JP3155452B2 - Clutch mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a clutch mechanism suitable for use in a door closer or the like.

[0002]

2. Description of the Related Art Generally, in a door closer, a door is urged to a closed position side by a return spring. However, if the door is urged to a normally closed position side, the door stops in an open state. Can not do it. Therefore, a clutch mechanism is installed on the door closer, and after the door is opened and rotated from the closed position to a predetermined position or more, the urging force of the return spring does not act on the door, thereby stopping the door at an arbitrary open position. So that it can be done.

A clutch mechanism having such a function is known, for example, from Japanese Patent Application Laid-Open No. Hei 4-27092. The clutch mechanism described in this publication uses three disks arranged one above the other with their axes aligned, and a clutch ball.The upper and lower disks are connected and fixed to a door and a gate post, respectively. The intermediate disk is disposed so as to be rotatable relative to the upper and lower disks. A return spring is provided between the intermediate disk and the door, and urges the door in the closing direction and urges the intermediate disk in the opening direction.

The above-mentioned clutch ball is accommodated in a through hole formed in an intermediate disk so as to be movable in the vertical direction, and the diameter thereof is larger than the thickness of the intermediate disk. Therefore, the upper or lower part of the clutch ball protrudes from the intermediate disk and enters one of the concave portions formed in the upper and lower disks, respectively. Thus, the intermediate disk and one of the upper and lower disks are non-rotatably connected.

In the above clutch mechanism, when the door is at the closed position, the intermediate disk and the lower disk are connected by a clutch ball. Therefore, in this case, the urging force acting on the intermediate disk is supported by the gate post via the intermediate and lower disks, and the door is urged in the closing direction. When the door is rotated to a predetermined position against the urging force of the return spring, the clutch ball comes out of the concave portion of the lower disk and enters the concave portion of the upper disk, and the intermediate disk and the upper Connect with disk. As a result, the urging force of the return spring does not act on the door. Therefore, the door can be stopped at an arbitrary position when the door is opened farther than the predetermined position.

[0006]

In the above-mentioned conventional clutch mechanism, when the clutch ball comes out of each recess,
And when entering into each concave part, the clutch ball and the peripheral part of the concave part make point contact. In addition, the clutch ball and the peripheral edge of the concave portion are strongly pressed by the return spring. For this reason, the clutch ball is worn early, and the peripheral edge of the concave portion is crushed or worn early. In addition, when the door is being rotated, the clutch ball comes into rolling contact with one of the upper and lower disks, but the clutch ball makes point contact with the upper and lower disks. For this reason, the clutch ball wears much earlier. As a result, the clutch mechanism may malfunction early.

[0007]

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and the invention according to claim 1 is an invention in which an outer member which is non-rotatably connected to one of two relatively rotating members. A cylinder, an intermediate cylinder rotatably fitted to the inner circumference of the outer cylinder, and a non-rotatably connected to the other of the two relatively rotating members, and a rotatable inner circumference of the intermediate cylinder. The fitted inner cylinder is provided between one of the outer cylinder and the inner cylinder and the intermediate cylinder, and urges the one and the intermediate cylinder to rotate in opposite directions. A biasing member, wherein the intermediate cylinder is formed with a holding notch that penetrates a peripheral wall thereof, and the holding notch has a diameter greater than a thickness of the peripheral wall of the intermediate cylinder and a radius of notch. The clutch shaft with a circular cross section smaller than the thickness of the peripheral wall of the intermediate cylinder The axis of the outer cylinder is parallel to the axis of the intermediate cylinder, and is movably mounted in the radial direction of the intermediate cylinder. The inner peripheral surface of the outer cylinder and the outer peripheral surface of the inner cylinder are provided with the holding cutoff at a predetermined rotation position. First and second locking notches are formed at positions facing the notch, into which a part of the outside of the clutch shaft and a part of the inside of the clutch shaft can enter, respectively .
The elastic member is provided between the outer cylinder and the intermediate cylinder.
The intermediate cylinder is provided with a key portion, and the inner cylinder is provided with a key.
The intermediate cylinder is moved from the predetermined rotation position to the elasticity.
Attempts to rotate in the direction opposite to the biasing direction of the member
When hitting the key, the middle circle
A reverse rotation restricting part is provided to prevent rotation of the cylinder in the same direction.
It is characterized by being. In this case, for the reason described later , the intermediate cylinder is
From the position in the same direction as the biasing direction of the elastic member.
When the key has rotated by a predetermined amount
To prevent the rotation of the intermediate cylinder in the same direction
It is desirable to provide a direction rotation restricting portion . Also, the above intermediate
A shaft is provided on the inner circumference of the cylinder so that it cannot rotate, and the outer circumference of this shaft is
The key portion is provided on the inner peripheral surface of the inner cylinder in the opposite direction.
It is desirable to provide a rotation restricting portion and the forward rotation restricting portion .

