JPH058313B2 - - Google Patents

Description

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

[Conventional technology and problems]

Closers for revolving doors that are attached to door frames via hinges have been in practical use for a long time, and it is no exaggeration to say that the common name "door closer" refers to the closer for revolving doors.

On the other hand, guided by rails, door wheels, etc.
Sliding doors that move along a plane parallel to the door surface are more commonly used than revolving doors, but it is no exaggeration to say that sliding door closers are not in practical use, at least at present.

This is because the inventors were aware of the fact that a sliding door closer that combined a tension coil spring and an air damper was commercially available, and when they actually purchased and tried it, they found that the spring was It was weak and could not close the sliding door reliably and its operation was uncertain, and on the other hand, I could easily predict that if the spring was made stronger, the impact when the sliding door closed would be greater, so I decided to purchase it in the end. However, I have had the experience of removing it from a sliding door.

Furthermore, a sliding door closer has been proposed in which the link mechanism of a door closer for a revolving door is modified for use with a sliding door so as to be capable of linear movement. However, although this door closer for sliding doors can be expected to operate reliably, it is too large in weight and size, and is generally not suitable for simple sliding doors.

[Purpose of the invention]

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a sliding door closer that is compact and simple in structure and that operates reliably.

[Means for solving problems]

In order to achieve the above purpose, the first
The invention consists of a tape-shaped drive spring having one end connected to a sliding door or door frame, and a tape-shaped drive spring rotatably supported on the door frame or a machine frame attached to the sliding door, and a tape-shaped drive spring having one end connected to a sliding door or a door frame. A drive drum with a drive spring wound around it from the other end, a pivot shaft rotatably supported on the machine frame, a pivot arm connected almost perpendicularly to the pivot shaft, and a pivot arm that moves along its longitudinal direction. A centrifugal speed governor is provided with a friction block that is freely guided, and a friction drum that is arranged coaxially with the pivot shaft and whose inner circumferential surface is in sliding contact with the friction block; A speed increaser that is interconnected and amplifies the rotational angular velocity of the drive drum and transmits it to the rotating shaft, and a centrifugal governor that connects the drive drum only when the drive drum rotates in the direction to wind up the drive spring. It is characterized by having a one-way clutch.

Further, the second invention includes a tape-shaped drive spring which is made of a natural contact type spiral spring, one end of which is connected to a sliding door or a door frame, and a tape-shaped drive spring which is rotatably supported by a door frame or a machine frame attached to the sliding door. , a drive drum with a drive spring wound around its outer periphery from the other end, a pivot shaft rotatably supported on the machine frame, a pivot arm connected almost perpendicularly to the pivot shaft, and a pivot arm connected to the pivot arm in its longitudinal direction. a guide shoe whose position can be adjusted in the
A friction block is movably guided by the guide shoe along the longitudinal direction of the swing arm and is biased in the direction of the swing axis, and a friction block is disposed coaxially with the swing axis and whose inner circumferential surface is in sliding contact with the friction block. A centrifugal governor equipped with a drum, a speed increaser that interconnects the rotary shaft of the centrifugal governor and the drive drum, amplifies the rotational angular velocity of the drive drum and transmits it to the rotary shaft, and the drive drum It is characterized by having a one-way clutch that connects the drive drum to the centrifugal governor only when the drive spring rotates in the winding direction.

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

[Embodiment of the first invention according to the present application] In FIGS. 1 and 2, reference numeral 1 indicates a drive spring, and 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.

Natural contact type spiral springs are made of tape-shaped spring plates,
It is a spring that is bent and formed so that each part in the length direction has a constant curvature, and in its natural state, the spring plates are curled and contracted so that they are in contact with each other, as shown on the left side of Figure 3. ing. 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 as the following equation (1).

P=Ebh ³ /24 (1-1/m ² )ρ ² (1) However, E: Modulus of longitudinal elasticity b: Width of spring plate h: Thickness of spring plate m: Poisson's number ρ: At the point of unwinding Let the radius of curvature of the leaf spring be.

By the way, the only thing that changes on the right side of equation (1) is ρ, and since ρ is almost constant and does not change much unless the spring plate is rolled extremely thickly, the above tensile force P is determined by the unwinding. The length S 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.

