JP6178083B2 - Door closer - Google Patents

Description

  The present invention relates to a door closer.

  As a kind of door closer, there is a floor hinge of the type embedded in the floor as in Patent Document 1 below. The floor hinge proposed by the present applicant in the following Patent Document 1 has a structure in which a spring seat on the fixed side, a return spring, and a piston are arranged in order from the side close to the main shaft. In other words, the return spring is interposed between the piston and the fixed-side spring receiving seat, and the end surface on the main shaft side of the piston is used as the movable-side spring receiving seat. Then, when the door is opened, the piston moves toward the fixed spring receiving seat so that the return spring compresses and accumulates the closing force, and the closing spring (spring force) of the return spring is used. The door is automatically closed by rotating the spindle. However, in the floor hinge of this configuration, the spring force of the return spring cannot be adjusted from the outside of the main body housing without disassembling, so excessively when opening the door due to the size and weight of the door. It can be a great force or the door may not close completely.

No. 7-55254

  Therefore, the present invention has been made in view of the above-mentioned conventional problems, and an object thereof is to provide a door closer that can easily adjust the spring force of the return spring.

The present invention has been made to solve the above problems, and a door closer according to the present invention includes a main shaft that rotates as the door is opened and closed, an oil chamber that supports the main shaft and is filled with hydraulic oil. And the oil chamber is divided into a first oil chamber on the main shaft side and a second oil chamber on the opposite side of the main shaft. Sometimes a piston that moves toward the second oil chamber, a piston drive that converts the rotational movement of the main shaft into a linear motion to drive the piston, and a fixed-side spring seat that is located on the same line as the piston and close to the main shaft It is equipped with a return spring interposed between the movable spring seat that is far from the main shaft, and returns when the movable spring seat moves closer to the fixed spring seat when opening the door. The door closer that compresses the closing force and stores the closing force The spring receiving member having a fixed-side spring receiving seat is configured to be able to change the position in the axial direction of the piston with respect to the main body housing, and the position of the spring receiving member can be changed by an operation from the outside of the main body housing. A spring force adjusting mechanism that adjusts the spring force of the spring is provided . The piston is located between the spring receiving member and the main shaft, and the piston and the movable spring receiving seat are connected by a connecting rod that penetrates the spring receiving member. The connecting rod has a cylindrical portion that opens at the end opposite to the piston, and the spring force adjustment mechanism includes an operation portion provided at the end of the main body housing on the second oil chamber side, And a transmission portion that transmits the movement of the operation portion to the spring receiving member via the inside of the cylindrical portion of the connecting rod and moves the spring receiving member in the axial direction of the piston .

  In the door closer configured as described above, the piston moves toward the second oil chamber during the closing operation, so that the pressure in the first oil chamber does not increase during the closing operation. Therefore, there is no possibility that the hydraulic oil leaks from the bearing portion of the main shaft due to the pressure increase in the first oil chamber. Since the spring receiving member is configured to change its position with respect to the main body housing and includes a spring force adjusting mechanism, the position of the spring receiving member is changed by operating the spring force adjusting mechanism from the outside of the main body housing. Thus, the spring force of the return spring can be easily adjusted.

The configuration in which piston is positioned between the spring receiving member and the main shaft, i.e., the piston is configured to position the spindle side against the spring receiving member, and the piston main axis against the spring receiving member Compared to the configuration located on the opposite side, the spring force adjusting mechanism can be easily configured. And since the operation part is provided in the edge part by the side of the 2nd oil chamber of a main body housing, an operation part can be operated easily. Even if the spring receiving member is located away from the end of the main body housing on the second oil chamber side, and there is a connecting rod or return spring between them, the transmission portion is the cylindrical portion of the connecting rod. Since the movement of the operation part is transmitted using the space inside the movement of the operation part, the movement of the operation part is reliably transmitted, and the enlargement of the main body housing can be prevented.

  Further, a lateral hole is formed in the peripheral wall of the cylindrical portion of the connecting rod, and the spring force adjusting mechanism passes through the end portion of the main body housing on the second oil chamber side and passes through the inside of the cylindrical portion of the connecting rod. It is preferable to include an adjustment shaft and a linkage member that links the adjustment shaft and the spring receiving member via a horizontal hole of the connecting rod. Adjustment that protrudes from the end of the main body housing on the second oil chamber side by inserting the adjustment shaft inside the connecting rod and connecting the adjusting shaft and the spring receiving member through the horizontal hole of the connecting rod by the connecting member By manipulating the protruding portion of the shaft, the position of the spring receiving member can be easily changed.