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, as a preferred embodiment of the present invention, a door closer 1 having a clutch mechanism according to the present invention will be described with reference to FIGS. The door closer 1 has a fixing portion 2 fixed to the gate post A.
And a rotating part 3 fixed to the gate B. The fixed portion 2 has a cylinder portion 2a, and a shaft 44 (described later) of the rotating portion 3 is rotatably inserted into the cylinder portion 2a, so that the rotating portion 3 is fixed to the fixed portion 2a. The gate B is rotatably supported by the gate A. Reference numeral C denotes a hinge provided between the gate post A and the gate B, and supports the gate B rotatably.

The door closer 1 has a clutch mechanism 4 and a damper mechanism 5 which will be described later, and the gate B rotates as follows by these functions. That is, as shown in FIG. 5, the gate B is rotatable between a closed position indicated by reference numeral A and a fully opened position indicated by reference numeral C,
In the range between the closed position A and the half-open position B separated by a predetermined rotation angle (hereinafter, this range is referred to as a restriction range X), the closing direction (arrow) is set by the return spring 45 of the clutch mechanism 4. B direction). Also,
In the regulation range X, when the gate B is rotated in the opening direction (the direction of the arrow A), no damping force is exerted on the gate B by the damper mechanism 5, but when the gate B is rotated in the closing direction. , A damper force acts to prevent rapid rotation of the gate B. On the other hand, in a range between the half-open position B and the fully-open position C (hereinafter, this range is referred to as a free range Y), the urging force and the damper force do not act on the gate B, and the gate B rotates freely. , Can be stopped.

Next, the structure of the door closer 1, in particular, the structure of the rotating portion 3 will be described in detail. As shown in FIG. 7, the rotating portion 3 has a rotating portion main body 31. As shown in FIG. 8, the rotating portion main body 31 has a cylindrical support tubular portion 32.
And a mounting plate portion 33 radially protruding from one side of the outer peripheral surface of the support tube portion 32. The rotation plate 3 is fixed to the gate B so that the rotating portion 3 It is fixed to the gate B. A key groove 34 extending from the upper end to the lower end is formed on the inner peripheral surface of the support cylinder 32.

As shown in FIG. 7, a clutch mechanism 4 is provided on the lower side and a damper mechanism 5 is provided on the upper side inside the support cylinder 32 of the rotating section main body 31.

The clutch mechanism 4 is for applying a spring force in the closing direction to the gate B in the restriction range X and for preventing the spring force from acting in the free range Y. The main components are an outer cylinder 41, an intermediate cylinder 42, a gate-side fixed cylinder (inner cylinder) 43, a shaft body 44, and a return spring (elastic member) 45.

The body-side fixed cylinder 41 is shown in FIGS.
As shown in the figure, the lower-diameter cylindrical portion 41a is concentric with the lower-diameter cylindrical portion 41b. The large-diameter cylindrical portion 41a is formed by fitting the key portion 41c into the key groove 34 of the support tubular portion 32.
Are fitted non-rotatably. A pair of locking window holes (first locking notches) 41d, 4 are formed in the peripheral wall of the large-diameter cylindrical portion 41a.
1d are formed 180 degrees apart in the circumferential direction. An insertion hole 41e extending in the circumferential direction is formed in the upper bottom of the large-diameter cylindrical portion 41a.

The intermediate cylinder 42 has a cylindrical shape, and is rotatably fitted to the inner peripheral surface of the large-diameter cylindrical portion 41a of the fixed cylinder 41. As shown in FIGS. 9 and 11, a pair of locking grooves 4 are formed on the outer peripheral surface of the upper end portion of the intermediate cylinder 42.
2a are formed 180 degrees apart in the circumferential direction. A locking claw 45a formed at the lower end of the return spring 45 is fitted into one of the pair of locking grooves 42a through the insertion hole 41e of the main body-side fixed cylinder 41. The upper end of the return spring 45 is connected to the support tubular portion 32 of the rotating portion main body 31 via the tubular body 11.
(See FIG. 7). Then, the return spring 45
As a result, the intermediate cylinder 42 is urged in the opening direction, while the rotating portion main body 31 is urged in the closing direction. Since the fixed cylinder 41 is non-rotatably connected to the support cylinder 32 of the rotating section main body 31, the fixed cylinder 41 is also urged in the closing direction by the return spring 45.

