JP2002081261A - Door closer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure sufficient stop holding power in a door closer. SOLUTION: This door closer has a hydraulic shock absorbing means 3 connected to rotary shafts 2 and 32 via a transmission device RP so as to apply resistance force against the rotary shafts 2 and 32 and the rotation, a closer body C attached to either one of a door D and a door frame F, a link mechanism L for connecting the rotary shafts 2 and 32 to either the other of the door D and the door frame F, and a stopper mechanism S for holding the door D in a prescribed opening position. The stopper mechanism S is composed of cams 8, 18 and 38 arranged on the rotary shafts 2 and 32 integrally rotatable with these rotary shafts, abutting members 9, 19 and 39 capable of abutting to the cams 8, 18 and 38, and a pressing means 10 for elastically pressing the abutting members 9, 19 and 39 to the cams 8, 18 and 38.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a door closer.

[0002]

2. Description of the Related Art Generally, a door closer has a rotating shaft and a fluid pressure buffer connected to the rotating shaft via a rack and pinion so as to impart a resistance to the rotation thereof. The door includes a closer body attached to one of the doors, a link mechanism for connecting the rotating shaft to the other of the door and the door frame, and a stopper mechanism for holding the door at a predetermined open position.

[0003] Japanese Patent Publication No. 2-45749 discloses a door closer having a closer body incorporating a stopper mechanism of this type (hereinafter referred to as "prior art 1").
The stopper mechanism of the prior art 1 basically applies an intermittent gear, and forms a rack on a part of a piston, and has teeth formed on a part of an outer periphery of a pinion that can mesh with the rack. An unremoved rack relief portion is formed, and rotation of the pinion is stopped by pressure contact between the tooth at the end of the rack and the rack relief portion of the pinion, so that the door is held at a predetermined open position.

However, in the prior art 1, it is difficult to secure a sufficient stop holding force due to the above-described structure, and it is difficult for a user to distinguish between a stopper operating state and a stopper releasing state. , Tend to cause inconvenience. Furthermore, in order to realize a proper pressure contact structure between the tooth at the end of the rack and the rack relief portion of the pinion, a high degree of processing accuracy is required, and extremely high hardness is required at the pressure contact portion. Heat treatment was required.

[0005] As means for solving the above-mentioned problem of the prior art 1, Japanese Utility Model Publication No. 1-30526 discloses a door closer provided with a stopper mechanism outside the closer body (hereinafter referred to as "prior art"). 2 ”).

[0006]

However, in the door closer of the prior art 2, the structure of the stopper mechanism is complicated, the number of parts is large, and the cost increases.

The door closer disclosed in Japanese Patent Application Laid-Open No. 7-217307 uses only a pneumatic cylinder without using a rack and pinion. Therefore, a smooth and stable power transmission mechanism using the rack and pinion is used. And the closer body tends to be large.

SUMMARY OF THE INVENTION An object of the present invention is to provide a door closer having a simple structure and a low manufacturing cost, which can ensure a sufficient stop holding force, allow a user to reliably distinguish between a stopper operating state and a stopper releasing state. To provide.

[0009]

In order to solve the above-mentioned problems, the present invention according to claim 1 provides a rotating shaft (2, 32) and a resistance to rotation of the rotating shaft (2, 32). And a fluid pressure buffer means (3) connected to the rotating shaft (2, 32) via a transmission (RP).
And a closer body (C) attached to one of the door frame (F) and the other of the door (D) and the door frame (F) for connecting the rotating shaft (2, 32) to the other of the door (D) and the door frame (F). In a door closer having a link mechanism (L) and a stopper mechanism (S) for holding the door (D) at a predetermined open position, the stopper mechanism (S)
A cam (8, 18, 38) provided on the rotating shaft (2, 32) so as to rotate integrally therewith; and a contact member (9) capable of contacting the cam (8, 18, 38). , 19,
39) and pressing means (1) for elastically pressing the contact members (9, 19, 39) against the cams (8, 18, 38).
0).

According to a second aspect of the present invention, in the door closer of the first aspect, the cam (8, 18, 38) has at least one recess (8a, 18a, 38a),
The contact members (9, 19, 39) are provided with the concave portions (8a,
18a, 38a) and rollers (13, 23, 4,
It is characterized by having 3).

According to a third aspect of the present invention, in the door closer of the first aspect, the cam (38) has at least one projection (38b), and the contact member (39).
Has a concave portion (43a) engageable with the convex portion (38b).

According to a fourth aspect of the present invention, in the door closer according to any one of the first to third aspects, the contact member (9, 39) is slidable in a length direction of the closer body (C). There is a feature.

According to a fifth aspect of the present invention, in the door closer according to any one of the first to fourth aspects, a stopper operating state in which the contact member (9) can contact the cam (8). Switching means (1) for selectively switching to any of a stopper release state in which the cam (8) cannot contact the cam (8).
2) is provided.

According to a sixth aspect of the present invention, the rotating shaft (2) is connected to the rotating shaft (2) via a transmission (RP) so as to impart a resistance to the rotation of the rotating shaft (2). And a closer body (C) having a fluid pressure buffer means (3) attached to one of the door (D) and the door frame (F), and the rotating shaft (2) being connected to the door (D) and the door (D). A door mechanism including a link mechanism (L) for connecting to the other one of the door frames (F) and a stopper mechanism (S) for holding the door (D) at a predetermined open position; (S) is a concave portion (8) of a push rod (5) provided with the rack (5a) at one end.
a, 8b), an engaging member (44) capable of abutting on the recesses (8a, 8b), and a pressing means (elastically pressing the engaging member (44) against the recesses (8a, 8b)). 10).

According to a seventh aspect of the present invention, in the door closer according to the sixth aspect, an adjusting means (50) for adjusting the position of the engaging member (44) capable of abutting on the recesses (8a, 8b). Is provided.

[0016]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a door closer according to a first embodiment of the present invention will be described in detail with reference to the accompanying drawings.

