JPH01299985A - Closer for sliding door - Google Patents

Abstract

PURPOSE:To ensure the proper operation of a sliding door by providing a driving drum wound with a tape-shaped driving spring and a speed control drum wound with a speed control spring of small tension, and applying a brake power via a centrifugal governor coming in slidable contact with a friction block at the time of door closing. CONSTITUTION:A casing 5 houses a driving drum 6 wound with a driving spring 1 comprising a natural contact type spiral spring, and a speed control drum 15 wound with a speed control spring 16 weaker than the spring 1. Furthermore, a friction drum 14 is housed in the drum 15, thereby constituting a one-way clutch comprising the external surface of the drum 14, a clutch groove 18 and a clutch ball 19. Then, the casing 5 is mounted on a sliding door 5 and one end of the spring 1 is hooked to a front closer, while one end of the spring 16 hooked to a back closer, respectively. When the rear side of the sliding door 25 striding over the rail of door rollers is released, the clutch operates and the drums 14 and 15 are thereby integrated. Furthermore, friction blocks 23 and 23 move outward due to a centrifugal force and come in slidable contact with the drum 14, thereby braking the sliding door 25 and ensure the uniform speed travel thereof. Consequently, it becomes possible to ensure the proper operation of the sliding door.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a sliding door closer, and more particularly to a sliding door closer that is simple and compact in structure and operates reliably.

[Conventional technology]

Sliding door closers that are guided by rails, door wheels, etc. and move parallel to the door surface include those that use a tension coil spring or a clockwork spring as the drive source for closing the sliding door and an air damper as a brake, and those that use a hydraulic damper as a revolving door. The link mechanism of the door closer for sliding doors has been modified to be used for sliding doors, and the door closer is guided inside the sliding door and the door frame so that it can move vertically, and the sliding door is closed using gravity while the air damper acts as a brake. etc. have been proposed and some are commercially available.

[Problem to be solved by the invention]

However, the inventors of the present invention actually purchased and tried a sliding door closer that combines a tension coil spring and an air damper, but the spring was weak and the sliding door could not be closed reliably and did not work. It is uncertain, and on the other hand, if you strengthen the spring,
Since I could easily predict that the impact would be greater when the sliding door was closed, I ended up buying it, but I had the experience of removing it from the sliding door.

Further, a door closer in which the link mechanism of a door closer for a revolving door is modified to be used for a sliding door can be expected to operate reliably, but it is too large in weight and size, and is generally unsuitable for a simple sliding door.

Furthermore, a closer using a weight requires a weight or the like to be incorporated into the sliding door or the door frame during manufacturing, and there is a disadvantage that it is difficult to apply to an existing sliding door. For these reasons, it is no exaggeration to say that there is currently no practical sliding door closer.

An object of the present invention is to provide a sliding door closer that is simple and compact in structure, operates reliably, and can be attached to an existing sliding door.

[Means to solve the problem]

In order to achieve the above object, the invention according to claim 1:
A tape-shaped drive spring consisting of a natural contact spiral spring, one end of which is connected to the sliding door or the door frame on the side facing the front stile of the sliding door, and a tape-shaped drive spring that is attached to the door frame or the sliding door on the side opposite to the front stile of the sliding door. A drive drum is rotatably supported on a base plate and has a drive spring wound around its outer periphery from the other end, and a tape-shaped natural drive drum whose one end is connected to a sliding door or a door frame on the side opposite to the rear stile of the sliding door. A speed regulating spring, which is a contact type spiral spring and is set so that its tensile force is smaller than that of the drive spring and the difference between the two is larger than the frictional resistance of the sliding door, and a door frame on the side opposite to the rear stile of the sliding door. , or a speed regulating drum rotatably supported on a board attached to the sliding door and having a speed regulating spring wrapped around its outer periphery from the other end, a pivot shaft rotatably supported on the board, and a pivot drum rotatably supported on the board; A rotating arm coupled approximately vertically, a friction block movably guided by the rotating arm along its longitudinal direction, and a friction drum disposed coaxially with the rotating shaft and having an inner peripheral surface in sliding contact with the friction block. a centrifugal governor equipped with the same structure, a speed increaser that interconnects the rotating shaft and the governing drum of the centrifugal governor, and amplifies the rotational angular velocity of the governing drum and transmits it to the rotating shaft; It is characterized by having a one-way crack that connects the regulating drum to the centrifugal governor only when the regulating drum rotates in the direction of unwinding the regulating spring.