The intermediate cylinder 42 has a small-diameter hole 42b at the upper end and a large-diameter hole 42c at the lower end. A pair of key grooves 42 is provided on the inner peripheral surface of the small diameter hole 42b.
d are formed 180 degrees apart in the circumferential direction. On the other hand, a pair of holding notches 42e penetrating through the large-diameter hole 42c is formed on the lower peripheral wall at the lower end side.
They are formed 0 ° apart. The holding notch 42e is formed in the locking window hole 4 of the body-side fixed cylinder 41 in the axial direction.
It is arranged at the same position as 1d.

A cylindrical clutch shaft 46 is inserted into the holding notch 42e with its axis directed vertically. The outside diameter D of this clutch shaft 46 is
The width is substantially the same as the width e (width in the circumferential direction).
Therefore, the clutch shaft 46 cannot move in the circumferential direction of the intermediate cylinder 42, but can move in the radial direction.

If the outer diameter of the clutch shaft 46 is D, and the thickness of the peripheral wall of the intermediate cylinder 42 in which the holding notch 42e is formed is T, the following relationship holds: D> T. Therefore, the clutch shaft 46 is
The outer or inner part thereof projects from the holding notch 42e, and the holding notch 42e and the fixed cylinder 41
When the retaining window hole 41d is opposed to the
Part of the outside of the clutch shaft 46 protruding from e can enter the locking window hole 41d. In a state where a part of the clutch shaft 46 has entered the locking window hole 41d, the intermediate cylinder 42 and the fixed cylinder 41 are non-rotatably connected via the clutch shaft 46.

The outer diameter D of the clutch shaft 46 is D / 2
<T. Moreover, the holding notch 42e
Assuming that the amount of protrusion of the clutch shaft 46 from P is P (= D−T), the amount of protrusion P is substantially the same as the thickness of the peripheral wall of the large-diameter cylindrical portion 41a. Therefore, the clutch shaft 46 enters the engagement window hole 41d only in a portion smaller than half of the entire clutch shaft 46. Therefore, if it is attempted to relatively rotate the fixed cylinder 41 and the intermediate cylinder 42 in a state where a part of the clutch shaft 46 has entered the locking window hole 41d,
The clutch shaft 46 is pushed inward by one of the inner side edges of the locking window hole 41d.

As shown in FIGS. 7, 9 and 12, the gate-side fixed cylinder 43 has an upper end side small diameter portion 43a and a lower end side large diameter portion 43b which are concentric with each other. The small diameter portion 43a is rotatably fitted in the large diameter hole 42c of the intermediate cylinder 42. On the other hand, a substantially square projecting portion 43c is formed on the lower end surface of the large diameter portion 43b. One end of the connection fitting 12 is non-rotatably fitted to the protruding portion 43c, and two engagement pieces 1 are attached to the other end of the connection fitting 12.
2a and 12b are formed. Then, as shown in FIG. 3, by inserting the fixing portion 2 between the engagement pieces 12a and 12b, the connection fitting 12 is non-rotatably connected to the fixing portion 2, and the gate-side fixing cylinder 43 is eventually turned. It is non-rotatably connected to the fixed part 2. .

A pair of locking grooves (second locking notches) 43d, 43d are formed on the outer peripheral surface of the small diameter portion 43a of the fixed cylinder 43.
Are formed 180 degrees apart in the circumferential direction. The locking groove 43d is arranged at the same position as the holding notch 41e of the intermediate cylinder 42 in the axial direction. Moreover,
The locking groove 43d has the same radius of curvature as the clutch shaft 46, and has a depth substantially the same as the protrusion amount P.
Therefore, when the locking groove 43d is opposed to the holding notch 41e, a part of the inside of the clutch shaft 46 is locked.
You can get into it. When the clutch shaft 46 is partially inserted, the fixed cylinder 43 and the intermediate cylinder 42 are non-rotatably connected via the clutch shaft 46. If the fixed cylinder 43 and the intermediate cylinder 42 are relatively rotated in this state, the clutch shaft 46 is pushed outward by one of the two side edges of the locking groove 43d.

Next, the operation of the clutch mechanism 4 having the above configuration will be described. In this case, the positional relationship among the locking window 41d, the holding notch 42e, and the locking groove 43d will be clear. Now, it is assumed that the gate B is located at the closed position A. At this time, as shown in FIG. 1A, a part of the inside of the clutch shaft 46 has entered the locking groove 43d, and the intermediate cylinder 42 and the fixed cylinder 43 are non-rotatably connected. The fixed cylinder 41 is provided with the locking window hole 4.
1 d is located away from the holding notch 42 e of the intermediate member 42 in the closing direction (the direction of the arrow B), and is urged in the closing direction by the return spring 45. Therefore, the gate B is also biased in the closing direction.