The door closer according to the first embodiment of the present invention is, as apparent from FIGS.
, Link mechanism L, stopper mechanism S, switching means 12
It is composed of

As shown in FIG. 1, the closer body C is fixed to a door D which is attached to a door frame F via a hinge H so as to be openable and closable. The casing 1 of the closer body C has a cylinder bore 1a extending in the length direction thereof,
It has a rack and pinion storage chamber 1b formed so as to communicate with it. The open end of the cylinder bore 1a is closed by a plug 1x, and the open end of the rack and pinion storage chamber 1b is closed by another plug 1y.

A rotary shaft 2 is rotatably supported on the rack and pinion storage chamber 1b side of the casing 1 via a pinion bush 1c and a bearing 1d (see FIG. 5). Also, an O-ring 1e as a sealing member is provided to prevent pressure oil from flowing out.

On the other hand, a piston 4 is arranged in the cylinder bore 1a of the casing 1 so as to be reciprocally slidable. It is divided into a room 1ay. The first chamber 1ax and the second chamber 1ay are communicated via a communication path (not shown), and a speed control valve (not shown) is provided in this communication path.

The piston 4 incorporates a one-way valve 4a. The one-way valve 4a allows the pressure oil to move from the second chamber 1ay through the one-way valve 4a to the first chamber 1ax, but allows the pressure oil to move from the first chamber 1ax through the one-way valve 4a. The movement to the two chambers 1ay is prevented. Therefore, when the piston 4 moves to the right in FIG. 4, the pressure oil opens the one-way valve 4a and moves from the second chamber 1ay to the first chamber 1a.
It can move to x. Therefore, the pressure oil does not cause a large resistance to the movement of the piston 4 in this direction. On the other hand, when the piston 4 moves to the left in FIG. 4, the one-way valve 4a is closed, and the movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is provided by the above-described speed adjusting valve. This is performed through the communication path provided. Therefore, depending on the degree of throttle of the speed control valve, the pressure oil generates a large resistance to the movement of the piston 4 in this direction.

A push rod 5 is provided in the cylinder bore 1a.
And one end thereof is connected to the piston 4 via the piston pin 6.

As described above, the communication passage provided with the piston 4, the push rod 5, and the speed adjusting valve incorporated in the cylinder bore 1a constitutes the fluid pressure buffering means 3.

The fluid pressure buffering means 3 is connected to the above-mentioned rotating shaft 2 via a rack and pinion RP as a transmission. That is, a rack 5 a is formed at the tip of the push rod 5, while a pinion 7 is attached to the rotating shaft 2 so as to rotate integrally. The rack 5a is engaged with the pinion 7.

As best understood from FIGS. 1 and 2, the link mechanism L comprises a main arm L1 and an adjust arm L2 having one end rotatably connected to one end of the main arm L1. . Main arm L1
Is attached to the above-described rotation shaft 2 of the closer body C so as to rotate integrally therewith. The other end of the adjusting arm L2 is rotatably connected to a bracket B fixed to the door frame F, as shown in FIGS.

Therefore, the rotation of the rotating shaft 2 accompanying the opening and closing of the door D is transmitted to the fluid pressure buffering means 3 via the rack and pinion RP. That is, as the door D opens and closes, the piston 4 slides in the cylinder bore 1a. When the piston 4 slides, the pressure oil applies a predetermined resistance to the piston 4 according to the moving direction, as described above.
This resistance produces a buffering effect when opening and closing the door D. When the door D is opened, the piston 4 moves to the right in FIG. 4, while when the door D is closed, the piston 4 moves to the left in FIG.

The stopper mechanism S comprises a pair of cams 8, a contact member 9, and a pressing means 10. Each of the pair of cams 8 has a shape shown in FIG. 9, a spline groove 8 b corresponding to the outer diameter of the pinion 7 is formed substantially at the center, and a single recess 8 a is formed on the outer periphery. ing.
The cams 8 are arranged so as to face each other, and are connected to each other via a cam support shaft 14 (see FIG. 11). These spline grooves 8b of the cam 8
Inside, a pinion 7 is inserted. Therefore, the cam 8
Can rotate integrally with the pinion 7.

The contact member 9 is formed as a substantially cylindrical slider having a through hole 9a, and the rack 5a in the cylinder bore 1a of the closer body C is inserted into the through hole 9a so as to be inserted into the cylinder bore 1a. It is slidably arranged (see FIG. 4). The roller 13 is provided at the contact member, that is, at the position on the side end of the slider 9 (upward and right side in FIG. 8). The roller 13 is
The cam 8 can be engaged with the recess 8a. A guide groove 9b is formed on the side surface of the slider 9, as shown in FIGS. A stopper screw 11 as a guide member extending toward the slider 9 is screwed into the casing 1 of the closer main body C, and the tip of the stopper screw 11 is inserted into the guide groove 9 b of the slider 9. Therefore,
The stopper screw 11 regulates the rotation of the slider 9 about its center axis and determines the sliding limit position of the slider 9 toward the cam 8.

The pressing means 10 is composed of a compression coil spring, and is arranged between the piston 4 and the slider 9 in the cylinder bore 1a as best understood from FIG. I'm going. At the same time, the coil spring 10 urges the piston 4 toward the plug 1x, and constantly applies an elastic force acting on the door D in the closing direction.

As shown in FIG. 6, the switching means 12 is composed of a pair of screws 12a and 12b which are obliquely screwed into the front wall of the casing 1 of the closer main body C. The tips of these screws 12a, 12b are respectively formed in stopper grooves 9c, 9d formed on the front side surface of the slider 9.
Can be engaged.

Next, the operation of the door closer will be described. First, when the stopper mechanism S is maintained in the stopper operating state, the switching means 12, that is, the screws 12a, 12
b are rotated counterclockwise, and the roller 13 of the slider 9 is placed in a state where the roller 13 can contact the cam 8.

When the door D is opened from the closed state, the rotating shaft 2 rotates because it is connected to the door frame F via the link mechanism L. The rotational force of the rotating shaft 2 accompanying the opening of the door D is transmitted to the fluid pressure buffering means 3 via the rack and pinion RP. That is, with the opening of the door D, the piston 4 slides in the cylinder bore 1a to the right in FIG. On this occasion,
Due to the operation of the one-way valve 4a, the pressure oil does not cause a large resistance to the movement of the piston 4. Therefore, the door D can be opened with a minimum force slightly larger than the elastic force of the coil spring 10.