In addition to the configuration of the invention as set forth in claim 1, the invention set forth in claim 2 further comprises: a guide shoe is attached to the swing arm of the centrifugal governor so that its position in the longitudinal direction can be adjusted; The frictional resistance torque of the centrifugal speed governor can be adjusted by attaching a friction block biased in the direction of the rotation axis to the guide shoe so as to be movable along the longitudinal direction of the guide shoe. .

[For production]

In the sliding door closer according to the present invention configured as described above, when no external force acts on the sliding door, the sliding door is urged in the closing direction by the drive spring and in the opening direction by the regulating spring. However, since the tensile force of the drive spring is set to be greater than that of the regulating spring plus the frictional resistance of the sliding door, the sliding door is eventually biased in the closing direction, and the natural contact type Due to the nature of the spiral spring, this biasing force is approximately constant regardless of the position of the sliding door. Therefore, even when the sliding door is closed, the sliding door is firmly pressed against the door frame and is reliably closed.

When the sliding door is opened, the drive spring is unwound from the drive drum, and at the same time the regulating spring is wound around the regulating drum. At this time, due to the action of the one-way clutch, the speed governor drum idles relative to the speed increaser and the centrifugal speed governor. Therefore, the force applied to the hand opening the sliding door is the difference between the tensile forces of the flap, drive, and regulating spring plus the frictional resistance of the sliding door.

When you let go of your hand after straddling the rail of the sliding door, the sliding door is biased in the closing direction as described above. This biasing force is equal to the tensile force of the dowel drive spring minus the tensile force of the regulating spring and the frictional resistance of the sliding door.

As a result, the sliding door starts to move in the closing direction, the drive drum rotates in a direction to wind up the drive spring, and the regulating drum rotates in a direction to unwind the regulating spring.

At this time, the one-way clutch interconnects the governor drum and the speed increaser, so the rotation of the governor drum accompanying the movement of the sliding door is amplified and transmitted to the rotation shaft of the centrifugal governor, resulting in The centrifugal governor operates and frictional resistance torque acts on the governor drum.

The sliding door moves in the closing direction while unwinding the regulating spring that interconnects the sliding door and the door frame on the side facing the rear stile from the regulating drum, that is, while lengthening the regulating spring. The fact that frictional resistance torque acts on the speed control drum means that even if the speed control drum is installed on the sliding door side, or even if it is installed on the door frame side facing the rear stile, the speed control spring is It is inevitable that braking force will be applied to the sliding door through the Furthermore, this braking force is proportional to the rotational speed of the regulating drum, that is, the moving speed of the sliding door.

Therefore, the sliding door equipped with the closer according to the present invention is
Immediately after the sliding door starts moving in the closing direction, it begins to move at a constant velocity, and buffers the front stile of the sliding door and the door frame when the sliding door is closed.

According to the second aspect of the present invention, the degree of buffering when the sliding door is closed can be adjusted by adjusting the frictional resistance torque.

〔Example〕

An embodiment of the present invention will be described below with reference to the drawings.

In FIGS. 1 and 2, reference numeral 1 indicates a drive spring;
This drive spring 1 is a tape-shaped leaf spring called a so-called natural contact type spiral spring.

Such natural contact type spiral springs are well known and are used, for example, in camera suspension springs for television camera support stands in broadcasting stations.Since their characteristics are closely related to the characteristics of the present invention, they will be briefly described below. I will explain it to you.

A natural contact type spiral spring is a spring made by bending a tape-shaped spring plate so that each part in the length direction has a constant curvature. In this case, the spring plates are curled into contact with each other. As shown in FIG. 3, when a force P is applied to one end of this spring to pull it outward, the natural contact type spiral spring unwinds into a substantially straight line. At this time, a tensile force P is exerted to the outside as a reaction force, and this tensile force is expressed by the following equation (1).

p-Ebh /24 (1-1/111”)ρ
(1) However, E - modulus of longitudinal elasticity b - width of spring plate - thickness of spring plate m - Poisson's number ρ - radius of curvature of the leaf spring at the point at which it is unwound.

By the way, the only thing that changes on the right side of equation (1) is ρ, and this ρ is almost constant and does not change much unless the spring plate is wound extremely thickly, so the above tensile force P is determined by the unwinding. The length S1 of the straight line portion, which corresponds to the elongation in a tension coil spring, is approximately constant regardless of the value. That is, the spring constant of the natural contact type spiral spring is approximately zero.