When the gate B is rotated in the opening direction (the direction of the arrow A in FIG. 1A) against the urging force of the return spring 45, the fixed cylinder 41 is also rotated in the same direction. When the gate B is rotated to the half-open position B, the locking window 41d faces the holding notch 42e as shown in FIG. 1 (B). Thereafter, when the fixed cylinder 41 is further rotated in the same direction, the intermediate cylinder 42 is urged in the opening direction by the return spring 45 as shown in FIG. The outer edge of the clutch shaft 46 is pushed out by the locking groove 43d, and a part of the outer side enters the locking window hole 41d. Thereby, the connection between the intermediate cylinder 42 and the gate-side fixed cylinder 43 is released, while the fixed cylinder 41 and the intermediate cylinder 42 are integrally connected. As a result, the fixed cylinder 41 and the intermediate cylinder 42
Of the return spring 45 acting between the clutch shaft 4
6 and does not act as a force to close the gate B. Therefore, the gate B can freely rotate and stop at any position. When the gate B rotates to the fully open position c, it cannot rotate any more. This will be described later.

Conversely, when the gate B is rotated from the fully closed position C toward the closed position A when the gate B is rotated to the half open position B, the fixed cylinder 41 rotates in the same direction. The holding notch 42e faces the locking groove 43d. Thereafter, when the fixed cylinder 41 is further rotated in the closing direction by a small amount, it is pushed inward by the side edge of the locking window hole 41d located in the opening rotation direction. As a result, the clutch shaft 46 moves inward,
While falling out of the locking window hole 41d, a part of the inside enters the locking groove 43d. As a result, the connection between the fixed cylinder 41 and the intermediate cylinder 4 is released, and the intermediate cylinder 42 and the fixed cylinder 43 are non-rotatably connected. Therefore, the urging force in the closing direction by the return spring 45 acts on the fixed cylinder 41, and the gate B is closed and rotated to the closed position A by the return spring 45.

Here, in the above-mentioned clutch mechanism 4, the clutch shaft 46 has a columnar shape parallel to the axis of each of the cylinders 41, 42, 43. The inner edge of the locking window hole 41d, that is, the side edge where the both side surfaces located in the circumferential direction of the locking window hole 41d and the inner peripheral surface of the fixed cylinder 41 intersect is the cylinder 4
The axis is parallel to the first axis, and both side edges of the locking groove 43d are also the same. Therefore, the clutch shaft 46 and the side edge of the locking window hole 41d and the side edge of the locking groove 43d are all in line contact. Thus, the pressure acting on each side edge can be significantly reduced as compared to the conventional one in which they are in point contact, thereby preventing each side edge from being crushed or prematurely worn. be able to. Also, the clutch shaft 46 is in rolling contact with the inner peripheral surface of the fixed cylinder 41 when the locking window hole 41d is separated from the holding notch 42e, and the locking groove 43d is separated from the holding notch 42e. , It comes into rolling contact with the outer peripheral surface of the fixed cylinder 43. At this time, the clutch shaft 46 makes line contact with the inner peripheral surface or the outer peripheral surface. Therefore, it is possible to prevent the clutch shaft 46 from being worn out early. Therefore, the clutch mechanism 4 can be operated in a good state for a long time.

In the free range Y, the gate B
Can be freely rotated, so that it can be rapidly rotated in the closing direction. However, when the gate B is rapidly rotated from the free range Y to the restricted range X, the clutch shaft 46 does not enter the locking groove 43d at the half-open position B, but remains in the locking window hole 41d. May pass through. In order to prevent such a problem and to surely stop the gate B at the fully open position C, the door closer 1 of this embodiment employs the following configuration.

That is, as shown in FIG. 7, the inner diameter of the small diameter portion 41b of the main body side fixed cylinder 41, the inner diameter of the small diameter hole 42b of the intermediate cylinder 42, and the inner diameter of the gate side fixed cylinder 43 are set to the same size. The shaft body 44 is inserted through them. On the outer peripheral surface of this shaft body 44,
A pair of key grooves 44a, 44a are arranged 180 degrees apart in the circumferential direction, and approximately half the inside of a key (key portion) 47 is fitted into each key groove 44a. The upper half of the outer half of the key 47 is fitted into the key groove 42d of the intermediate cylinder 42. Thus, the shaft body 44 and the intermediate cylinder 42 are connected so as to rotate integrally.