When the door D is opened and the rotating shaft 2 rotates, the cam 8 rotates at the same time. At this time, the roller 13 of the slider 9 is pressed against the outer peripheral surface of the cam 8 by the coil spring 10. In this state, when the cam 8 rotates to a predetermined rotation angle, the roller 13 of the slider 9
Engages with the concave portion 8a of the cam 8 (see FIG. 11B). Therefore, the rotation of the cam 8 is held in a stopped state.
As a result, the rotation of the rotating shaft 2 is prevented, and as a result, the door D is held at the predetermined open position.

When the door D is further opened from such a state, the cam 8 further rotates, the roller 13 of the slider 9 comes out of the concave portion 8a of the cam 8, and the engagement is released.
The door D is placed in a state where it can be opened up to the maximum open position (see FIG. 11C).

When the force applied to the door D is released at the maximum open position of the door D, the piston 4 moves to the left in FIG.
Thus, the force applied to the piston 4 by the coil spring 10 is transmitted to the rotating shaft 2 via the rack and pinion RP, and therefore, the door D rotates in the direction automatically closed by the action of the coil spring 10. . When the piston 4 moves to the left in FIG. 4 as described above, the one-way valve 4a is shut off, and the movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is provided with a speed adjusting valve. It is performed through a communication passage. Therefore, depending on the degree of throttle of the speed control valve, the pressure oil generates a large resistance to the movement of the piston 4 in this direction. As a result, the speed with which the door D rotates in the closing direction is significantly reduced.

At such a remarkably reduced speed, the door D
When the rotation angle reaches a predetermined angle, the roller 13 of the slider 9 engages with the concave portion 8a of the cam 8 again (see FIG. 11B). Therefore, the rotation of the cam 8 is held in a stopped state. As a result, the rotation of the rotating shaft 2 is prevented, and as a result, the door D is again held at the predetermined open position.

When the door D is held in the open position and a force is applied to the door D in a direction to close the door D, the slider 9 moves the elasticity of the coil spring 10 with the rotation of the cam 8. 4 against the force, the roller 13 of the slider 9 and the concave portion 8a of the cam 8 are disengaged. Thereafter, the piston 4 moves to the left in FIG.
As described above, when the piston 4 moves to the left in FIG. 4, the one-way valve 4a is closed, and the movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is as follows.
This is performed via a communication passage provided with a speed control valve. Therefore, depending on the degree of throttle of the speed control valve, the pressure oil generates a large resistance to the movement of the piston 4 in this direction. As a result, the door D is automatically closed at a significantly reduced speed.

To maintain the stopper mechanism S in the stopper released state, the switching means 12, ie, the screws 12a, 12
b is rotated clockwise, and the slider 9 is moved toward the piston 4 to a position where the roller 13 cannot contact the cam 8.

When such operation of the switching means 12 is performed,
The roller 13 of the slider 9 does not engage with the concave portion 8a of the cam 8. Therefore, the door D is not held at the above-described predetermined open position.

In the above-described first embodiment, the stop holding force of the door D can be adjusted by operating the switching means 12. That is, if the tightening of the screws 12a and 12b as the switching means 12 is adjusted so that the roller 13 of the slider 9 can be incompletely engaged with the concave portion 8a of the cam 8, they are completely engaged. The engagement can be released with a smaller force than in the state.

In the above-described first embodiment, as shown in FIG. 9, a pair of cams 8 having a single concave portion 8a are used. However, as shown in FIG.
A pair of cams 18 having a, 18a and a spline groove 18b may be used. If it is necessary to hold the door D at a plurality of predetermined open positions, the number of recesses may be increased according to the number.

In consideration of the smooth contact between the slider 9 and the cam 8, it is desirable that the slider 9 has the roller 13 as described above. A curved surface instead of the roller 13 may be provided.

In the first embodiment, the switching means 12
Although the description has been made of a pair of screws 12a and 12b arranged obliquely with respect to the sliding direction of the slider 9, it may be composed of only a single screw. In this case, if the slider 9 can be moved to the piston 4 side to a position where the roller 13 cannot contact the cam 8, the screw mounting position is arbitrary. For example, the sliding direction of the slider 9 to the plug 1y May be screwed in the same direction.

Further, the switching means 12 does not need to be composed of the screws 12a and 12b as described above, and the stopper screw 11 shown in FIG. 4 can also have a function as the switching means. For example, it is possible to provide a cam member at the tip of the stopper screw 11 and selectively switch the slider 9 between a stopper operating state and a stopper releasing state according to the rotational position of the stopper screw 11.
Further, the stopper screw 11 itself may be moved with respect to the casing 1 so as to be selectively held in the above-described two states without providing such a cam member on the stopper screw 11.

In the first embodiment described above, the stopper mechanism S is of a built-in type, that is, the cam 8 and the slider 9
Is arranged in the cylinder bore 1a. Therefore, the appearance of the door closer can be maintained beautifully. Moreover,
The cam 8 and the slider 9 operate in the working oil filled in the cylinder bore 1a. Therefore, excellent lubrication characteristics are obtained, and long-term durability is realized. Of course, if there is no request for such an effect, the stopper mechanism S
May be configured as an exterior type.

Next, a door closer according to a second embodiment of the present invention will be described in detail with reference to FIGS.

The door closer according to the second embodiment is the same as the door closer according to the first embodiment except that the door closer has a different form of contact member 19. Therefore, the same components are denoted by the same reference numerals, and description thereof will be omitted.

In the first embodiment, the contact member is configured as a slider 9 which can slide in the longitudinal direction of the closer body C. In the second embodiment, the support shaft 2 is provided.
The lever 19 is configured to be swingable about 0.

