation of the elastic member caused by the opening operation is maintained in a deformed state until the door is fully closed or immediately before the door is fully closed. The door closer further comprises elastic deformation control means for releasing the deformation state and resetting the elastic member to the initial state before the door opening operation.

[2] The elastic deformation control means is provided with a reinforcing piston in the cylinder in addition to the piston, and the reinforcing piston moves when the door is opened to elastically deform the elastic member in cooperation with the piston, thereby controlling elastic deformation. 2. The door closer according to claim 1, wherein the means maintains and releases the elastic deformation of the elastic member due to the movement of the reinforcing piston as a part of the elastic deformation in a deformed state until the door is fully closed or immediately before the door is fully closed.

3. The door closer according to claim 2, wherein the elastic member is a compression panel that is compressed when the door is opened, and the reinforcing piston compresses the compression panel from a side opposite to the piston.

4. The door closer according to claim 2, wherein the elastic deformation control means includes a cam as driving means for the reinforcing piston when the door is opened.

[5] The main shaft includes a main shaft that rotates forward and backward in conjunction with the opening and closing of the door, and a rack and a pinion that connect the main shaft and the piston so that the piston reciprocates in the cylinder as the main shaft rotates. 5. The door closer according to claim 4, wherein the door closer is provided so as to rotate in a body.

6. The door closer according to claim 5, wherein when the door is opened, the follower member is brought into contact with the cam to move the reinforcing piston, and when the door is closed, the follower member is separated from the cam by reverse rotation of the main shaft.

[7] The door closer according to claim 4, wherein the cam surface of the cam is provided with a climbing wall portion in which a force for moving the boosting piston increases stepwise in the moving section of the boosting piston.

[8] The elastic deformation control means is provided with position holding means for holding the reinforcing piston moved at the time of opening the door at the position until it is fully closed or just before the door is closed, and the position holding means is opened. 3. The door closer according to claim 2, wherein the door closer is a boosting oil chamber that increases its volume by movement of the boosting piston when the door is closed and maintains the volume until fully closed or immediately before the fully closing by the filled hydraulic oil when the door is closed.

[9] The elastic deformation control means includes a position holding means for holding the boosting piston moved when the door is opened at the position until the piston is fully closed or just before the door is closed, and holds the position of the boosting piston by the position holding means. 3. The door closer according to claim 2, further comprising: a reset mechanism that resets the reinforcing piston to the initial position before the door opening operation by releasing and releasing the elastic member to the initial state before the door opening operation.

10. The door closer according to claim 9, wherein the reset mechanism is configured such that the operation starting force is adjustable so that the time until the elastic member is reset to the initial state before the door opening operation can be adjusted.

11. The door closer according to claim 9, wherein the elastic deformation control means includes a cam as a driving means of the reinforcing piston, and the cam operates the reset mechanism immediately before or after the full closure.

12. The door closer according to claim 9, further comprising a determination unit that makes it possible to visually confirm whether or not the reset mechanism is activated.

13. The door closer according to claim 12, wherein the discriminating section is configured to be withdrawn from the outer surface of the door closer in response to whether the reset mechanism is activated.

14. The door closer according to claim 2, wherein the reinforcing piston moves to a predetermined section after the predetermined amount of door is opened from the fully closed position.

[15] A door closer that includes a door closer body that is attached to a rotating door and a bracket that is attached to a door frame. The door closer body is provided with a cylinder, and the bracket and the door closer body are connected via a link mechanism. 15. The door closer according to claim 14, wherein the reinforcing piston moves to a predetermined section after the door is opened at a predetermined angle from the fully closed position.

16. The door closer according to claim 2, further comprising biasing means for biasing the reinforcing piston in the direction of movement when the door is opened.