  Furthermore, the connecting rod has a cylindrical shape over its entire length, and a communication hole with a check valve that connects the first oil chamber and the second oil chamber is formed at the center of the piston. It is preferable that the communication hole is located inside the end of the. Since the communication hole with the check valve is formed in the piston, the hydraulic oil can be passed through the communication hole of the piston during the opening operation, and the communication hole can be closed by the check valve during the closing operation. Moreover, a communicating hole can be located inside the edge part by the side of the piston by making a connecting rod cylindrical shape over the full length. Therefore, it is possible to prevent an increase in the size of the piston and an increase in the size of the main body housing as compared with the configuration in which the communication hole is located outside the connecting rod. Moreover, since the connecting rod is cylindrical up to the end on the piston side, the hydraulic oil can pass through the inside of the connecting rod from the communication hole of the piston. In addition, when the connecting rod has a horizontal hole, the hydraulic oil can easily move from the inside of the connecting rod to the outside through the horizontal hole.

  As described above, in the door closer according to the present invention, the position of the spring receiving member having the fixed spring receiving seat can be changed from the outside of the main body housing by the spring force adjusting mechanism. Accordingly, the spring force of the return spring can be easily adjusted.

It is sectional drawing of the front view which shows the floor hinge as one embodiment of the present invention, and shows a closed state with the minimum spring force. It is sectional drawing of the planar view which shows the floor hinge, Comprising: A spring force is the minimum and shows a closed state. It is sectional drawing of the front view which shows the floor hinge, Comprising: The state when a spring force is the minimum and a door opens 180 degree | times is shown. It is sectional drawing of the planar view which shows the floor hinge, Comprising: The state when a spring force is the minimum and a door opens 180 degree | times is shown. It is sectional drawing which shows the principal part of the floor hinge, (a) shows the state in which the check valve was closed in the door closing operation, (b) shows the state in which the check valve was opened in the door opening operation. Yes. Sectional drawing of the planar view which shows the principal part of the floor hinge. It is sectional drawing of the front view which shows the floor hinge, Comprising: A spring force is the maximum and shows a closed state. It is sectional drawing of the planar view which shows the floor hinge, Comprising: A spring force is the maximum and shows a closed state. It is sectional drawing of the front view which shows the floor hinge, Comprising: A spring force is the maximum and a state when a door opens 180 degree | times is shown. It is sectional drawing of the planar view which shows the floor hinge, Comprising: A spring force is the maximum and a state when a door opens 180 degree | times is shown.

  Hereinafter, a floor hinge as a door closer according to an embodiment of the present invention will be described with reference to FIGS. The floor hinge in the present embodiment includes a main body housing 1 that forms an oil chamber filled with hydraulic oil. The main body housing 1 has a constant thickness in the vertical direction as shown in FIG. 1 and is long in a predetermined direction as shown in FIG. The main body housing 1 incorporates a piston 2 that divides the oil chamber into two chambers, and the longitudinal direction of the main body housing 1 is the axial direction of the piston 2. Hereinafter, the axial direction means the axial direction of the piston 2 unless otherwise specified in the detailed description. In the drawings, the right side is an axial direction one end side and the left side is an axial direction other end side. However, the axial direction one end portion side is simply referred to as a front side, and the axial direction other end portion side is simply referred to as a rear side.

  The main body housing 1 is composed of a main portion 10 constituting a main portion, an upper cap 11 attached to an upper portion on the rear side, and a lateral cap 12 attached to an end portion on the front side. An oil chamber to be filled is formed.