That is, the lever 19 is disposed in the rack and pinion accommodating chamber 1b of the closer body C,
0 and is swingably supported by the casing 1. The lever 19 has a substantially L-shaped shape on the side surface as shown in FIG. 13A, and has a through hole 19a at the center as shown in FIGS. 13A and 13C. are doing. The rack 5a is inserted into the through hole 19a. The lever 19 has a first roller 2 on one side thereof.
3 and a second roller 24 on the other side. The first roller 23 can be engaged with the recess 8 a of the cam 8. The second roller 24 guides the rack 5a.

As in the first embodiment, an elastic force is applied to the lever 19 by the compression coil spring 10. That is, the end of the coil spring 10 is in contact with the end face of the lever 19 as shown in FIG.

Therefore, the coil spring 10 constantly applies an elastic force to the lever 19 to swing the lever 19 toward the cam 8. In addition, as shown in FIG.
Abuts on the step 1e of the casing 1 to determine the swing limit position of the lever 19.

The door closer according to the second embodiment is also provided with a screw (not shown) as a switching means. This screw is similar to the first embodiment,
The tip of the first roller 23 contacts the lever 19 and
May be screwed into the casing 1 so that the cam cannot be brought into contact with the concave portion 8a of the cam 8.

The operation of the door closer in the second embodiment is the same as that in the first embodiment except that the lever 19 swings. Therefore, the description is omitted.

In the second embodiment, the lever 19 is
Since it is supported by the casing 1 via the support shaft 20, there is no need to provide the stopper screw 11 as in the first embodiment.

Next, a door closer according to a third embodiment of the present invention will be described in detail with reference to FIGS.

The door closer according to the third embodiment comprises:
(1) The cam 38 is single, (2) the rotating shaft 32 and the cam 38 are integrally formed, and
(3) It is the same as the door closer according to the first embodiment except that the contact member 39 has a different shape due to the single cam 38. Therefore, the same components are denoted by the same reference numerals, and description thereof will be omitted.
In FIG. 14, reference numeral 1f denotes a mounting bracket for mounting the closer body C.

The rotation shaft 32 used in the third embodiment has a pinion gear portion 37 and a cam 38 at its center, as is clear from FIGS. 16 (a) and 16 (b).
Are integrally provided. That is, a pinion gear portion 37 is formed integrally with a half peripheral portion at the center of the rotary shaft 32, and a cam 38 is formed integrally with the remaining half peripheral portion. The cam 38 has a pair of recesses 38a, 38a formed on its outer circumference at intervals in the circumferential direction.
The end of the rotating shaft 32 is formed in a tapered shape in order to secure a strong connection with the main arm.

As shown in FIG. 18, the contact member 39 is formed as a substantially cylindrical slider having a through hole 39a, and inserts the rack 5a in the cylinder bore 1a of the closer body C into the through hole 39a. And slidably disposed in the cylinder bore 1a (FIG. 1).
4). A roller 43 is provided at the contact member, that is, at a position on the side end of the slider 39. Roller 43
Can be engaged with the recess 38a of the cam 38 described above.
18 (a) and FIG.
As shown in FIG. 8B, a guide groove 39b is formed. A slider 39 is provided on the casing 1 of the closer body C.
Stopper screw 1 as a guide member extending toward the side
1 is screwed in, and its tip is inserted into the guide groove 39b of the slider 39. Therefore, the stopper screw 1
Numeral 1 regulates the rotation of the slider 39 about its central axis and determines the sliding limit position of the slider 39 toward the cam 38. In such a state that the roller 43 is located at the sliding limit position, the roller 43 of the slider 39 does not contact the pinion gear portion 37 but can contact the cam 38.

In the first embodiment, the rollers 13 of the slider 9 are driven by the pair of cams 8, 8 which are spaced from each other.
8 have a length longer than the distance between them. As a result, on the side surface of the slider 9, the roller 13 projects outside the slider body. Therefore, it is necessary to perform special processing for the roller 13 on the portion of the housing 1 on the side of the stopper screw 11 in the cylinder bore 1a. Meanwhile, the third
In the embodiment, since the single cam 38 is used, the length of the roller 43 of the slider 39 can be significantly reduced. As a result, it is possible to prevent the roller 43 from protruding outward from the slider main body on the side surface of the slider 39. In other words, the side surface shape of the slider 39 can be made substantially a perfect circle. Therefore, it is not necessary to perform special processing for the roller 43 on the portion of the cylinder bore 1a of the housing 1 on the stopper screw 11 side.

The door closer according to the third embodiment is also
A switching means (not shown) similar to that of the first embodiment is provided, and the switching operation and the effect provided thereby are the same. Therefore, these descriptions are omitted,
Only the operation of the door closer when the stopper mechanism S is maintained in the stopper operating state will be described below.

When the door (not shown) is opened from the closed state, the rotating shaft 32 is caused by the fact that it is connected to the door frame (not shown) via a link mechanism (not shown). And rotate. The rotational force of the rotating shaft 32 accompanying the opening of the door is transmitted to the fluid pressure buffering means 3 via the rack and pinion RP. That is, with the opening of the door, the piston 4 slides in the cylinder bore 1a to the right in FIG. At this time, due to the operation of the one-way valve 4a, the pressure oil does not cause a large resistance to the movement of the piston 4. Therefore, the door can be opened with a minimum force slightly larger than the elastic force of the coil spring 10.

When the door is opened and the rotating shaft 32 rotates, the cam 38 also rotates at the same time. Such a rotating shaft 32
19A, the pinion gear portion 37 is located near the roller 43 of the slider 39, as shown in FIG.
No contact with 3.

When the cam 38 rotates to a predetermined rotation angle in such a state, the roller 43 of the slider 39 comes into contact with the end of the cam 38 (see FIG. 19B). Cam 3
8 further rotates, the end of the cam 38
Is pressed to the left side in FIG. 19C against the coil spring 10. When the cam 38 further rotates, the roller 43 engages with the first concave portion 38a of the cam 38 (FIG. 20).
(A)). Therefore, the rotation of the cam 38 is kept in a stopped state. Thereby, the rotation of the rotating shaft 32 is prevented,
As a result, the door is held at the first predetermined open position.

When the door is further opened from such a state, the cam 38 further rotates, and the roller 43 of the slider 39 is rotated.
Escapes from the first concave portion 38a of the cam 38, and the engagement is released (see FIG. 20B).