As shown in FIGS. 1 and 12, a pair of rotation restricting grooves 43e, 43e are formed in the upper part of the inner peripheral surface of the gate side fixed cylinder 43. Each rotation restricting groove 43e
Extends in the circumferential direction at substantially the same angle as the angle between the half-open position A and the fully-open position C, and the lower half of the key 47 is fitted movably in the circumferential direction. Further, when the gate B closes from the fully open position C and reaches the half-open position B, the key 47 is turned into the rotation restricting groove 43e.
When it reaches the end (forward rotation restricting portion) 47f on the closing direction side, it opens and rotates from the half-open position B side and reaches the fully open position c, and hits the other end (reverse rotation restricting portion) 47g. Are arranged as follows.

Therefore, the intermediate cylinder 42 and the shaft body 44
Is rotated in the direction of arrow B from the fully open position c and the holding notch 42e faces the locking groove 43d of the fixed cylinder 43,
Since the key 47 abuts on the end 47f, the key 47 cannot rotate further in the same direction and stops. Therefore,
The clutch shaft 46 can reliably enter there without passing through the locking groove 43d. When the gate B rotates in the opening direction and reaches the fully open position c, the key 46 is moved to the regulating groove 4.
Since the intermediate cylinder 42 and the shaft body 44 cannot rotate any more in the same direction because of abutment against the end portion 47g of 3e, the intermediate cylinder 42 and the shaft body 44 stop. As a result, the gate-side fixed cylinder 41 and the main body 31 are stopped, and the gate B is reliably stopped at the fully open position c.

Next, the damper mechanism 5 will be described.
As shown in FIG. 7, the damper mechanism 5 includes a pressure generating unit 6 and a pressure control unit 7.

First, the pressure generator 6 will be described.
The pressure generating section 6 has a casing 61 and the shaft body 44 as main components. The casing 61 is shown in FIGS.
As shown in FIG. 14 and FIG.
The main body 31 is fitted around the inner periphery of the support cylinder 32, and the key 61 a is fitted into the key groove 34 of the support cylinder 32 so as to be non-rotatably supported by the support cylinder 32. Therefore, the casing 61 rotates integrally with the gate B. At the center of the casing 61, the shaft 4
4 is inserted. Shaft 4 facing casing 61
A large diameter portion 44b is formed on the outer peripheral surface of the casing 4 and the upper and lower ends are sealed by seal members 62, 62 between the outer peripheral surface of the large diameter portion 44b and the inner peripheral surface of the casing 61. A closed annular space is formed. A fluid is sealed in this closed space. In this case, it is desirable to use a viscous fluid as the fluid.

On the inner peripheral surface of the casing 61, two partition portions 61b are formed so as to be 180 ° apart in the circumferential direction. The distal end surface (the inner peripheral surface) of each partition 61b is relatively rotatably and liquid-tightly contacted with the outer peripheral surface of the shaft body 44, thereby dividing the closed space into two spaces S, S. ing. On the other hand, on the outer peripheral surface of the large-diameter portion 44b of the shaft body 44, two support protrusions 44c are arranged and formed 180 ° apart in the circumferential direction. A support recess 44d having a substantially semicircular shape is formed on the distal end surface (surface on the outer peripheral side) of each support protrusion 44c.
The opening / closing valve body 63 is rotatably supported in each support recess 44d.

The opening-closing valve body 63, a high pressure chamber S _H side (the arrow A direction in FIG. 15) to open pivoting direction the space S, into a low pressure chamber S _L of the closed kinematic direction (arrow B) side It is for partitioning and has a shaft portion 63a having a substantially circular cross section. The shaft portion 63a is rotatably supported by the shaft body 44 by being rotatably fitted into the support recess 44d. On one side of the outer peripheral surface of the shaft portion 63a in the direction of arrow A, a valve portion 63b is formed which extends over the entire length thereof. A communication groove 63c is formed on the outer peripheral surface of the on-off valve body 63 and extends from a position slightly deviated from the tip of the valve portion 63b in the direction of arrow B to the shaft portion 63a.

The valve portion 63b and the communication groove 63c provide
Depending on the rotational direction of the gates B and the the high-pressure chamber S _H and the low-pressure chamber S _L so that the communication is interrupted. That is, FIG.
4 (A) shows a state when the gate B is closed. When the gate B is opened from the closed position A and the casing 61 is rotated in the direction of arrow A accordingly (at this time, As described above, the shaft body 44 is stopped.), The low-pressure chamber S _L
The valve body 63 is rotated clockwise by the fluid inside,
The valve portion 63b moves away from the inner peripheral surface of the casing 61. As a result, the high pressure chamber S _H and the low-pressure chamber S _L communicate with each other through the communication groove 63c. Therefore, high pressure is not generated in the high pressure chamber S _H and the low-pressure chamber S _L.