  A main shaft 3 is pivotally supported at the rear portion of the main body housing 1. The main shaft 3 serves as a rotation axis of the door, and rotates according to the opening / closing operation of the door. The center of the main shaft 3 is located on the center line (on the axis) of the piston 2 in plan view. The main shaft 3 is rotatably supported on the bottom of the upper cap 11 and the main portion 10 via bearings 13 and 14, and the upper portion protrudes upward from the upper cap 11 by a predetermined length. A heart-shaped cam 4 is provided on the main shaft 3. The cam 4 rotates integrally with the main shaft 3. The cam 4 may be integrally formed so as to constitute one member with the main shaft 3, or may be a separate member from the main shaft 3. In any case, the cam 4 rotates integrally with the main shaft 3 together with the opening / closing operation of the door, and functions as a piston drive unit that drives the piston 2 by converting the rotation operation of the main shaft 3 into a linear motion in the axial direction. The cam 4 is a plate cam whose peripheral surface is a cam surface, and only a predetermined angle region of the entire periphery is used as a section used in the door opening / closing operation. In the present embodiment, the peripheral surface of the cam 4 has a symmetrical shape, and one of the two 180-degree regions is used as a use section, but may be an asymmetric shape. Incidentally, a recess 4a is formed in one place on the cam surface. The recess 4a is formed at a position corresponding to a closed state, that is, when the door opening degree is 0 degree.

  Slide plates 5 are arranged above and below the cam 4, respectively. A roller 6 as a cam follower that rotates in contact with the cam 4 is provided between the sliding plates 5, and a support shaft of the roller 6 is attached to the sliding plates 5. Therefore, when the cam 4 rotates with the main shaft 3, the sliding plate 5 moves in the axial direction via the roller 6. When the cam 4 is rotated 180 degrees, the state shown in FIGS. 1 and 2 is changed to the state shown in FIGS. 3 and 4. The roller 6 is provided on the rear side of the cam 4, and when the opening degree of the door is 0 degree as shown in FIGS. 1 and 2, the roller 6 is engaged with the recess 4 a of the cam 4. A roller 7 is also provided on the front side of the cam 4. The front roller 7 has a slightly smaller diameter than the rear roller 6, and the door opening degree is 180 as shown in FIGS. At this time, the roller 7 on the front side is engaged with the recess 4a of the cam 4 with a slight gap. Further, the front end portions of the sliding plates 5 are inserted into recesses formed in the rear end surfaces of the pistons 2, and the sliding plates 5 and the pistons 2 are connected by pins 8 penetrating both sliding plates 5 up and down. And are connected.

  The piston 2 divides the oil chamber into a first oil chamber 15 on the main shaft 3 side, that is, the rear side, and a second oil chamber 16 on the opposite side to the main shaft 3, that is, on the front side. It moves to the rear side and moves to the second oil chamber 16 side, that is, the front side during the closing operation. The piston 2 includes a cylindrical outer cylinder 20 and a cylindrical inner cylinder 21 that is press-fitted and integrated inside the outer cylinder 20. The inner cylinder 21 is formed with a small diameter portion on the front side and a large diameter portion on the rear side, and the inside of the large diameter portion becomes the concave portion, and the sliding plate 5 is inserted therein.

  A check valve 22 is provided inside the small diameter portion of the inner cylinder 21. Specifically, as shown in a cross-sectional view in FIG. 6, a cylindrical valve seat 23 is inserted and fixed inside the small diameter portion of the inner cylinder 21, and the inner side of the valve seat 23 is reversely movable in the axial direction. A stop valve 22 is inserted. In FIG. 6, an adjusting shaft and a spring receiving member 40 which will be described later are omitted. FIG. 5 shows only the valve seat 23 and the check valve 22 in a sectional view. During the closing operation in which the piston 2 moves to the front side, the check valve 22 receives the hydraulic pressure on the second oil chamber 16 side and moves to the rear side relative to the valve seat 23 as shown in FIG. The O-ring 24 is in contact with the front end surface of the valve seat 23 and the side hole 25 is closed. At the time of the opening operation in which the piston 2 moves to the rear side, the check valve 22 receives the hydraulic pressure on the first oil chamber 15 side and moves to the front side relative to the valve seat 23 as shown in FIG. Yes, the stopper pin 26 of the check valve 22 comes into contact with the rear end surface of the valve seat 23, the O-ring 24 is separated from the front end surface of the valve seat 23 to the front side, and the side hole 25 is opened. The hydraulic oil on the first oil chamber 15 side can flow from the inner passage 27 through the side hole 25 to the second oil chamber 16 side. That is, the inner passage 27 and the side hole 25 of the check valve 22 constitute a communication hole that connects the first oil chamber 15 and the second oil chamber 16. The inner passage 27 of the check valve 22 opens not only to the rear end face of the check valve 22 but also to the front end face. The front opening is always urged forward by a spring 28. When the safety valve 29 is closed and the door is forcibly closed by an external force and the hydraulic pressure on the second oil chamber 16 side suddenly increases, the safety valve 29 is moved by the increased hydraulic pressure of the second oil chamber 16. The spring 28 is compressed against the biasing force of the spring 28 and moved rearward to open the front opening of the inner passage 27.