The roller 43 is connected to the first concave portion 38a of the cam 38.
After the cam 38 is further rotated after having escaped from the
3 engages with the second recess 38a of the cam 38 (FIG. 20).
(C)). Therefore, the rotation of the cam 38 is kept in a stopped state. Thereby, the rotation of the rotating shaft 32 is prevented,
As a result, the door is held at the second predetermined open position.

When the cam 38 further rotates from such a state, the roller 43 of the slider 39 escapes from the second concave portion 38a of the cam 38, the engagement is released, and the door can be opened to the maximum open position of the door. Placed in state.

When the force applied to the door is released at the maximum open position of the door, the piston 4 moves to the left in FIG. Thus, the force given to the piston 4 by the coil spring 10 is transmitted to the rotating shaft 32 via the rack and pinion RP, and therefore, the door rotates in the direction automatically closed by the action of the coil spring 10. When the piston 4 moves to the left in FIG. 14 as described above, the one-way valve 4a is shut off, and the movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is provided with a speed adjusting valve. It is performed through a communication passage. Therefore, depending on the degree of throttle of the speed control valve, the pressure oil generates a large resistance to the movement of the piston 4 in this direction. As a result, the speed at which the door rotates in the direction in which it closes is significantly reduced.

When the door is rotated in the direction in which the door is closed at such a remarkably reduced speed, and the rotation angle reaches a predetermined angle, the roller 43 of the slider 39 is rotated by the cam 38.
(See FIG. 20 (c)). Therefore, the rotation of the cam 38 is kept in a stopped state. As a result, the rotation of the rotating shaft 32 is prevented, and as a result, the door is again held at the second predetermined open position.

When the door is held at the second open position and a force is applied to the door in a direction to close the door, the slider 39 moves the coil spring 10 with the rotation of the cam 38. 14, the roller 43 of the slider 39 is disengaged from the second recess 8a of the cam 38 (see FIG. 20 (b)). First recess 8a of cam 38
And the door is again held in the first open position (see FIG. 20 (a)).

Thereafter, when the door is held at the first open position and a force is applied to the door in a direction to close the door, the slider 39 is moved by the coil 14 against the elastic force of FIG.
19, the roller 43 of the slider 39 is disengaged from the first recess 8a of the cam 38 (FIG. 19).
(B)).

Thereafter, the piston 4 is moved to the coil spring 1
Due to the action of 0, it moves to the left in FIG. As described above, when the piston 4 moves to the left in FIG. 14, the one-way valve 4a is closed, and the movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is as follows.
This is performed via a communication passage provided with a speed control valve. Therefore, depending on the degree of throttle of the speed control valve, the pressure oil generates a large resistance to the movement of the piston 4 in this direction. As a result, the door closes automatically at a significantly reduced speed.

According to the third embodiment of the present invention, by integrating the pinion gear portion 37 and the cam 38 with the rotary shaft 32, the structural components can be simplified, and the side surface shape of the slider 39 can be further improved. By simplifying
Processing of the housing 1 is facilitated, and as a result, the closer body C can be made more compact.

Next, a door closer according to a fourth embodiment of the present invention will be described with reference to FIG.

The door closer according to the fourth embodiment has a third
Unlike the door closer according to the embodiment, the cam 38 has at least one convex portion 38b, and the contact member 39 is
8 has a concave portion 43a that can be engaged with the convex portion 38b.
The rotation shaft 32 and the door D are restrained at the stop stop position by the engagement of the convex portion 38b of the cam 38 with the concave portion 43a of the contact member 39. The other points are the same as those of the door closer according to the third embodiment, so that the same components are denoted by the same reference numerals and description thereof will be omitted.

Next, a door closer according to a fifth embodiment of the present invention will be described with reference to FIG.

The door closer according to the fifth embodiment has a first
The structure of the door closer and the stopper mechanism S according to the embodiment is different.

That is, the cam 8 is formed integrally with the pinion 7, and as a result, the pinion 7 is a toothless gear with no teeth at the place where the cam 8 is formed. As a result, the cam 8 can rotate integrally with the pinion 7.

The contact member 9 comes into contact with the cam 8 via a ball 44 which is a rolling member and a slide piece 45. A guide hole 46 is formed in the casing 1 so as to extend obliquely in a direction substantially tangential to the pinion 7 and the cam 8 from the side surface of the contact member 9.
And the slide piece 45 are inserted, and the ball 44 is inserted into the guide hole 4.
6 faces the pinion 7 from one opening, and slides 4
5 is fitted in a concave portion 9 c formed on the side surface of the contact member 9.

In addition, as in the case of the first embodiment, the switching means 12 composed of the screws 12a and 12b is screwed obliquely into the near side wall of the casing 1 of the closer main body C.

Next, the operation of the door closer will be described.

When the door D is opened from the closed state, the rotating shaft 2 rotates because it is connected to the door frame F via the link mechanism L. The rotational force of the rotating shaft 2 accompanying the opening of the door D is transmitted to the fluid pressure buffering means 3 via the rack and pinion RP. That is, with the opening of the door D, the piston 4 slides in the cylinder bore 1a to the right in FIG. At this time, due to the operation of the one-way valve 4a, the pressure oil does not cause a large resistance to the movement of the piston 4. Therefore, the door D can be opened with a minimum force slightly larger than the elastic force of the coil spring 10.

When the door D is opened and the rotating shaft 2 rotates, the cam 8 rotates at the same time. At this time, the ball 44 is moved by the coil spring 1 via the slider 9 and the slide piece 45.
0 presses the outer peripheral surface of the cam 8. When the cam 8 rotates to a predetermined rotation angle in such a state, the ball engages with the concave portion 8a of the cam 8 (FIG. 23A).
(See (b), (c) and (d)). Therefore, the rotation of the cam 8 is held in a stopped state. As a result, the rotation of the rotating shaft 2 is prevented, and as a result, the door D is held at the predetermined open position.