In addition, the above tensile force P is such that the spring plate has a radius of curvature ∞
Since this is due to the elastic energy released when returning from ρ to ρ, it becomes quite strong even though it is a relatively compact spring. For example, b=8mm, h=
Assuming 0.5mm and ρ=60mm, P≒1Kg weight.

At one end of the drive spring 1, there are shown in FIGS.
As shown in the figure, a connecting body 2 having, for example, a U-shaped cross section and a potbell-shaped connecting hole 2a 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 come off from the locking pin 4. Furthermore,
A bent portion integrally formed at one end (the right side in FIGS. 1 and 2) of the connecting body 2 serves as an operating piece 2b, and by hooking a finger or the like onto this operating piece 2b, the drive spring can be activated. 1 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 peripheral surface of a flanged ring-shaped drive drum 6, 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. and is inserted into an open locking slit (not shown). Note that the dimension of the bent portion in the length direction of the drive spring 1 is the same as that of the drive drum 6.
Set the thickness to be slightly smaller than the thickness of the outer periphery. Further, the radius of curvature r (see FIG. 3) given in advance to the drive spring 1 is set to be smaller than the outer diameter of the drive drum 6. By configuring as described above, unless the drive spring 1 is completely unwound from the drive drum 6, the other end of the drive tape 1 is connected to the drive drum 6.
It is firmly held on the outer periphery of the

The drive drum 6 is rotatably supported by a machine frame 7 attached to the other of the sliding door or the door frame (the sliding door in the embodiment shown in the fourth figure).

In the embodiments shown in FIGS. 1, 2, and 5, the machine frame 7 includes a substantially rectangular bottom plate 7a, a top plate 7b of the same shape, and four parts of these top and bottom plates 7a and 7b.
Four flange-attached supports 7c, 7c connect these integrally and parallel to each other at the corners.
For example, by using female screw holes (not shown) formed in the center of each of the four sides of the base plate 7a, insert a countersunk screw into the base plate 5a of the case 5 from the bottom side of the base plate 5a through the spacer washer 8 (Fig. 2). Fixed to call by

Incidentally, the case 5 includes a board 5a and a lid 5b that covers the machine frame 7 fixed to the board 5a.
b is the substrate 5a as shown in FIGS. 1 and 2.
It is screwed to the substrate 5a by a plurality of screws passing through the side surface of the lid 5b, for example, through connecting blocks 5c, 5c protruding from the upper surface of the lid 5b.

On the other hand, as shown in FIGS. 1, 2, and 5, a pinion 9, which serves as a pivot shaft of the centrifugal governor, is rotatably supported in the center of the machine frame 7.

Further, a pair of idle gears 11, 11 are located at symmetrical positions with respect to the pinion 9 on the main plate 7a of the machine frame.
is rotatably supported, and these idle gears 11, 11 are engaged with the pinion 9 so as to sandwich it therebetween.

Furthermore, as shown in FIG. 2, a cup-shaped friction drum 12 is rotatably supported on a portion of the pinion shaft near the top plate 7b with its opening facing toward the base plate 7a. The drive drum 6 is slidably fitted on the outside of the friction drum 12.

A ring-shaped internal gear 13 is integrally connected to the opening edge of the friction drum 12. As shown in FIG. 6, this internal gear wheel 13 is coaxially and integrally formed with a short cylindrical portion, and by press-fitting this short cylindrical portion into the opening edge of the friction drum 12, for example, The friction drum 12 and the internal gear wheel 13 are integrally connected.

As shown in FIG. 1, FIG. 2, and FIG.
are engaged from the outside.

Further, as shown in FIGS. 2 and 6, the outer peripheral edge of the internal gear 13 extends outward from the friction drum 12 to form a flange. It restricts downward movement. Incidentally, a protruding strip 10 (see FIG. 6) is formed on one opening edge of the drive drum 6, and the engagement of this protruding strip 10 with the top plate 7b of the machine frame causes the drive drum 6 to move. Movement upward in the drawing is restricted.