Further, the above-mentioned tensile force P is due to the elastic energy released when the spring plate returns from the radius of curvature to ρ, so it is quite strong for a relatively compact spring. For example, b=13mm, h=0.37mm, ρ-2
Assuming that it is 5mm, the weight of P is 1kg.

As shown in FIGS. 1 and 2, one end of the drive spring 1 is provided with a connecting hole 2a having, for example, a U-shape in cross section and a potbellied shape.
The connecting body 2 with the opening is crimped. One end of the drive spring 1 is connected to either a sliding door or a door frame via the connecting body 2. In the embodiment shown in the fourth figure, the connecting hole 2a of the connecting body engages with a locking pin 4 with a flange fixed to the door frame 3 side, and the connecting body 2 and the locking pin 4 are connected to each other. One end of the drive spring 1 is locked to the door frame 3 through the door frame 3. The outer diameter of the flange of the locking pin 4 is set to be smaller than the opening of the large diameter part of the connecting hole 2a (FIG. 2) but larger than that of the small diameter part, and the tension of the drive spring 1 Since the small-diameter portion of the connecting hole 2a and the shaft portion of the locking pin 4 are engaged with each other by utilizing the above, the connecting body 2 will not be removed from the locking pin 4. Furthermore, a bent portion integrally formed at one end (the left side in FIGS. 1 and 2) of the connecting body 2 serves as an operating piece 2b.
A finger or the like is hooked onto this operation piece 2b and the drive spring 1 is operated to be pulled out from the case 5.

Further, the bent portion at the other end of the connecting body 2 serves as a stopper piece 2c, which prevents the connecting body 2 from being drawn into the case 5.

On the other hand, the other end of the drive spring 1 is wound around the outer periphery of a cup-shaped drive drum 6 with a flange and inner tube, as shown in FIGS. 1 and 2. In order to restrain the other end of the drive spring 1 and the drive drum 6, the other end of the drive spring 1 is bent inward at right angles, and this bent portion is formed along the generatrix on the outer peripheral surface of the drive drum 6. It is inserted into a locking slit (not shown) that is opened. Note that the dimension of the bent portion in the length direction of the drive spring 1 is set to be slightly smaller than the thickness of the outer peripheral portion of the drive drum 6. Also,
The radius of curvature given to the drive spring 1 in advance (see Figure 3)
is set smaller than the outer diameter of the drive drum 6. With the above configuration, the other end of the drive tape 1 is firmly held on the outer periphery of the drive drum 6 unless the drive spring 1 is completely unwound from the drive drum 6.

On the other hand, as shown in FIGS. 1 and 2, the case 5
has, for example, an elongated rectangular substrate 5a and a box-like lid 5b with one side open.
For example, it is screwed to the substrate 5a by a plurality of screws passing through the side surface of the lid 5b.

A support shaft 7 is vertically provided at one end of the inner surface of the substrate 5a (on the left side of the upper surface in FIGS. 1 and 2), and a bearing 8 made of, for example, a 21-dollar bearing is mounted on the support shaft 7. The drive drum 6 is rotatably supported through the .

Further, a speed governor drum and a centrifugal speed governor, which will be described later, are attached to the other end of the inner surface of the substrate 5a via a machine frame 9.

In the embodiments shown in FIGS. 1, 2, and 5, the machine frame 9 includes a substantially rectangular base plate 9a, a top plate 9b of the same shape, and four corner portions of the top and base plates 9a and 9b. It has four flange-attached supports 9c, 9c that are connected integrally and parallel to each other, for example, 4 of the base plate 9a.
Using female screw holes (not shown) formed in the center of each side,
It is fixed to the base fN5a of the case 5 from the underside with a countersunk screw via a spacer washer 11 (FIG. 2).

A pinion 12, which serves as a pivot of the centrifugal governor, is rotatably supported in the center of the machine frame 9.

In addition, a pair of idle gears 13°13 are rotatably supported at symmetrical positions with respect to the pinion 12 on the base plate 9a of the machine frame, and these idle gears 1B, 1B are
It meshes with the pinion 12 so as to sandwich it therebetween.

Furthermore, as shown in FIG. 2, the pinion shaft top plate 9
In a portion near b, a cup-shaped friction drum 14 is rotatably supported with its opening facing the base plate 9a. and,
A flanged ring-shaped regulating drum 15 is slidably fitted on the outside of the friction drum 14.