When the door D is further opened from such a state, the cam 8 further rotates, and the ball 44 escapes from the recess 8a of the cam 8 and engages with the next recess 8b of the cam (FIG. 2).
3 (e) (f)).

When the door D is held at the open position and a force is applied to the door D in a direction to close the door D, the slider 9 moves the coil spring 1 with the rotation of the cam 8.
23 (d) and (f) against the elastic force of 0, the ball 44 and the concave portion 8a of the cam 8 are disengaged from each other. Thereafter, the piston 4 is moved to the coil spring 10
23 (d) and (f) moves to the left. When the piston 4 moves to the left in this manner, as described above, the one-way valve 4a is shut off,
The movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is performed via a communication passage provided with a speed control valve. Therefore,
Depending on the degree of throttling of the speed regulating valve, the pressure oil produces a large resistance to the movement of the piston 4 in this direction.
As a result, the door D is automatically closed at a significantly reduced speed.

Next, a door closer according to a sixth embodiment of the present invention will be described with reference to FIG.

The door closer according to the sixth embodiment has a structure similar to that of the first embodiment.
The structure of the door closer and the stopper mechanism S according to the embodiment is different.

That is, the stopper mechanism of the door closer according to the sixth embodiment includes the concave portions 8a and 8b of the push rod 5 provided with the rack 5a at one end, and one of the concave portions 8a and 8b.
The ball 44 is an engagement member that can be brought into contact with the a and b, and a pressing unit that elastically presses the ball 44 into one of the recesses 8a and 8b.

The recesses 8a and 8b of the push rod 5
It functions similarly to the concave portions 8a and 8b of the cam 8 of the embodiment, and is formed, for example, in a spherical shape on the opposite side of the rack teeth 5a of the push rod 5. When a plurality of recesses 8a and 8b are formed, they are arranged in parallel to the axial direction of the push rod 5.

The engaging members that can contact the recesses 8a and 8b
Specifically, it is a steel ball 44 conforming to the shape of the recesses 8a, 8b, and one or a plurality of balls are housed in a tunnel-shaped guide hole 47 formed in the wall surface of the slider 9 in the slider axial direction. One end of the guide hole 47 is a coil spring 1
0 and the other end is open to the push rod 5 side. One ball 44 projects from the opening at the other end of the guide hole 47 toward the wall surface of the push rod 5, and a push rod 48 is inserted into the guide hole 47 from one opening of the guide hole 47. Have been. One end of the push rod 48 is connected to the coil spring 1 via a washer 49.
The other end of the push rod 48 is in contact with the rearmost ball 44a of the plurality of balls housed in the guide hole 47. Thereby, the push rod 5 slides with the opening and closing of the door D with respect to the slider 9, and when the opening of the door D reaches a desired size, the ball 44 receiving the repulsive force of the coil spring 10 pushes the push rod 5. The push rod 5 is restrained by being fitted into one of the concave portions 8a and 8b, which are the cams 8 on the 5, and the door D is held at the stop stop position.

The coil spring 10 of the slider 9
On the opposite side, the slider 9 is interposed between the coil spring 10 and
Is provided. This bolt 5
0 is screwed into the side wall of the casing 1. This bolt 5
Numeral 0 is also used as an adjusting screw, and is also provided with a function as adjusting means for adjusting the position of the ball 44, which is an engaging member that can abut on the recesses 8a and 8b. That is, the bolt 50 is further tightened than the state of FIG.
Is moved together with the slider 9 to the left in the figure, the stop position of the door can be changed.

Next, the operation of the door closer will be described.

When the door D is opened from the closed state, the rotating shaft 2 rotates, and the rotating force of the rotating shaft 2 is transmitted to the fluid pressure buffer 3 via the rack and pinion RP. That is, with the opening of the door D, the piston 4 slides in the cylinder bore 1a to the right in FIG. At this time, due to the operation of the one-way valve 4a, the pressure oil does not cause a large resistance to the movement of the piston 4. Therefore, the door D can be opened with a minimum force slightly larger than the elastic force of the coil spring 10.

When the door D is opened and the rotating shaft 2 rotates, the push rod 5 slides with respect to the slider 9. At this time, the ball 44 is pressed against the side surface of the push rod 5 by the coil spring 10 via the push rod 48. When the push rod 5 slides to a predetermined position in such a state, the ball 44
(See FIGS. 25A, 25B, 25C, and 25D).
Therefore, the slide of the push rod 5 is held in a stopped state. As a result, the rotation of the rotating shaft 2 is prevented, and as a result, the door D is held at the predetermined open position.

When the door D is further opened from such a state, the push rod 5 slides further and the ball 44
Escapes from the concave portion 8a of the cam 8, and the next concave portion 8b of the cam 8
(See FIGS. 25E and 25F).

When the door D is held in the open position and a force is applied to the door D in a direction to close the door D, the slider 9 resists the elastic force of the coil spring 10 and the door 9 moves as shown in FIG. At the left side, the ball 44 and the cam 8
Is disengaged from the recesses 8a and 8b. Thereafter, the piston 4 moves to the left by the action of the coil spring 10. When the piston 4 moves to the left in this manner, as described above, the one-way valve 4a is shut off,
The movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is performed via a communication passage provided with a speed control valve. Therefore,
Depending on the degree of throttling of the speed regulating valve, the pressure oil produces a large resistance to the movement of the piston 4 in this direction.
As a result, the door D is automatically closed at a significantly reduced speed (see FIGS. 25 (c), (b) and (a)).

Next, a door closer according to a seventh embodiment of the present invention will be described with reference to FIG.

The door closer according to the seventh embodiment has a
The structures of the door closer and the transmission according to the sixth to sixth embodiments are different.

That is, a crank mechanism is used in place of the rack and pinion RP in the first to sixth embodiments. Specifically, a crank arm 51 is
Are fixed, and a long hole 51a is formed in the crank arm 51 in the radial direction, and a crank pin 52 fixed to the push rod 5 is inserted into the long hole 51a.

Next, the operation of the door closer will be described.