On the other hand, one of the flanges formed on the outer periphery of the drive 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 13 As shown in FIGS. 2, 5 and 6, a clutch groove 14 is formed which has a substantially triangular projection in the direction of the rotational axis of the drive drum and communicates with the inner hole of the drive drum 6. A clutch ball 15 is housed in this clutch groove 14. In the illustrated embodiment, the clutch grooves 14 are provided in pairs symmetrically with respect to the axis of rotation. The projected shape of each clutch groove 14 in the direction of the rotational axis is as shown in FIG. In other words, when the drive spring 1 rotates in the direction in which it is unwound, the clutch ball 15 is moved into the clutch groove 14.
It is set to move around inside. However,
When the drive drum 6 rotates in the opposite direction, that is, in the direction to wind up the drive spring 1, the clutch ball 15 is sandwiched between the outer peripheral surface of the friction drum 12 and the inner surface of the clutch groove 14, Drive drum 6 and friction drum 12 via ball 15
are integrally connected. That is, the outer peripheral surface of the friction drum 2, the clutch groove 14, and the clutch ball 15 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 9 to the rotational support portion of the friction drum 12 has an irregular cross section with a rectangular cross section, for example. A pair of swing arms 16, 16 are vertically provided.

As shown in FIGS. 7 and 8, this swing arm 16 is, for example, a stepped plate-shaped body, and its base (in the illustrated embodiment, the middle of the pair of swing arms 16, 16) has a A boss portion 17 coaxially formed with a modified hole that fits into the modified cross section of the pinion shaft is integrally connected. It is connected perpendicularly to the pinion shaft by screwing a set screw (not shown) into the formed female screw hole 17a (FIG. 8).

A friction block 18 is guided in each pivot arm 16 so as to be movable in the longitudinal direction. In the illustrated embodiment, each pivot arm 16 is formed with a guide slit 16a (FIG. 7) along its length, while the friction block 18 is formed as shown in FIGS. , consisting of a pair of cylindrical bodies crimped together via a short connecting shaft with an oval cross section,
Guide slit 16 connects the outer surface flat part of the connecting shaft.
It is supported and guided by the pivoting arm 16 by slidingly engaging with the edge forming the section a.

A return spring 1 as a tension coil spring is also provided between the friction block 18 and the base of the swing arm 16.
9 is tensioned, and the friction block 18 is biased in the pinion axial direction by the elasticity of the return spring 19. However, since the friction block 18 is locked to the stepped portion of the swing arm 16, it remains semi-static. In normal conditions, the friction block 18 remains in the position shown. At this time, it is assumed that a constant gap is maintained between the friction block 18 and the inner peripheral surface of the friction drum 12.
The outer end of each friction block 18 facing the friction drum 12 is desirably formed to have the same curvature so that it can come into surface contact with the inner circumferential surface of the friction drum 12, as shown in FIG.

The above pinion shaft, rotating arm 16, friction block 1
8 and the friction drum 12 constitute a known centrifugal governor.

[Function] As shown in FIG. 4, the sliding door closer according to the embodiment of the first invention of the present application configured as described above connects, for example, one end of the drive spring 1 with the connecting body 2 and the locking pin 4. The case 5 is secured to the door frame 3 through the door frame 3, and the case 5 is secured to the sliding door 21 by screws, for example. Alternatively, contrary to Fig. 4, place the case 5 on the door frame 3 side,
One end of the drive spring 1 pulled out from the case 5 may be attached to the sliding door 21 side.

Therefore, the sliding door 2
1, the sliding door 21 moves to the left, so the drive spring 1 is relatively pulled out from the case 5. At this time, the drive drum 6
rotates clockwise in FIG. 1 and counterclockwise in FIG. Rotate while unwinding. In reality, the friction drum 12 is dragged by the drive drum 6 due to friction, and in some cases, the centrifugal governor operates and brakes the friction drum 12. In any case, when the drive drum 6 rotates clockwise in FIG. 1, the frictional resistance of the drive drum 6 does not exceed the frictional torque between the drive drum 6 and the friction drum 12. Therefore, the load applied to the finger, etc. that opens the sliding door is the sum of the tensile force exerted by the drive spring 1, the frictional resistance of the sliding door, and the frictional torque of the drive drum 6 divided by ρ in equation (1) above. becomes.

