JPH01151682A - Door closer - Google Patents

Abstract

PURPOSE: To aim at the compatible use of a door closer for interior and exterior by arranging an input shaft to be rotated with opening and closing of a door in the vertical direction, and arranging a rotary center shaft of an accelerating gear train for accelerating displacement of a slider in the horizontal direction so as to reduce the thickness of a closer. CONSTITUTION: A door closer is formed of a slider 11 to be displaced by the rotation of input shafts 3, 3, a coil spring 12 for storing energy, accelerating gears 20, 21, 22 and a worm 17 as a control means. A clutch means 19 is built in the gear 22. When a door is opened, the input shaft 3 is rotated, and the slider 11 is displaced so as to store the energy in the spring 12, but the clutch means 19 cuts the transmission between the control means 17. At the time of closing the door, the slider 11 energized by the spring 12 is moved, and the worm 17 is rotated at a high speed through the gears 20, 21 and the gear 22, which contacts with the clutch means 19, and the rotation is braked by the worm means 17 so as to close the door slowly.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a door closer that automatically closes an open door, specifically a mechanical door closer.

(Prior Art) The most popular type of door closer is the oil type. Mechanical door closers have also been proposed with the aim of solving the problems of oil-type door closers, such as oil leakage and variation in closing speed due to changes in oil viscosity.

There are two types of door closers: an exterior type that is installed on the door surface, and a built-in type that is embedded inside the door.

(Problem that the invention attempts to solve) Mechanical door closers that have been proposed so far are:

The problems of the oil type have been solved and it can be put to practical use, but if you try to use it as a built-in type, the thickness cannot be made much thinner compared to the thickness of the door. , the problem remained.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a mechanical door closer that can be built into a door and can also be used as an exterior type door closer.

(Means for Solving the Problems) The door closer of the present invention includes an input shaft that rotates in conjunction with opening and closing of the door about a vertical rotation center axis;
A slider that is displaced following the rotation of the input shaft; a spring that is stored when the slider is moved in the door opening direction and biases the slider in the door closing direction; and a horizontal rotation center axis. a speed increasing gear train that rotates around and accelerates the displacement of the slider; a worm that is rotatable around a vertical rotation center axis and meshes with a final stage of the speed increasing gear train; and a clutch means for cutting off rotational transmission between the braking means and the slider when the slider moves in the door opening direction.

(Operation) When the door is opened, the input shaft rotates and displaces the slider in the door opening direction. When the slider is displaced, the spring is compressed and stored. When the door is opened, rotational transmission between the slider and the braking means is interrupted by the clutch means. When the action to open the door is released, the slider, which is biased by a spring and moves, rotates the input shaft and closes the door. The displacement of the slider at this time is transmitted to the worm through the speed increasing gear train, causing the worm to rotate at high speed. The rotation of the worm is braked by the braking means, thereby braking the rotation of the input shaft, that is, the rotation of the door.

(Example) Hereinafter, the present invention will be described in detail based on the illustrated example.

In FIG. 1, a door closer 1 according to the present invention is
The input shaft 3 is comprised of a frame 2, an input shaft 3 rotatably supported by the frame and having an end protruding from the frame, and each component described later.

The frame 2 is fixed to a storage part formed, for example, at the upper end of a door (not shown) with screws 4, 4.

On the other hand, a guide rail 5 having a U-shaped cross section is fixed to a door frame (not shown). A slider 6a pivotally attached to one end of an arm 6 is slidably fitted into the guide rail 5. The other end 6b of the arm 6 has a square hole 6-c formed therein connected to the protruding end of the input shaft 3.

In FIGS. 2 and 3, the frame 2 consists of a right frame 2a and a left frame 2b which are overlapped with each other. The right frame 2a and the left frame 2b are fixed to each other by spacer pins 7 and screws 8. frame 2
are the tapping holes 2c, 2c formed on the top of the
It is attached to the door using. The illustrated example is attached to a left-handed door, but it can be attached to a right-handed door by turning the illustration upside down and using the tapping holes 2d and 2d formed at the bottom. be done. Moreover, when it is fixed to a door as an exterior type, the fixing screws are inserted into the holes 2e, 2e formed in the right frame 2a, and the holes 2f formed in the left frame 2b.

Insert a screwdriver from 2f and turn the fixing screw. That is, the slider 1 can be installed as either a built-in type or an external type, and can be opened either left or right.

An input shaft 3 whose rotation center axis extends vertically is disposed approximately in the center of the frame 2 . The input shaft 3 is made of metal in consideration of the load applied thereto, and is rotatably supported by bearings 9, 9. Bearing 9
, 9 are supported by bearing holders 10.10 fixed to the frame 2, only one of which is shown in FIG.