  As shown in FIG. 6, flow control channels 17 and 18 are formed in both side walls of the main body housing 1, respectively. These flow control channels 17 and 18 communicate with the first oil chamber 15 and the second oil chamber 16 so as to bypass the piston 2. FIG. 6 shows a state in which the door is fully closed. In this state, the first flow control channel 17 in one side wall portion shown on the upper side in FIG. Both the opening on the side and the opening on the second oil chamber 16 side are not blocked by the piston 2 and are in the open state. Conversely, the second flow rate control flow path 18 in the other side wall portion shown on the lower side in FIG. 6 is in the open state on the first oil chamber 15 side, but the second oil chamber 16 is open. The opening on the side is in a closed state closed by the piston 2. When the door starts to open and the piston 2 starts to move to the rear side, the check valve 22 opens and the hydraulic oil moves from the first oil chamber 15 to the second oil chamber 16 through the communication hole of the piston 2. In both cases, the hydraulic oil also flows from the first flow control channel 17 to the second oil chamber 16 until the opening on the first oil chamber 15 side of the first flow control channel 17 is closed by the piston 2. Flowing. Thereafter, when it is time to close the opening of the first flow rate control flow path 17 on the first oil chamber 15 side, the opening of the second flow rate control flow path 18 on the second oil chamber 16 side opens. The hydraulic oil now flows from the second flow control channel 18 to the second oil chamber 16. The reverse is the case when the door is closed, and the check valve 22 is closed so that the hydraulic oil cannot pass through the communication hole of the piston 2, but the second flow rate control flow path 18 is passed from the beginning to the middle of the door closing operation. When hydraulic oil flows through the first oil chamber 15 and the piston 2 closes the second flow control channel 18 in the later stage of the closing operation, the first flow control channel 17 moves to the first oil chamber 15. Flowing. These flow rate control channels 17 and 18 are provided with an adjustment valve (not shown) for controlling the flow rate of hydraulic oil flowing therethrough.

  A cylindrical main connecting rod 30 is connected to the piston 2. The main connecting rod 30 is connected to the front side of the piston 2 so that its axis is the same as the axis of the piston 2, and extends from the piston 2 to the front side. A male thread portion is formed in the small diameter portion of the inner cylindrical body 21 of the piston 2, and an annular gap is formed between the small diameter portion and the outer cylindrical body 20. The rear end portion of the rod 30 is screwed to the small diameter portion of the inner cylinder 21 of the piston 2. Accordingly, the check valve 22 of the piston 2 is located inside the rear end portion of the main connecting rod 30.

  A cylindrical auxiliary connecting rod 31 is connected to the front side of the main connecting rod 30. The sub-connecting rod 31 is screwed to the female thread portion on the inner peripheral surface of the front end portion of the main connecting rod 30. An annular flange portion 32 is formed at the front end portion of the sub-connecting rod 31, and the rear end surface of the flange portion 32 constitutes a movable spring seat. Further, the main connecting rod 30 and the sub connecting rod 31 constitute a connecting rod that connects the piston 2 and the movable spring receiving seat.

  On the front side of the piston 2, a spring receiving member 40 is disposed at a position spaced apart from the piston 2 in the closed state by a predetermined distance, and on the front side of the spring receiving member 40, a return spring 50 including a coil spring is disposed. The spring receiving member 40 has a disk shape having a through hole in the center, and the main connecting rod 30 passes through the inside thereof. The front end surface of the spring receiving member 40 constitutes a fixed spring receiving seat. That is, the return spring 50 is interposed between the spring receiving member 40 and the flange portion 32 of the sub-connecting rod 31, and the connecting rod is inserted inside the return spring 50. Accordingly, the spring receiving member 40 is always pressed and urged rearward by the return spring 50, and the sub connecting rod 31 is pressed and urged forward, and the urging force acting on the sub connecting rod 31 is applied from the main connecting rod 30 to the piston. 2, transmitted to the sliding plate 5 and the cam 4. Therefore, during the opening operation, the piston 2 and the connecting rod move rearward as shown in FIGS. 3 and 4 to compress the return spring 50 and the return spring 50 accumulates the closing force. During the closing operation, the piston 2 and the connecting rod are moved forward by the closing force of the return spring 50.