When the door D is opened from the closed state, the rotating shaft 2 rotates, and this rotating force is transmitted to the fluid pressure buffering means 3 via the crank arm 51 and the crank pin 52. That is, with the opening of the door D, the piston 4 slides in the cylinder bore 1a to the right in FIG. On this occasion,
Due to the operation of the one-way valve 4a, the pressure oil does not cause a large resistance to the movement of the piston 4. Therefore, the door D can be opened with a minimum force slightly larger than the elastic force of the coil spring 10.

When the door D is opened and the rotating shaft 2 rotates, the cam 8 rotates at the same time. At this time, the roller 13 of the slider 9 is pressed against the outer peripheral surface of the cam 8 by the coil spring 10. When the cam 8 rotates to a predetermined rotation angle in such a state, the roller 13 engages with the concave portion 8a of the cam 8 (see FIGS. 27A, 27B, 27C, and 29D). Therefore, the rotation of the cam 8 is held in a stopped state.
As a result, the rotation of the rotating shaft 2 is prevented, and as a result, the door D is held at the predetermined open position.

When the door D is further opened from such a state, the cam 8 further rotates, and the ball is moved to the concave portion 8a of the cam 8.
And try to engage with the next recess of the cam (FIG. 2).
7 (e)).

When the door D is held in the open position and a force is applied to the door D in a direction to close the door D, the slider 9 moves the coil spring 1 with the rotation of the cam 8.
27 (e) and (d), the roller 13 of the slider 9 and the concave portion 8a of the cam 8 move to the left in FIG.
Is disengaged. Thereafter, the piston 4 moves to the left by the action of the coil spring 10. When the piston 4 moves to the left, the push rod 5 connected thereto also moves to the left, and the rotation shaft 2 rotates by the action of the crank arm 51 and the crank pin 52, and the door D rotates in the door closing direction.

As described above, when the piston 4 moves to the left, the one-way valve 4a is shut off as described above, and the movement of the pressure oil from the first chamber 1ax to the second chamber 1ay is as follows.
This is performed via a communication passage provided with a speed control valve. Therefore, depending on the degree of throttle of the speed control valve, the pressure oil generates a large resistance to the movement of the piston 4 in this direction. As a result, the door D is automatically closed at a significantly reduced speed.

Next, a door closer according to an eighth embodiment of the present invention will be described with reference to FIG.

The door closer according to the eighth embodiment has the structure shown in FIG.
The structure of the door closer and the stopper mechanism S according to the sixth embodiment shown in FIG. 4 is different.

That is, in the stopper mechanism of the door closer according to the eighth embodiment, one ball 44 functioning as a cam follower is inserted into the guide hole 47 formed in the slider 9, and comes into contact with the ball 44 at the tip of the push rod 48. A conical surface is formed. As a result of the ball 44 being pressed against the conical surface of the push rod 48, the ball 44 is pushed toward the wall surface side of the push rod 5 and strongly fits into the concave portion 8 a or 8 b functioning as a cam formed on the push rod 5. Recess 8a or 8
b is formed in the push rod 5 as an annular groove.
Accordingly, the movement of the rod 5 is restricted, and the rotation of the rotating shaft 2 is also restricted. As a result, the door D is stopped and held.

Next, a door closer according to a ninth embodiment of the present invention will be described with reference to FIG.

The door closer according to the ninth embodiment is shown in FIG.
The structure of the door closer and the stopper mechanism S according to the eighth embodiment shown in FIG. 8 is different.

That is, in the stopper mechanism of the door closer according to the ninth embodiment, the guide hole 47 formed in the slider 9 is an oblique hole that is inclined with respect to the sliding direction of the push rod 5. A plurality of balls 44, 44a, 44b are inserted. Therefore, the eighth
The push rod 48 of the embodiment is omitted. The leading ball 44 among the plurality of balls 44, 44 a, 44 b is a concave portion 8 which functions as a cam formed on the push rod 5.
a, 8b, and the tail ball 44b
Is a washer 49 on the side opposite to the piston of the coil spring 10.
Are in contact with each other. Ball 44 is coil spring 1
The push rod 5 is pushed toward the wall surface of the push rod 5 by the action of the zero reaction force, and is strongly fitted into one of the recesses 8 a and 8 b on the push rod 5. The recesses 8a and 8b are formed in the push rod 5 as annular grooves. Accordingly, the movement of the rod 5 is restricted, and the rotation of the rotating shaft 2 is also restricted.
As a result, the door D is stopped and held.

Of course, the door closers according to the first to third embodiments have been described as including the switching means 12, but the switching means 12 is an optional component and not an essential component. Therefore, if the effect provided by the switching means 12 is not required, the switching means may be omitted.

Further, in the first to ninth embodiments,
The closer body C is attached to the door D, and the link mechanism L is
Although it has been described that the rotating shaft 2 is connected to the door frame F side, the closer body is attached to the door frame F side,
The link mechanism L may be configured to connect the rotating shaft 2 to the door D side.

Further, in the above-described first embodiment,
Although the third embodiment has been described as using a single cam 38 using a pair of cams 8, three or more cams may be used.

[0114]

According to the door closer of the present invention, the stopper mechanism for holding the door at the predetermined open position is provided on the rotating shaft with the cam provided so as to rotate integrally therewith, and on the cam. Since it is composed of a contact member capable of contacting and pressing means for elastically pressing the contact member against the cam, a sufficient stop holding force can be secured, and the user can switch between the stopper operating state and the stopper released state. , The structure is simple, and the manufacturing cost can be kept low.

In the door closer of the present invention, claim 2 is provided.
As described in the above, if at least one concave portion is provided on the cam and a roller capable of engaging with the concave portion is provided on the contact member, a more appropriate stop holding force can be maintained in a state where a smooth door opening / closing operation is maintained. Can be secured.

In the door closer according to the present invention, a third aspect is provided.
As described in the above, if at least one convex portion is provided on the cam, and the contact member is provided with a concave portion which can be engaged with the convex portion, it is possible to maintain a smooth opening and closing operation of the door. Appropriate stop holding force can be secured.

In the door closer of the present invention, claim 4 is provided.
As described in the above, if the contact member is slidable in the length direction of the closer body, especially when the stopper mechanism is configured as an interior type, the contact member can be arranged coaxially with the rack. The body can be made more compact.