When the sliding door is released after stepping over the threshold or the rail of the door wheel of the sliding door, the drive spring 1 exerts an external force P on the sliding door 21 via the drive drum 6 and the machine frame 7, and begins to move it in the direction of the door frame 3. Then, the drive drum 6 rotates counterclockwise in FIG. 1 and clockwise in FIG. The driving drum 6 and the friction drum 12 are interposed in between and integrally connected.

Therefore, as the sliding door moves in the closing direction, the internal gear wheel 13 integrated with the friction drum rotates clockwise in FIG. 5, and this rotation is transmitted to the pinion 9 via the idle gear 11. In the illustrated embodiment, the pinion 9 rotates at a rotational speed approximately 10 times that of the internal toothed wheel 13. Then, the friction blocks 18, 18 supported at the tip of the swing arm 16 move outward due to the centrifugal force and against the elasticity of the return spring 19, and the tip ends inside the friction drum 12. It comes into sliding contact with the peripheral surface, and as a result, the sliding door 21 is braked.

As is well known, when such a centrifugal speed governor is driven by a constant tensile force P of the drive spring 1 according to the present invention, the sliding door 21 immediately begins to run at a constant speed after a transition period at the beginning of the drive.

At this time, the friction block 18 is connected to the friction drum 12.
The force p pressed against the inner circumferential surface of is expressed by the following equation (2).

p=mr ₀ ω ² −k(d ₀ +d) (2) where, m: Mass of friction block 18 r ₀ : Distance between center of gravity of friction block 18 and axis of pinion 9 ω: Angular velocity of swing arm 16 k: Spring constant of the return spring 19 d ₀ : Initial charge amount of the return spring 19 d : Amount of gap between the friction block 18 and the inner peripheral surface of the friction drum 12 when the swing arm 16 is stationary.

Friction torque is generated in the pinion 9 due to the above p, and this friction torque is transmitted between the internal gear wheel 13 and the pinion 9.
Following the speed increaser in the opposite direction, it is amplified and transmitted to the drive drum 6.
Since it rotates at a constant angular velocity, that is, with zero acceleration, the following equation (3) holds true.

2μRN {mr ₀ ω ² −k(d ₀ +d)}=ρ/2(P−F)(
3) However, μ: Friction coefficient between the friction block 18 and the friction drum 12 R: Radius of the inner peripheral surface of the friction drum 12 N: Speed increase ratio between the internal gear 13 and the pinion 9 F: Frictional resistance of the sliding door do.

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 a function of ρ (the radius of curvature at the point where the drive spring 1 is unrolled or contracted), and the Since ρ is almost constant as described above, V is also almost constant.
Therefore, the sliding door 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. By the way, the speed V of the sliding door is ρ=5cm, μ=0.2, R=2.5cm, P=1Kg
Weight, F = 0.5Kg Weight, weight of friction block 18: 5g
Assuming that the weight is r ₀ = 2 cm, N = 10, and k (d ₀ + d) = 25 g, V = approximately 30 cm/sec.

However, the choice of whether to close the sliding door with a sharp smack or with a gentle thud is...
This is possible by appropriately setting the values of various parameters on the right side of equation (5) above, depending on the frictional resistance F of the sliding door. Specifically, the manufacturer may prepare several types of closers depending on the frictional resistance F of the sliding door.

Even when the sliding door is closed, the driving spring 1 biases the sliding door in the direction of pressing it against the door frame 3, so that the closed state of the sliding door is maintained stably.

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

[Another embodiment of the first invention according to the present application] Fig. 9 shows a sliding door closer according to another embodiment of the first invention according to the present application, and one end of the drive spring 1 of this closer has a length At a predetermined position in the direction, the width is narrowed over a certain length to form a weak force portion 1a.

The distance of this weak force part 1a from the connecting body 2 in the length direction of the drive spring 1 is, for example, when the sliding door is approximately 10 to 20 cm before the closed position.
The left end in the figure shall be set so that it is curled.

[Effect]

In the sliding door closer configured as described above, when the sliding door advances in the closing direction and reaches a position where the weak force portion 1a begins to curl, the force of the driving spring 1 to pull the sliding door 21 decreases the width of the driving spring 1. (see equation (1) above). On the other hand, since the centrifugal governor exhibits the frictional resistance torque due to inertia,
At this point, the sliding door is further braked and its movement speed is reduced.