  The spring receiving member 40 is a separate member from the main body housing 1 and is configured to be slidable in the axial direction with respect to the main body housing 1. 1 to 4 show a state in which the spring receiving member 40 is located at the rearmost side, and the spring receiving member 40 is brought into contact with the stepped portion 41 on the inner wall surface of the main body housing 1 so that the spring receiving member 40 abuts the spring. The rearward movement of the receiving member 40 is prevented.

  Next, a spring force adjusting mechanism that changes the position of the spring receiving member 40 by an operation from the outside of the main body housing 1 in order to adjust the spring force of the return spring 50 will be described. 1 to 4 show a state in which the spring receiving member 40 is located on the rearmost side and the spring force of the return spring 50 is the smallest. FIGS. 7 to 10 show that the spring receiving member 40 is located on the most front side. Thus, the amount of compression of the return spring 50 in the closed state is the maximum and the spring force is the largest.

  The spring force adjustment mechanism includes an adjustment shaft and a linkage pin 60 as a linkage member. The adjustment shaft is coaxial with the piston 2, the return spring 50, and the connecting rod, and includes a first adjustment shaft 61 and a second adjustment shaft 62. The first adjustment shaft 61 passes through the center of the horizontal cap 12 in the axial direction, and a front end portion 61a of the first adjustment shaft 61 protrudes forward from the horizontal cap 12. The front end portion 61a of the first adjustment shaft 61 protruding from the lateral cap 12 is an operation portion, and this portion is rotated. Further, the first adjustment shaft 61 is inserted inside the connecting rod, a male screw portion is formed on the outer peripheral surface of the rear end portion, and a female screw formed on the inner peripheral surface of the front end portion of the second adjustment shaft 62. Screwed into the part. The entire second adjusting shaft 62 is inserted inside the connecting rod, specifically, inside the main connecting rod 30, and is slid in the axial direction by the screw feed mechanism by rotating the first adjusting shaft 61.

  A linkage pin 60 is attached and fixed to the rear portion of the second adjustment shaft 62. The linkage pin 60 has an axis in the vertical direction and penetrates the second adjustment shaft 62 in the vertical direction. Long hole-shaped horizontal holes 63 are formed in the upper and lower portions of the peripheral wall of the main connecting rod 30, and the upper and lower ends of the linkage pins 60 are inserted through the horizontal holes 63. And extending downward. A pair of upper and lower engaging recesses 42 are formed on the inner peripheral surface of the spring receiving member 40, and the upper end portion and the lower end portion of the linkage pin 60 are engaged with the engaging recess portion 42, respectively. A flat surface 60a is formed on the front portion of each of the upper end portion and the lower end portion of the linkage pin 60, and a corresponding flat surface is also provided on the front portion of the wall surface of the engagement recess 42 of the spring receiving member 40. Accordingly, the flat surfaces of the link pin 60 and the spring receiving member 40 are in contact with each other, and the flat surface 60a of the link pin 60 presses the flat surface of the spring receiving member 40 forward, and the spring is pressed. The receiving member 40 is moved in the axial direction. As described above, in the present embodiment, the front end portion 61a of the first adjustment shaft 61 protruding from the lateral cap 12 is an operation unit that is rotated, and the rotation of the first adjustment shaft 61 is second adjusted by the screw feed mechanism. The movement of the shaft 62 is converted into the movement in the axial direction, and is transmitted to the spring receiving member 40 by the linkage pin 60 through the lateral hole 63 of the main connecting rod 30. In the present embodiment, the first adjustment shaft 61, the second adjustment shaft 62, and the linkage pin 60 constitute a transmission unit that transmits the movement of the operation unit to the spring receiving member 40.