A regulating spring 16 made of a natural contact type spiral spring similar to the drive spring 1 is wound around the outer circumference of the regulating drum 15 in the same manner as the driving spring 1 of the driving drum 6. The connecting body 2 is coupled to one end portion of the lid body 5b which is led out of the case through a slit opened therein.

The specifications such as the width and thickness of the regulating spring 16 are such that the tensile force P of the regulating spring 16 (see Fig. 3) is smaller than that of the drive spring 1, and the difference between the two is the same as that of the sliding door described later. It is set to be larger than the frictional resistance value.

Note that the drive spring 1 and speed regulating spring 1 in the case 5
6 and 6, even if the winding directions with respect to the respective rotating shafts are opposite to each other as in the illustrated embodiment, or even if they are in the same direction (not shown), the two can be unwound. When moving, one end (outer end) of each of the connecting bodies 2 attached thereto is set so as to be pulled out in opposite directions with respect to the case 5.

On the other hand, a ring-shaped internal gear 17 is integrally connected to the opening edge of the friction drum 14 . Of these, 17 mm cars
As shown in FIG. 6, a short cylindrical portion is coaxially and integrally formed, and by press-fitting this short cylindrical portion into the opening edge of the friction drum 14, the friction drum i4 and the internal teeth are connected. The gear 17 is integrally connected.

The internal gear 17 meshes with the idle gears 1B and 13 from the outside, as shown in FIGS. 1, 2, and 5.

Further, as shown in FIGS. 2 and 6, the outer peripheral edge of the internal gear 17 extends outward from the friction drum 14 to form a flange, and this flange is connected to the regulating drum 15.
The downward movement is regulated in the drawing. Incidentally, a protruding strip 10 (see FIG. 6) is formed on one opening edge of the regulating drum 15, and the engagement of this protruding strip 10 with the top plate 9b of the machine frame causes the regulating drum 15 to open. upward movement is restricted in the drawing.

On the other hand, one of the flanges formed on the outer periphery of the regulating drum (lower in FIGS. 2 and 6) is thicker than the other, and the surface of this thick flange that comes into sliding contact with the internal gear 17 is As shown in FIGS. 2, 5, and 6, the clutch groove 18 is formed so that the projection in the direction of the rotational axis of the speed regulating drum is approximately triangular, and the clutch groove 18 communicates with the inner hole of the speed regulating drum 15. A clutch ball 19 is housed in this clutch mechanism 18. In the illustrated embodiment, a pair of clutch grooves 18 are provided symmetrically with respect to the rotational axis. As shown in FIG. 5, the projected shape of each clutch groove 18 in the direction of the rotational axis is such that the regulating drum 15 rotates clockwise relative to the friction drum 14 that is integrated with the internal gear 17. In other words, when the regulating spring 16 rotates in the winding direction, the clutch ball 19 is rotated in the clutch groove 1.
It is set to float at 8. However, when the regulating drum 15 rotates in the opposite direction, that is, in the direction of unwinding the regulating spring 16, the clutch ball 19 is sandwiched between the outer peripheral surface of the friction drum 14 and the inner surface of the clutch groove 18. The regulating drum 15 and the friction drum 14 are integrally connected via the clutch ball 19. That is, the outer peripheral surface of the friction drum 14, the clutch groove 18, and the clutch ball 19 constitute a one-way clutch.

On the other hand, as shown in FIGS. 1 and 2, the portion of the pinion shaft from the pinion 12 to the rotational support portion of the friction drum 14 has an irregular cross section with a rectangular cross section, for example. A pair of pivoting arms 21.21 are provided vertically.

As shown in FIGS. 7 and 8, this rotating arm 21 is
For example, it is a stepped plate-like body, and its base (in the illustrated embodiment, the middle of the pair of rotating arms 21, 21) is coaxially formed with a modified hole that fits into the modified cross-section of the pinion shaft. A boss portion 22 is integrally connected, and the boss portion 22 is fitted to the irregular cross section of the pinion shaft, and a set screw (not shown) is screwed into a female threaded hole 22a (FIG. 8) formed in the boss portion 22. It is connected perpendicularly to the pinion shaft.

A friction block 23 is guided in each pivot arm 21 so as to be movable in the longitudinal direction. In the illustrated embodiment, each pivot arm 21 has a guide slit 21a along its length.
(Fig. 7) is formed, while the friction block 23
As shown in FIGS. 1 and 2, it is composed of an integral cylindrical body that is swaged together via a short connecting shaft with an oval cross section, and the outer plane part of the connecting shaft is connected to a guide slit 21a.
It is supported and guided by the pivot arm 21 by slidingly engaging with the edge forming the pivot arm 21 .