On the other hand, FIG. 14B shows a state in which the gate B is located at the half-open position B. From this state, the gate B is closed and rotated, and accordingly, the casing 61 is moved in the direction indicated by the arrow B. When rotated in the direction, the valve body 63 by the fluid in the high pressure chamber S _H is pivoted in the counterclockwise direction, the valve portion 63b is in contact with the inner peripheral surface of the casing 61. As a result, the high pressure chamber S
_H and the low pressure chamber S _L is cut off, a high pressure is generated in the high pressure chamber S _H. When the high-pressure chamber _SH becomes high in pressure, the pressure presses the casing 61 in the opening direction via the partition 61b. Therefore, the closing rotation speed of the gate B decreases. The pressure in the high pressure chamber S _H is adjusted appropriately by the pressure control unit 7 to be described later.

On both upper and lower ends of the shaft portion 63a, elastic projecting pieces 63d projecting in the opposite direction to the valve portion 63b are formed. As shown in FIG. 14A, the elastic body 63d rotates the valve body 63 clockwise due to the rotation of the casing 61 in the direction of arrow A, and the communication groove 63c.
Is open, the end of the casing 61
, And is elastically deformed by being brought into contact with the inner peripheral surface thereof to urge the valve body 63 to rotate counterclockwise. Therefore, when the casing 61 rotating in the direction of arrow A is stopped,
The elastic protruding piece 63d rotates the valve body 63 counterclockwise, and causes the valve portion 63b to approach the inner peripheral surface of the casing 61. Therefore, when to rotate the casing 61 in the arrow B direction may be the valve portion 63 comes into contact immediately with the inner peripheral surface of the casing 61, thereby immediately generate a high pressure in the high pressure chamber S _H.

When the gate B is located in the free area X between the half-open position B and the fully-open position C, the casing 61 and the shaft 44 rotate integrally. Therefore, high pressure is not generated in the high pressure chamber S _H.

Next, the pressure controller 7 will be described.
As shown in FIGS. 15 and 17, a vertical hole 44e extending downward is formed in the upper end surface of the shaft body 44. An upper horizontal hole 44e and a lower horizontal hole 44f are formed in the large diameter portion 44b. Upper lateral hole 44e has one end opened to the low pressure chamber S _L, the other end is vertical hole 44e open. On the other hand, the lower horizontal hole 44g has one end open to the high pressure chamber S _H, and the other end is open to the vertical hole 44e.

A pressure regulating valve 8 is provided in the vertical hole 44e. The pressure adjusting valve 8 has a valve body 81 screwed into the vertical hole 44e. The lower end of this valve body 81
The storage hole 81a is located slightly above the lower horizontal hole 44g, and has a storage hole 81a extending upward at the center of the lower end surface. The valve body 81 has window holes 81b, 81b extending from the outer peripheral surface to the storage hole 81a. Each window hole 81b is arranged and formed so as to communicate with the upper horizontal hole 44f regardless of the rotational position of the valve body 81.

A valve body 82 is slidably provided in the housing hole 81a. At the lower end of the valve body 82, a valve portion 82a is formed. This valve portion 82a is connected to the high pressure chamber S
Until _H reaches a predetermined pressure, it is pressed against the bottom surface of the vertical hole 44e by a spring 83 for urging the valve body 82 downward, and protrudes downward from the storage hole 81a. The magnitude of the urging force of the spring 83 for urging the valve element 82 downward is
It can be adjusted by adjusting screw 84. Also, the valve 82
A plurality of vertically extending communication grooves 82b are formed on the outer peripheral surface of the valve body 82 following the line a. When the valve portion 82a abuts against the bottom surface of the vertical hole 44e, the lower end portion of the communication groove 82b is exposed downward from the vertical hole 44e, and the upper end portion faces the window hole 81b. Therefore, in this state, the clearance C between the lower edge of the high pressure chamber S _H and the low-pressure chamber S upper end of the _L leaflet portion 82a edge and the valve body 81, communication grooves 82b, window holes 81b and the upper and lower horizontal holes 44f , 44g. On the other hand, when the valve portion 82a moves upward against the urging force of the spring 83 and fits into the storage hole 81a, the high pressure chamber S _H
It is blocked by the low-pressure chamber S _L leaflets 82 and.