  A recess 62a is formed in the rear end surface of the second adjustment shaft 62. When the piston 2 is closest to the spring receiving member 40 as shown in FIGS. A predetermined amount can be inserted into the recess 62a of the two adjustment shafts 62.

  In the floor hinge configured as described above, the piston 2 moves toward the first oil chamber 15 when the door is opened, and moves toward the second oil chamber 16 when the door is closed. The oil pressure on the oil chamber 15 side does not increase. Therefore, it is possible to suppress oil leakage from the location of the bearing 13 of the main shaft 3 caused by the pressure increase in the first oil chamber 15.

  Since the front end portion 61a of the first adjustment shaft 61 protrudes from the lateral cap 12, the position of the spring receiving member 40 is easily changed in the axial direction by rotating the front end portion 61a of the first adjustment shaft 61. The spring force of the return spring 50 can be easily adjusted from the outside of the main body housing 1. In particular, since the front end portion 61a of the first adjustment shaft 61 protruding from the lateral cap 12 can be operated as an operation portion, the main body housing 1 can be prevented from being enlarged, and the spring force adjustment operation is easy.

  Moreover, since the connecting rod is cylindrical and the first adjusting shaft 61 and the second adjusting shaft 62 are inserted inside the connecting rod, the movement of the operating portion can be transmitted using the inner space of the connecting rod. The transmission unit can be configured without making the housing 1 thicker in the vertical direction or widening the left and right sides. Then, a pair of the horizontal holes 63 are formed to face the connecting rod 180 degrees, and the linkage pins 60 protrude radially outward from the horizontal holes 63. Therefore, the spring receiving member 40 is smoothly moved to return the spring. 50 can be compressed. Moreover, since the spring receiving member 40 moves in the axial direction without rotating, a sliding noise may be generated between the returning spring 50 and the spring receiving member 40 when adjusting the spring force of the returning spring 50. Absent. That is, if the spring receiving member 40 is configured to rotate together with the adjustment shaft, the spring receiving member 40 slides while rotating in the circumferential direction with respect to the return spring 50. Since the receiving member 40 is configured to move in the axial direction, it is possible to prevent the generation of sliding noise with the return spring 50 and to adjust smoothly.

  On the other hand, since the piston 2 is located behind the spring receiving member 40, that is, on the main shaft 3 side, the adjustment shaft does not penetrate the piston 2. Accordingly, the spring force adjustment mechanism can be easily configured, the check valve 22 of the piston 2 can be easily arranged, and the piston 2 can be prevented from being elongated in the axial direction. , 18 can be easily arranged. Further, since the sliding plate 5 is inserted into the rear portion of the piston 2 for a predetermined length, the overall length dimension in the axial direction of the main body housing 1 is also possible as a configuration in which the piston 2 is disposed on the rear side of the spring receiving member 40. Can be suppressed.

  Since the connecting rod is cylindrical up to the rear end, and the check valve 22 is located inside the rear end, the opening of the piston 2 from the communication hole of the piston 2 to the second oil chamber 16 side. The moved hydraulic oil can pass through the inside of the connecting rod, and can easily move from the lateral hole 63 of the connecting rod to the outside of the connecting rod. Further, in the configuration in which the check valve 22 is positioned outside the connecting rod, the diameter of the piston 2 is increased. However, by arranging the check valve 22 inside the connecting rod as a cylinder, the size of the piston 2 is increased. And increase in size of the main body housing 1 can be prevented.

  In the present embodiment, the linkage pin 60 is configured to penetrate the connecting rod in the vertical direction. However, the linkage pin 60 may be configured to penetrate in the horizontal direction, and any direction may be used. 60 is preferably configured to penetrate the connecting rod in the radial direction. Moreover, the structure which the cooperation pin 60 is located in the back side of the spring receiving member 40 may be sufficient. However, when the linkage pin 60 is engaged with the spring receiving member 40 from the inside in the radial direction as described above, the dimension in the front-rear direction is shortened compared to the configuration in which the linkage pin 60 is arranged on the rear side of the spring receiving member 40. can do.

  Further, although the heart-shaped cam 4 is used as the piston drive unit, a rack and pinion configuration may be used. However, in the case of a floor hinge, it is preferable to use the cam 4 because a large driving force is required.