In the door closer according to the present invention, claim 5 is provided.
As described in the above, if the switching member for selectively switching the contact member between a stopper operating state capable of contacting the cam and a stopper releasing state that cannot contact the cam is provided, the door closer may be provided. Can be selectively and easily switched between the two states described above, and a use form suitable for the purpose can be realized.

According to the door closer of the present invention, the stopper mechanism for holding the door at the predetermined open position can contact the concave portion of the push rod provided with the rack at one end and the concave portion. Since it is composed of the engaging member and the pressing means for elastically pressing the engaging member against the concave portion,
Sufficient stop holding force can be secured, the user can be surely distinguished between the stopper operating state and the stopper releasing state, the structure is simple, and the manufacturing cost can be kept low.

In the door closer according to the present invention, claim 7 is provided.
As described in the above, since the adjusting means for adjusting the position of the engaging member that can contact the concave portion is provided, the stop position of the door can be easily adjusted from the outside.

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing an operation state of a door closer according to a first embodiment of the present invention.

FIG. 2 is a front view of the door closer of FIG. 1;

FIG. 3 is a side view of the door closer of FIG. 1;

FIG. 4 is a horizontal vertical sectional view of the door closer of FIG. 1;

FIG. 5 is a vertical longitudinal sectional view of the door closer of FIG. 1;

FIG. 6 is a vertical longitudinal sectional view showing switching means in the door closer of FIG. 1;

FIG. 7 is a rear view showing a contact member in the door closer of FIG. 1;

FIG. 8 is a sectional view of the contact member of FIG. 7;

FIG. 9 is a front view of a cam in the door closer of FIG. 1;

FIG. 10 is a front view showing a modification of the cam of FIG. 9;

FIG. 11 is a partial sectional view showing the operation of the door closer of FIG. 1;

FIG. 12 is a partial cross-sectional view showing an operation state of a door closer according to a second embodiment of the present invention.

FIG. 13 is a view showing a contact member in the door closer of FIG. 12;

FIG. 14 is a horizontal sectional view of a door closer according to a second embodiment of the present invention.

FIG. 15 is a vertical longitudinal sectional view of the door closer of FIG. 14;

FIG. 16 is a view showing a rotation shaft used in the door closer of FIG. 14;

FIG. 17 is a sectional view taken along line XVII-XVII in FIG. 16;

FIG. 18 is a diagram showing a contact member used in the door closer of FIG. 14;

FIG. 19 is a partial sectional view showing a first half of a series of operating states of a door closer according to a third embodiment of the present invention.

FIG. 20 is a partial sectional view showing the latter half of a series of operating states of the door closer according to the third embodiment of the present invention.

FIG. 21 is a partially cutaway horizontal sectional view of a door closer according to a fourth embodiment of the present invention.

FIG. 22 is a horizontal sectional view of a door closer according to a fifth embodiment of the present invention.

FIG. 23 is a horizontal sectional view showing a series of operating states of a door closer according to a fifth embodiment of the present invention.

FIG. 24 is a horizontal sectional view of a door closer according to a sixth embodiment of the present invention.

FIG. 25 is a horizontal sectional view showing a series of operating states of a door closer according to a sixth embodiment of the present invention.

FIG. 26 is a horizontal sectional view of a door closer according to a seventh embodiment of the present invention.

FIG. 27 is a horizontal sectional view showing a series of operating states of a door closer according to a seventh embodiment of the present invention.

FIG. 28 is a partially cutaway horizontal sectional view of a door closer according to an eighth embodiment of the present invention.

FIG. 29 is a partially cutaway horizontal sectional view of a door closer according to a ninth embodiment of the present invention.

[Explanation of symbols]

 C Closer body L Link mechanism D Door F Door frame B Bracket RP Rack and pinion S Stopper mechanism 2, 32 Rotary shaft 3 Fluid pressure buffering means 8, 18, 38 Cam 8a, 18a, 38a Recessed parts 9, 19, 39 Contact member DESCRIPTION OF SYMBOLS 10 Pressing means 12 Switching means 13,23,43 Roller 38b Convex part 43a Concave part 44 Ball 50 Bolt

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[Procedure amendment]

[Submission date] May 21, 2001 (2001.5.2)
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Claims (7)

[Claims] 1. A rotating shaft and a fluid pressure buffer connected to the rotating shaft via a transmission so as to impart a resistance to rotation of the rotating shaft, wherein one of a door and a door frame is provided. A door main body, a link mechanism for connecting the rotating shaft to the other of the door and the door frame, and a stopper mechanism for holding the door at a predetermined open position. The stopper mechanism includes a cam provided on the rotation shaft so as to rotate integrally with the cam, a contact member capable of contacting the cam, and pressing means for elastically pressing the contact member against the cam. A door closer characterized by being constituted. 2. The door closer according to claim 1, wherein the cam has at least one concave portion, and the contact member has a roller capable of engaging with the concave portion. 3. The device according to claim 1, wherein the cam has at least one convex portion, and the contact member has a concave portion engageable with the convex portion. Door closer. 4. The apparatus according to claim 1, wherein the contact member is slidable in a length direction of the closer body.
The door closer according to claim 3. 5. A switching means for selectively switching the contact member between a stopper operation state in which the contact member can contact the cam and a stopper release state in which the contact member cannot contact the cam. The door closer according to any one of claims 1 to 4, wherein the door closer is provided. 6. A rotating shaft and a fluid pressure buffer connected to the rotating shaft via a transmission so as to impart a resistance to rotation of the rotating shaft, wherein one of a door and a door frame is provided. A door main body, a link mechanism for connecting the rotating shaft to the other of the door and the door frame, and a stopper mechanism for holding the door at a predetermined open position. The stopper mechanism includes a concave portion of the push rod provided with the rack at one end, an engaging member capable of contacting the concave portion, and pressing means for elastically pressing the engaging member against the concave portion. A door closer characterized by: 7. The door closer according to claim 6, further comprising adjusting means for adjusting the position of the engaging member that can contact the concave portion.