The pressure control unit 7 configured as described above, to adjust the pressure in the high pressure chamber S _H as follows, to control the closed kinematic velocity of the gates B. That is, when the gates B starts closed kinematic in regulating range X by the biasing force of the return spring 45, the fluid is lower horizontal hole 44g in the high pressure chamber S _H, the clearance C, the communication groove 82b, windows 8
Through 1b and upper lateral holes 82b and flows into the low pressure chamber S _L. At the beginning of the closing rotation in which the rotation speed of the gate B is slow, the flow resistance to the fluid due to the gap C is small, but as the closing rotation speed of the gate B increases, the flow resistance in the gap C increases. There is no closing rotation at a speed higher than the rotation speed.
The flow resistance due to the gap C can be adjusted by changing the position of the valve body 81 in the vertical direction.

[0041] In the course closed movement of the gates B, when it is pressed in the closing direction by the wind or manpower, but gates B tries closed kinematic above a predetermined speed, the pressure in the high pressure chamber S _H The valve body 82 moves upward against the urging force of the spring 83, and the valve portion 82a fits into the storage hole 81a. Thus, the cut off between the high pressure chamber S _H and the low-pressure chamber S _L. Therefore, the gate B stops. In practice, the partition wall 61 of the large diameter portion 44b and the casing 61 of the high pressure chamber gaps minute between the members for blocking between S _H and the low-pressure chamber S _L, for example, shaft 44
Since the fluid flows through the small gap between the gate B and the gate B, the gate B closes and turns at an extremely low speed. When the pressing force in the closing direction to gates B does not act, the pressure of the high pressure chamber S _H is lowered, is moved downward by the valve body 82 the spring 83. Thus, communication with the high pressure chamber S _H and the low-pressure chamber S _L again, gates B is closed kinematic again at a predetermined rotational speed.

As shown in FIG. 7, the above-mentioned clutch mechanism 4 and damper mechanism 5 are attached to the support cylindrical portion 32 by upper and lower lids 13 and 14 so as not to escape. Reference numeral 15 denotes a decorative lid.

The clutch mechanism according to the present invention is not limited to the above-described embodiment, but can be appropriately designed and changed.
For example, the clutch mechanism of the present invention is applicable to anything other than the door closer as long as it has two members that rotate relatively. In the above embodiment,
Although the lower end of the holding notch 42e is open downward, it may be formed as a hole such as the locking window hole 41d. However, in such a case, the fixed cylinder 41,
In order to enable the assembling of the 43 and the intermediate cylinder 42, it is necessary to open the lower end of the locking window hole 41d. Further, the locking window hole 41d is formed as a through-hole penetrating the peripheral wall of the fixed cylinder 41, but may be a groove similar to the locking groove 43d. Of course, the locking groove 43d may be a through hole similar to the locking window hole 41d.

[0044]

As described above, according to the first aspect of the present invention, early wear of the clutch shaft, and the first and second clutch shafts are achieved.
It is possible to prevent the side edges of the locking notch from being crushed and prematurely worn, so that the clutch mechanism can be favorably operated for a long period of time. According to the invention of claim 2, when the outer cylinder is rotated from the free range to the restricted range, the clutch shaft can be reliably inserted into the first locking notch of the outer cylinder. According to the third aspect of the present invention, the range in which the outer cylinder can rotate in the direction opposite to the biasing direction of the elastic member can be reliably restricted. According to the invention according to claim 4, the clutch mechanism can be downsized.

[Brief description of the drawings]

FIG. 1 shows a main part of a clutch mechanism according to the present invention;
FIG. 1 (A) shows a state when the gate is located at a closed position, and FIG. 1 (B) shows a state when the gate is located at a half-open position. FIG. 1
FIG. 1C shows a state where the gate is slightly rotated from the half-open position to the fully-open position, and FIG. 1D shows a state where the gate is located at the fully-open position.

FIG. 2 is a front view showing a gate post and a gate to which a door closer having the clutch mechanism shown in FIG. 1 is attached.

FIG. 3 is a perspective view showing an attachment state of a door closer, a gate post, and a gate.

FIG. 4 is a plan view of the same.

FIG. 5 is a plan view showing a rotation range of a gate.

FIG. 6 is a perspective view showing a rotating portion of the door closer.

FIG. 7 is a vertical cross-sectional view of the rotation unit.

FIG. 8 is a view showing a rotating portion main body of the rotating portion, and FIG.
8A is a front view thereof, FIG. 8B is a plan view thereof, FIG.
FIG. 9C is a sectional view taken along the line CC of FIG.

FIG. 9 is an exploded perspective view showing a clutch mechanism of the door closer.

10 (A) is a plan view, FIG. 10 (B) is a front view thereof, and FIG. 10 (C) is FIG. 10 (A). It is CC sectional drawing of.