  Although the check valve 22 is arranged at the center of the piston 2, it may be arranged outside the connecting rod. Moreover, although the connecting rod was made into the cylinder shape over the full length, it is good also considering the rear part as a solid shape and making only the front side into a cylinder shape. Furthermore, the connecting rod may be configured integrally with the piston 2 as one member, the main connecting rod 30 and the piston 2 may be configured as one member, and the sub-connecting rod 31 may be configured as another member.

  Further, the piston 2 may be arranged on the front side of the spring receiving member 40. That is, the rear end surface of the piston 2 may be a movable spring receiving seat, and the return spring 50 may be interposed between the piston 2 and the spring receiving member 40.

  Furthermore, although the protruding portion of the adjustment shaft that protrudes from the lateral cap 12 is used as the operating portion, a configuration in which it is simply exposed without protruding from the lateral cap 12 may be employed. The operation is preferably a rotation operation, but is not limited thereto. For example, an operation for moving the operation unit in the axial direction may be used.

  Moreover, although the case of a floor hinge was demonstrated, it is applicable to the various door closer attached to the upper part of a door, the inside, or a door frame.

1 Body housing 2 Piston 3 Spindle 4 Cam (piston drive part)
4a Concave part 5 Sliding plate 6 Roller 7 Roller 8 Pin 10 Main part 11 Upper cap 12 Horizontal cap 13 Bearing 14 Bearing 15 First oil chamber 16 Second oil chamber 17 First flow control flow path 18 Second flow control flow Path 20 Outer cylinder 21 Inner cylinder 22 Check valve 23 Valve seat 24 O-ring 25 Side hole (communication hole)
26 Stopper pin 27 Inner passage (communication hole)
28 Spring 29 Safety valve 30 Main connecting rod (connecting rod)
31 Sub connecting rod (connecting rod)
32 Flange part 40 Spring receiving member 41 Step part 42 Engaging recess 50 Returning spring 60 Cooperation pin (Cooperation member, transmission part)
60a Flat surface 61 First adjustment shaft (transmission part)
61a Front end (operation part)
62 Second adjustment shaft (transmission part)
62a Recess 63 Horizontal hole

Claims (3)

A main shaft that rotates as the door opens and closes, a main body housing that supports the main shaft and is filled with hydraulic oil, and a first oil chamber and a main shaft on the main shaft side of the oil chamber. It is divided into the second oil chamber on the opposite side, and it moves to the first oil chamber side during the opening operation, and the piston moving to the second oil chamber side during the closing operation, and the rotation of the main shaft is converted into linear motion. A piston drive unit that drives the piston, and a return spring that is located on the same line as the piston and interposed between a fixed spring receiving seat near the main shaft and a movable spring receiving seat far from the main shaft In the door closer in which the return spring compresses and accumulates the closing force by moving the movable spring receiving seat closer to the fixed spring receiving seat during the opening operation,
A spring receiving member having a fixed-side spring receiving seat is configured such that the position of the spring receiving member can be changed in the axial direction of the piston with respect to the main body housing, and the position of the spring receiving member is changed by an operation from the outside of the main body housing. It has a spring force adjustment mechanism that adjusts the spring force of
The piston is located between the spring receiving member and the main shaft, and the piston and the movable spring receiving seat are connected by a connecting rod penetrating the spring receiving member, and the connecting rod opens at the end opposite to the piston. The spring force adjusting mechanism includes an operating portion provided at an end portion of the main body housing on the second oil chamber side, and movement of the operating portion via the inside of the cylindrical portion of the connecting rod. And a transmission part for transmitting the spring receiving member to the axial direction of the piston . A horizontal hole is formed in the peripheral wall of the cylindrical portion of the connecting rod, and the spring force adjusting mechanism passes through the end of the main body housing on the second oil chamber side and passes through the inside of the cylindrical portion of the connecting rod. If, door closer according to claim 1, characterized in that a linkage member to link the adjusting shaft and the spring receiving member through the transverse bore of the connecting rod. The connecting rod is cylindrical over its entire length, and a communication hole with a check valve that connects the first oil chamber and the second oil chamber is formed at the center of the piston, and the end of the connecting rod on the piston side door closer of claim 1 or 2, wherein the communicating hole is located inside.

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