After that, the centrifugal speed governor quickly shifts to uniform motion according to the tensile force of the weak force 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 increases. The same slow speed will be achieved.
Then, the stile of the sliding door may be brought into contact with the door frame 3 at the same speed, or the width of the drive spring 1 may be returned to its original width just before the stile contacts the door frame 3. good. In the latter case, since the sliding door closes in a transient state where the sliding door tries to increase its speed, the impact is small, and the force that attracts the stile of the sliding door to the door frame is large, so the closed state of the sliding door is stabilized.
There is an advantage.

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.

[Embodiment of the second invention according to the present application] Figures 10 to 12 show a sliding door closer according to an embodiment of the second invention according to the present application. It is configured so that it can be adjusted.

That is, in the sliding door closers shown in these figures, the pivot shaft 9 of the centrifugal governor is rotatably supported on the machine frame 7, as described above, but each of the sliding door closers has a bottom. The cup-shaped drive drum 6 and friction drum 12 are coaxially supported on a pivot shaft 9, and a one-way clutch is arranged between these bottom plates. A clutch plate 22 having a clutch notch 14 (FIG. 10) is screwed to the drive drum 6 side.

Also, when the sliding door moves in the closing direction, the rotation of the friction drum 12, which is integrally connected to the drive drum 6 via the one-way clutch, is controlled by the large gear 23 carved on the flange of the friction drum, The rotation shaft 9 is accelerated through a pinion 24 supported on a shaft other than the rotation shaft 9, a first idle gear 25 coaxially and integrally connected to the pinion, and a second idle gear 26 coaxial with the rotation shaft. transmitted to.

The swivel arm 16 has a trough-like swivel arm 16 with a U-shaped cross section and an opening of the same shape on the bottom surface of the rotating shaft with the flange 9a (FIG. 11). is fitted and fixed, for example, with an adhesive applied between the collar portion 9a and the collar portion 9a.

A guide shoe 27 is guided at the tip (outer end) of the swing arm 16 so as to be movable in the radial direction of the friction drum 12, and as shown in FIG. The leg portion 27a of each guide shoe 27 protruding toward the 26 side is connected to the pivot shaft 9.
The threaded rod 29 is rotatably fitted in a vertically penetrating position, and is screwed into the tip of a threaded rod 29 which is prevented from coming off by retaining rings 28, 28. Both ends of the threaded rod 29 are threaded in opposite directions, and a single or cross-shaped slit (not shown) formed only on one end surface of the threaded rod 29 is engaged with the tip of the screwdriver. By aligning the threaded rod 29 and rotating the pair of guide shoes 27, 2,
The position of the pivot arm 7 in the longitudinal direction can be changed symmetrically.

A guide rod 18a integrated with a friction block 18 is guided in each guide shoe 27 so as to be movable in the longitudinal direction of the swing arm 16, and a spring holding plate is engaged with a stop shaft 28 fitted to the guide rod 18a. A return spring 19 as a compression coil spring is elastically mounted between the guide shoe 31 and the guide shoe 27. and,
Due to the elasticity of this return spring 19, the friction block 1
8 is biased in the direction of the pivot axis 9.

[Effect]

With the above configuration, the frictional resistance torque of the centrifugal governor can be adjusted by rotating the screw rod 29 with a screwdriver or the like to symmetrically change the position of the guide shoes 27, 27 in the longitudinal direction of the swing arms. I can do it. For example, guide shoes 27, 27
When these values are adjusted toward each other, r ₀ in equation (5) decreases and d increases, so these values work 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 is 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〕

As is clear from the above description, the present invention provides a sliding door closer by pulling the sliding door in the closing direction by the force of a drive spring made of a natural contact type spiral spring and applying braking by a centrifugal speed governor. Not only has the basic objective of the present invention been achieved, but also the closer operates reliably, and is compact and lightweight.

In addition, since rotational movement occurs naturally in the drive drum when the drive spring is compressed, there is no need for a mechanism to convert the linear movement of the sliding door into the rotational movement of the speed governor, and the structure is therefore 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 a closer using a conventional oil damper.
Not only is maintenance management 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 connecting body at one end of the drive spring and the locking pin, and it can be applied regardless of the amount of movement of the sliding door, or it can be attached to an existing sliding door. This has various effects, such as ease of use.