Further, a return spring 24 as a tension coil spring is stretched between the friction block 23 and the base of the swing arm 21, and the elasticity of the return spring 24 causes the friction block to
3 is biased in the pinion axial direction, but since the friction block 23 is locked to the stepped portion of the swing arm 21, the friction block 23 maintains the illustrated position in a quasi-static state.

At this time, a constant gap is maintained between the friction block 23 and the inner peripheral surface of the friction drum 14.

The outer end of each friction block 23 facing the N friction drum 14 is desirably formed to have the same curvature so that it can come into surface contact with the inner peripheral surface of the friction drum 14, as shown in FIG.

The pinion shaft, the rotating arm 21, the friction block 23, and the friction drum 14 constitute a known centrifugal speed governor.

As shown in FIG. 4, in the sliding door closer according to one embodiment of the invention as set forth above, the case and the like are attached to the sliding door 25 by, for example, screws. At this time, the case 5 is attached to the sliding door 25 so that the drive spring 1 comes out to the front stile side of the sliding door 25, that is, to the front side (left side in FIG. 4) when the sliding door moves in the closing direction. Then, as described above, the regulating spring 16 comes out on the side opposite to the drive spring 1, that is, on the rear stile side.

Therefore, as shown in FIG. 4, the drive spring 1 is pulled out from the case 5, and the connecting body 2 is pulled into the locking pin 4 provided on one door frame 3 on the side facing the front stile of the sliding door. Multiply. Similarly, one end of the regulating spring 16 is pulled out in the opposite direction to the drive spring 1, and the connecting body 2 is hooked on the locking pin 4 provided on the other door frame 3. In addition, in FIG. 4, the reference numeral 26 indicates another sliding door that is different from the sliding door 25 to which the case 5 is attached.

Attach the case 5 to the sliding door 25 as described above, and press the drive spring 1.
As a result of the regulating spring 16 being hung between the front and rear door frames, the sliding door 25 is pulled from the front and rear by the tension of these springs. However, when the tensile force of the drive spring 1 is P, that of the regulating spring 16 is P2, and the frictional resistance of the sliding door is F, as mentioned above, Pl-P2>F, so no external force is applied to the sliding door. Sometimes, the front stile of the sliding door 25 is pressed against the front door frame 3, so that the sliding door 25 is stably held in a closed state.

Therefore, when opening the sliding door 25 from the door closed state shown in FIG. 4, the sliding door 25 moves to the right in FIG.
The drive spring 1 is relatively pulled out from the case 5, and
The regulating spring 16 is wound around the regulating drum 15. At this time, the governor drum 15 rotates counterclockwise in FIG. 2, so the one-way clutch installed between the friction drum 14 and the governor drum 15 does not operate, and the governor system does not operate. The regulating drum 15 is in sliding contact with the outer peripheral surface of the friction drum 14 and rotates while winding the regulating spring 16. Therefore, the load applied to the finger or the like that opens the sliding door is the difference between the tensile forces of the drive spring 1 and the regulating spring 16 plus the frictional resistance of the sliding door.

When the sliding door is released after stepping over the threshold or the rail of the door wheel of the sliding door, the driving spring 1 exerts a pulling force on the sliding door 25 via the driving drum 6 and the base plate 5a, despite the pulling force in the opposite direction of the regulating spring 16. and begin to move it to the left in Figure 4. Then, the speed governor drum 15 rotates clockwise in FIG.
4 are integrally connected.

Therefore, as the sliding door moves in the closing direction, the internal gear 17 integrated with the friction drum rotates counterclockwise in FIG.
In the illustrated embodiment, the pinion 12 rotates at a rotational speed approximately 10 times that of the internal gear 17. Then, the friction block 23.23 carried on the tip of the swing arm 21
However, due to the centrifugal force and against the elasticity of the return spring 24, it moves from the outside and the tip comes into sliding contact with the inner circumferential surface of the friction drum 14, and as a result, the sliding door 26 is braked.

As is well known, when such a centrifugal speed governor is driven by a constant tensile force of the drive spring 1 according to the present invention, the sliding door 25 immediately begins to run at a constant speed after a transition period at the beginning of running.