11 (A) is a plan view of the clutch mechanism, FIG. 11 (B) is a front view thereof, FIG. 11 (C) is a bottom view thereof, and FIG. D) is FIG.
It is DD sectional drawing of 1 (A).

12 (A) is a plan view, FIG. 12 (B) is a front view thereof, and FIG. 12 (C) is a bottom view thereof. 12 (D) is a sectional view taken along line DD of FIG. 12 (A).

FIG. 13 is an exploded perspective view showing a pressure generating portion of a damper mechanism of the door closer.

FIG. 14 is an enlarged sectional view taken along the line YY of FIG. 7 showing the pressure generating unit, wherein FIG. 14 (A) shows a state when the gate is located at a closed position, and FIG. The state when the gate is located at the half-open position is shown.

15A and 15B are views showing a shaft body of the door closer, wherein FIG. 15A is a partially omitted front view, FIG. 15B is a partially omitted side view, and FIG. CC of (B)
FIG. 15D is a cross-sectional view, FIG.
(F) is each EE and FF sectional drawing of FIG. 15 (A).

16A and 16B are diagrams showing an opening / closing valve body of a pressure generating portion of the damper mechanism of the door closer, wherein FIG. 16A is a plan view thereof, and FIG. 16B is an enlarged BB of FIG. 16A. Sectional view,
FIG. 16C is a view taken in the direction of arrow C in FIG. 16B, and FIG.
FIG. 4 is an enlarged sectional view showing a relationship between an inner peripheral surface of a casing and an on-off valve body.

FIG. 17 is a view illustrating a pressure control unit of the damper mechanism, taken along line Z- in FIG.
It is a Z enlarged sectional view. .

FIG. 18 is an exploded perspective view showing the pressure control unit.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Door closer 2 Fixed part (one member) 3 Rotating part 31 Rotating part main body (the other member) 41 Main body side fixed cylinder (outer cylinder) 41d Locking window hole (first locking notch) 42 Intermediate cylinder 42e Holding notch 43 Gate cylinder side fixed cylinder (inner cylinder) 43d Locking groove (second locking notch) 43e Rotation restricting groove 43f End of rotation restricting groove (reverse rotation restricting part) 43g times End of movement regulation groove (forward rotation regulation part) 44 Shaft 45 Return spring (elastic member) 46 Clutch shaft 47 Key (key part)

Claims (3)

(57) [Claims] An outer cylinder non-rotatably connected to one of two relatively rotating members, an intermediate cylinder rotatably fitted to an inner periphery of the outer cylinder, and an outer cylinder rotatably connected to the two relatively rotating members. An inner cylinder rotatably connected to the other side and rotatably fitted to the inner periphery of the intermediate cylinder, and an inner cylinder provided between one of the outer cylinder and the inner cylinder and the intermediate cylinder. A biasing member for biasing the one and the intermediate cylinder so as to rotate in the opposite directions to each other, wherein the intermediate cylinder is formed with a holding notch penetrating a peripheral wall portion thereof. The notch has a clutch shaft having a circular cross section with a diameter larger than the thickness of the peripheral wall of the intermediate cylinder and a radius smaller than the thickness of the peripheral wall of the intermediate cylinder, with its axis parallel to the axis of the intermediate cylinder. The inner peripheral surface of the outer cylinder is mounted to be movable in the radial direction of And the outer peripheral surface of the inner cylinder,
First and second locking notches, into which a part of the outside and an inside of the clutch shaft can enter, respectively, are formed at a position facing the holding notch at a predetermined rotation position. The elastic member comprises the outer cylinder and the intermediate cylinder
And a key portion is provided on the intermediate cylinder.
The intermediate cylinder is mounted on the inner cylinder at the predetermined rotation position.
From the position in the direction opposite to the biasing direction of the elastic member.
When trying to rotate, hit the above key part
Reverse rotation that prevents rotation of the intermediate cylinder in the same direction
A clutch mechanism comprising a movement restricting portion . 2. The inner cylinder is provided with the intermediate cylinder.
From the fixed position in the same direction as the biasing direction of the elastic member
When the key has rotated by a predetermined amount,
Prevents rotation of the intermediate cylinder in the same direction by tapping
The clutch mechanism according to claim 1, further comprising a forward rotation restricting portion . 3. A shaft body cannot rotate around the inner periphery of the intermediate cylinder.
The key portion is provided on the outer periphery of the shaft body,
The above-mentioned reverse rotation restricting portion and the above-mentioned
The clutch mechanism according to claim 2, further comprising a forward rotation restricting portion .