In addition, in the above-mentioned embodiment, the case was installed protruding from the outside surface of the sliding door or the door frame, but the case is omitted and the machine frame is built into the sliding door, and one end of the drive spring is connected to the joint end of the sliding door with the door frame. Of course, it may be pulled out from the edge, and in this case, the locking pin that engages with the connecting body is housed in a recess cut into the door frame.

[Brief explanation of drawings]

Fig. 1 is a partially sectional plan view of a sliding door closer according to an embodiment of the first invention according to the present application, Fig. 2 is a sectional view thereof, and Fig. 3 is a diagram for explaining a natural contact type spiral spring. , FIG. 4 is a partial front view of the sliding door with the closer attached, FIG. 5 is a partially sectional bottom view of the closer shown in FIG. 1, FIG. 6 is a partially enlarged sectional view of the closer shown in FIG. 8 is a side view of the swing arm, FIG. 9 is a side view of a sliding door closer according to another embodiment of the first invention according to the present application, and FIG.
Figure 0 is a partially sectional plan view of a sliding door closer according to an embodiment of the second invention of the present application, and Figure 11 is a plan view of the first embodiment of the sliding door closer.
FIG. 0 is a sectional view taken along the line XI-XI, and FIG. 12 is a partially sectional plan view of the centrifugal governor. DESCRIPTION OF SYMBOLS 1... Drive spring, 6... Drive drum, 7... Machine frame, 9... Rotating shaft, 12... Friction drum, 13...
...Internal gear wheel, 14...Clutch groove, 15...Clutch ball, 16...Swivel arm, 18...Friction block, 19...Return spring, 21...Sliding door.

Claims (1)

[Scope of Claims] 1. A tape-shaped drive spring consisting of a natural contact type spiral spring, one end of which is connected to a sliding door or door frame, and rotatably supported by a door frame or a machine frame attached to the sliding door, a drive drum having a drive spring wound around its outer periphery from the other end; a pivot shaft rotatably supported on the machine frame; a pivot arm connected approximately perpendicularly to the pivot shaft;
A centrifugal speed governor includes a friction block that is movably guided along the longitudinal direction of the swing arm, and a friction drum that is disposed coaxially with the swing shaft and whose inner peripheral surface is in sliding contact with the friction block. A speed increaser that interconnects the rotating shaft and drive drum of the centrifugal speed governor, amplifies the rotational angular velocity of the drive drum and transmits it to the rotating shaft, and when the drive drum rotates in the direction to wind up the drive spring. and a one-way clutch connecting the drive drum to the centrifugal governor. 2. The sliding door closer according to claim 1, wherein the width of one end of the drive spring is narrowed to form a weak force section. 3. The sliding door closer according to claim 1, wherein the drive drum and the friction drum are coaxially arranged. 4. Consists of a natural contact spiral spring, with a tape-shaped drive spring connected to the sliding door or door frame at one end, and a drive spring rotatably supported by the door frame or machine frame attached to the sliding door, with the drive spring attached to the outer periphery. A drive drum wound from the other end, a pivot shaft rotatably supported on the machine frame, a pivot arm connected almost perpendicularly to the pivot shaft,
A guide shoe attached to the swing arm so that its position in the longitudinal direction can be adjusted; a friction block that is movably guided by the guide shoe in the longitudinal direction of the swing arm and is biased in the direction of the swing axis; and a swing block. A centrifugal governor is equipped with a friction drum that is disposed coaxially with the shaft and whose inner peripheral surface is in sliding contact with a friction block, and the rotating shaft and drive drum of this centrifugal governor are interconnected to control the rotation of the drive drum. It is characterized by having a speed increaser that amplifies the angular velocity and transmits it to the rotating shaft, and a one-way clutch that connects the drive drum to the centrifugal governor only when the drive drum rotates in the direction to wind up the drive spring. A sliding door closer. 5. The sliding door closer according to claim 4, wherein the width of one end of the drive spring is narrowed to form a weak force section. 6. The sliding door closer according to claim 4, wherein the drive drum and the friction drum are coaxially arranged.