At this time, the force p with which the friction block 23 is pressed against the inner peripheral surface of the friction drum 14 is expressed by the following (2).

p-mr ω -k(d + d) (2) O where, m: Mass of friction block 23; o: Distance between center of gravity of friction block 23 and axis of pinion 12 ω: Angular velocity of swing arm 21 k: Return spring Spring constant do of 24: Initial charge amount d of return spring 24: Swivel arm 2
The amount of gap between the friction block 23 and the inner circumferential surface of the friction drum 14 when the friction drum 1 is at rest.

Frictional torque is generated in the pinion 12 by the above p, and this frictional torque follows the speed increaser consisting of the internal gear 17 and the pinion 12 in the opposite direction, is amplified, and is transmitted to the speed control drum 15. Since the drum 15 rotates at a constant angular velocity, that is, with zero acceleration, the following equation (3) holds true.

2, czRN (mr −k (do+d)1ρ −= (P, −P2−F) (3) However, μ
: Friction coefficient R between the friction block 23 and the friction drum 14 : Radius N of the inner peripheral surface of the friction drum 14 : Speed increase Pl of the internal gear 17 and pinion 12 : Tensile force P2 of the drive spring 1 ::J! The tensile force F of the J-speed spring 16 is the frictional resistance of the sliding door.

From equation (3), on the other hand, if the speed of the sliding door is V, as is clear from equation (5), assuming that the resistance F of the sliding door is constant, the speed V of the sliding door is curvature radius at the point of unwinding or curling), and as mentioned above, ρ is almost constant, so
■ is also almost constant. Therefore, the sliding door 12 advances in the closing direction at approximately the same speed, and when the stile of the sliding door comes into contact with the door frame 3, the sliding door 21 stops without impact. The choice of whether to close the sliding door with a sharp smack or a gentle thud depends on the frictional resistance F of the sliding door, as described in (5) above.
) This is possible by appropriately setting the values of various parameters on the right side of the equation. Specifically, the frictional resistance F of the sliding door
Manufacturers can prepare several types of closers depending on the situation.

Even when the sliding door is closed, the drive spring 1 moves the sliding door to the door frame 3.
Since the sliding door is biased in the direction of pressing, the closed state of the sliding door is maintained stably.

If it is necessary to keep the sliding door open for some reason, the connecting body 2 (see FIG. 4) connected to one end of the drive spring 1 can be removed from the locking pin 4.

FIG. 9 shows a sliding door closer according to another embodiment of the invention as set forth in claim 1, in which one end of the driving spring 1 of the closer has a width over a constant length at a predetermined position in the longitudinal direction. is narrowed to form a weakened portion 1a.

The distance of the weakened portion 1a from the connecting body 2 in the length direction of the drive spring 1 is, for example, approximately 10 to 20 mm when the sliding door is in the closed position.
The left end of this weakened portion in FIG. 9 shall be set so that when it comes to this side cm, the left end of this weakened portion will be curled and contracted.

In the sliding door closer configured as described above, when the sliding door advances in the closing direction and reaches a position where the weakened portion 1a begins to curl, the force of the driving spring 1 to pull the sliding door 25 decreases, and the width of the driving spring 1 decreases. (see equation (1) above). on the other hand,
Since the centrifugal governor still exhibits frictional resistance torque due to inertia, the sliding door is now further braked and its moving speed is reduced.

After that, the centrifugal speed governor quickly shifts to constant velocity interlocking according to the tensile force of the weakened part 1a, but as is clear from equation (5), the speed of the new sliding door changes as if the frictional resistance of the sliding door had increased. The same slow speed as . Then, the stile of the sliding door can be brought into contact with the door frame 3 at the same speed, or,
The width of the drive spring 1 may return to its original width just before the stile contacts the door frame 3. In the latter case, the sliding door closes in a transient state where it is trying to increase its speed, so the impact is small, and the force that attracts the door frame to the door frame is large, so the closed state of the sliding door is stabilized. There are advantages.

In the embodiment shown in FIG. 9, the width of the drive spring is changed rapidly, but it goes without saying that it may be changed continuously little by little.

10 to 12 show a sliding door closer according to an embodiment of the invention as set forth in claim 2, and this closer is configured to be able to adjust the frictional resistance torque of a centrifugal governor.

That is, in the sliding door closers shown in these figures, the pivot shaft 12 of the centrifugal governor is rotatably supported by the machine frame 9, as described above, but each of the sliding door closers has a bottom. The cup-shaped regulating drum 15 and friction drum 14 are coaxially supported by the rotating shaft 12, and a one-way clutch is disposed between these bottom plates.

A clutch plate 28 having a clutch notch 27 (FIG. 10) is screwed to the regulating drum 15 side.

Furthermore, when the sliding door moves in the closing direction, the rotation of the friction drum 14, which is integrally connected to the speed control drum 15 via the one-way clutch, is controlled by the rotation of the large gear 29 carved on the flange of the friction drum. A small gear 31 supported on a shaft other than the shaft 12
, a first idle gear 32 that is coaxially and integrally connected to this small gear, and a second idle gear 33 that is coaxial with the rotation axis (
The speed is increased and transmitted to the rotating shaft 12 via the rotation shaft 12 (FIG. 11).

The irregular cross section of the pivot shaft with the flange 12a (see FIG. 11) has an oval cross section (see FIG. 12), and a trough-like pivot arm 21 with a U-shaped cross section and an opening of the same shape on the bottom surface. is fitted and fixed, for example, with an adhesive applied between the flange portion 12a and the flange portion 12a.

A guide shoe 34 is movably guided at the tip (outer end) of the swing arm 21 in the radial direction of the friction drum 14.
As shown in FIG. 11, the legs 34a of each guide shoe 34 that penetrate the bottom plate of the swing arm and protrude toward the second idle gear 33 are perpendicularly penetrated through the swing shaft 12, and rotate with the swing shaft 12. It is threadedly engaged with the tip of a threaded rod 36 that can be fitted together and prevented from being pulled out by a stopper shaft 35.35. Both ends of the threaded rod 36 are threaded in opposite directions, and one side of the threaded rod 36 has a linear or cross-shaped slit (not shown) formed only on the end surface for engagement with the tip of the screwdriver. By rotating the screw rods 36 in unison, the positions of the pair of guide shoes 34, 34 in the longitudinal direction of the pivoting arms can be symmetrically changed.

A guide rod 23a integrated with the friction block 23 is movably guided in each guide shoe 34 in the longitudinal direction of the swing arm 21, and a spring retainer is engaged with a stop shaft 35 fitted to the guide rod 23a. A return spring 24 as a compression coil spring is elastically mounted between the plate 37 and the guide shoe 34. The friction block 23 is urged in the direction of the pivot shaft 12 by the elasticity of the return spring 24.

With the above configuration, the frictional resistance torque of the centrifugal governor is adjusted by rotating the screw rod 36 with a screwdriver or the like to symmetrically change the position of the guide shoe 34, 34 in the longitudinal direction of the swing arm. be able to. For example, when the guide shoes 34 and 34 are adjusted in a direction in which they approach each other, r in the equation (5). As d decreases and d increases, these values act synergistically to increase the speed of the sliding door.

That is, the frictional resistance torque of the centrifugal governor is reduced.

By adjusting the frictional resistance torque, it becomes possible to adjust the speed in the closing direction of the sliding door and to adjust the speed of the sliding door in response to changes in the frictional resistance of the sliding door due to long-term use.

〔Effect of the invention〕

As is clear from the above description, in the present invention, the sliding door is pulled in the closing direction by the force of a drive spring made of a natural contact type spiral spring, and braking is applied by a centrifugal governor.
In addition to achieving the basic objective of the present invention, which is to provide a sliding door closer, the closer operates reliably, is compact and lightweight.

In addition, since rotational motion occurs naturally in the regulating drum when the regulating spring is unwound as well as when it is rolled up, there is no need for a mechanism to convert the linear motion of the sliding door into the rotational motion of the governor. The structure is simple and can be manufactured at low cost.

Furthermore, since the frictional force that generates the braking force does not change depending on temperature, there is no need in principle for a mechanism to adjust the orifice opening through which hydraulic oil passes, unlike in conventional closers using oil dampers, and maintenance management is easy. Not only is this easier, but the structure is also simpler.

In addition, when it is not needed, it can be removed at any time by touching the engagement between the coupling body at one end of the drive spring and speed regulating spring and the locking pin. It has various effects such as being easy to attach to sliding doors.

In the above-mentioned embodiment, the case was installed protruding from the surface of the sliding door or the door frame, but the case was omitted and the board and machine frame were built into the sliding door, and one end of the drive and regulating spring was attached to the door of the sliding door. Of course, it is also possible to pull it out from the joint edge with the frame, and in this case, the locking pin that engages with the connecting body is housed in a recess dug into the door frame.

[Brief explanation of the drawing]

FIG. 1 is a partially sectional plan view of a sliding door closer according to an embodiment of the invention as set forth in claim 1, FIG. 2 is a sectional view thereof, and FIG.
The figure is a diagram to explain a natural contact type spiral spring, Figure 4 is a partial front view of a sliding door with a closer attached, and Figure 5 is a diagram of a sliding door equipped with a closer.
6 is a partially enlarged sectional view of the speed governor of the closer shown in FIG. 2; FIG. 7 is a plan view of the swing arm; 8 is a side view thereof, FIG. 9 is a side view of a sliding door closer according to another embodiment of the invention set forth in claim 1, and FIG. 10 is a side view of a sliding door closer according to an embodiment of the invention set forth in claim 2. This is a partially sectional plan view of the closer, showing only the speed governor part, and FIG. 11 is similar to FIG. 10 XI.
12 is a partially sectional plan view of the centrifugal governor. DESCRIPTION OF SYMBOLS 1... Drive spring, 6... Drive drum, 9... Machine frame, 12... Rotating shaft (pinion), 14... Friction drum, 15... Governor drum, 16... Regulating spring, 17
...Internal gear, 18...Clutch groove, 19...Clutch ball, 21...Swivel arm, 23...Friction block, 24...Return spring, 25.26...Sliding door. Figure 6 Figure 7

Claims (1)

[Scope of Claims] 1. A tape-shaped drive spring made of a natural contact type spiral spring, one end of which is connected to the sliding door or the door frame on the side facing the front stile of the sliding door, and the side facing the front stile of the sliding door. A drive drum rotatably supported on a board attached to the door frame or sliding door, and having a drive spring wound around its outer periphery from the other end, and a door frame with one end facing the sliding door or the rear stile of the sliding door. A tape-shaped natural contact type spiral spring connected to a regulating spring whose tensile force is smaller than that of the driving spring and whose difference is larger than the frictional resistance of the sliding door, and a regulating spring connected to the rear of the sliding door. It is rotatably supported on the door frame on the side facing the stile or on a board attached to the sliding door, and includes a speed regulating drum with a speed regulating spring wound around the outer periphery from the other end, and a speed regulating drum rotatably supported on the board. a pivot shaft, a pivot arm connected substantially perpendicularly to the pivot shaft, a friction block movably guided along the longitudinal direction of the pivot arm, and a friction block disposed coaxially with the pivot shaft, the inner circumferential surface of which is disposed coaxially with the pivot arm; A centrifugal governor equipped with a friction drum that makes sliding contact with a friction block, a rotating shaft of this centrifugal governor, and a governing drum are interconnected, and the rotating angular velocity of the governing drum is amplified and transmitted to the rotating shaft. A sliding door closer comprising a speed increaser and a one-way clutch that connects the speed governor to the centrifugal speed governor only when the speed governor drum rotates in a direction to unwind and unwind a speed governor. 2. A tape-shaped drive spring consisting of a natural contact type spiral spring, one end of which is connected to the sliding door or the door frame on the side facing the front stile of the sliding door, and a tape-shaped drive spring on the side opposite to the front stile of the sliding door or the sliding door. A drive drum that is rotatably supported by an attached board and has a drive spring wound around its outer periphery from the other end, and a tape-shaped drive drum that has one end connected to a sliding door or a door frame on the side opposite to the rear stile of the sliding door. A natural contact type spiral spring with a speed regulating spring whose tensile force is smaller than that of the drive spring and whose difference is greater than the frictional resistance of the sliding door, and a speed regulating spring on the side facing the rear stile of the sliding door. A speed regulating drum rotatably supported on a base plate attached to a door frame or a sliding door and having a speed regulating spring wound around its outer periphery from the other end; a pivot shaft rotatably supported on the base plate; a pivoting arm coupled substantially perpendicularly to the axis; a guide shoe movably guided along the longitudinal direction of the pivoting arm; a guide shoe movably guided along the longitudinal direction of the pivoting arm; a centrifugal governor comprising a friction block biased in the direction of the rotation axis, and a friction drum disposed coaxially with the rotation axis and having an inner peripheral surface in sliding contact with the friction block;
A speed increaser that interconnects the rotating shaft and the governing drum of this centrifugal governor, amplifies the rotating angular velocity of the governing drum and transmits it to the rotating shaft, and a direction in which the governing drum unwinds the governing spring. 1. A sliding door closer comprising a one-way clutch that connects a speed governor drum to a centrifugal speed governor only when the speed governor rotates.