Both ends 3a of the input shaft 3 protrude from the frame.

3b is formed into a square shaft and is engaged with a square hole 6c of the arm 6 (see FIG. 1). The illustrated example shows a door closer attached to a left-hand door. The arm 6 is therefore connected towards the end 3a. The input shaft 3 is formed with a toothed portion 3c and a cylindrical portion 3d having a diameter substantially equal to the tip circle of the toothed portion.

A metal slider 11 is slidably provided on the frame 2. As shown in FIG. 5, the slider 11 includes a first rack portion 11a that engages with the teeth 3C of the input shaft.
A second rack portion 11b that meshes with a second gear, which will be described later, and a spring receiver portion 11c that abuts one end 12a of the coil springs 12, 12 are formed.

The first rack section 11a and the second rack section 11b are formed to be orthogonal to each other. A spacer 13 made of synthetic resin is provided between the inner surface of the frame 2 made of sheet metal and the slider 11 to reduce the sliding resistance between the metal members.

Two coil springs 12 are arranged vertically in parallel, and the other ends 12b, 12b are supported by a plate 14 as a spring receiver. The spring bearing plate 14 has both ends engaged with holes formed in the frame 2, and is screwed into the frame 2 by screws 15a.

It is supported by a stay 15 fixed at 15a. The coil springs 12, 12 are precompressed and stored within the frame to the extent that they can engage the door latch.

Inside the frame 2, a speed increasing gear train 16 that accelerates the displacement of the slider 11, a worm 17 that meshes with the final stage of the speed increasing wheel train 16, a braking means 18 provided on this worm, and a part of the slider 11 are provided. A clutch means 19 for transmitting only movement in the direction to the braking means 18 is housed.

The speed increasing gear train 16 includes a second gear 20, a third gear 21, a fourth gear 22, and so on. It consists of a worm wheel 23. These wheel trains are rotatably supported by support shafts 20 a , 21 a , and 22 a arranged horizontally, respectively. Support shafts 20a, 21a, 22
a is supported by a right case 2a and a left case 2b.

The second gear 20 includes a small-diameter partial tooth portion 20b that meshes with the second rack portion 11b, a large-diameter partial tooth portion 20c, and a cylindrical portion 2Qd that is equal to the addendum circle of the partial tooth portion 20b. The third gear 21 is a two-stage gear consisting of a small-diameter tooth portion 21b that meshes with the partial tooth portion 20c of the second gear, and a large-diameter tooth portion 21c. The fourth gear 22 is a small-diameter gear that meshes with the large-diameter tooth portion 21c.

The fourth gear 22 and the worm wheel 23 also serve as a part of the clutch means 19. A sleeve 22b is formed on the fourth gear 22, and locks one end 19aa of a coil spring 19a wound around the sleeve 22b.

The worm wheel 23 has teeth formed on the outer peripheral surface of a sleeve 23a surrounding the sleeve 22b.

The coil spring 19a is given an expanding habit to press against the inner peripheral surface of the sleeve 23a, and its free end is free with respect to the sleeve 23a.

When the fourth gear 22 rotates in the direction of arrow a, the coil spring 19a is tightened by one turn and does not transmit the rotation of the sleeve 22b to the sleeve 23a. When the No. 4 gear 22 rotates in the opposite direction to arrow a, at this time,
Since the coil spring 19a expands, the rotation of the sleeve 23b is transmitted to the sleeve 23a, that is, the worm wheel 23. Therefore, the rotation of the second gear 20 is transmitted to the worm wheel 23 at an increased speed. Note that the clutch means 19 is not limited to the illustrated example;
Other types of clutches that provide the above effects may be employed.

The worm 17 is a bearing 17a fixed to the frame.

It is rotatably supported by 17b and rotates about a vertical axis of rotation.

As shown in FIGS. 3 and 6 to 8, the braking means 18 includes holders L8a and 1 that are press-fitted into the wall 417.
A pair of arms 18c, 18c are swingably supported by pins 18b, 18b on 8aa, and a high friction material 18d is press-fitted into the outer edge of the arm near the free end.

18d, and a braking cup 18e surrounding the arm. Cup 18e is fixed to bearing 17b. When the worm 17 is rotated at high speed, the arms 18c, 18c are expanded by centrifugal force, and the high friction material 1
8d and 18d are brought into sliding contact with the inner peripheral surfaces of the cups 18e and 18e to brake the rotation of the worm. The arm 18c is made of metal or a material having a similar mass so as to obtain sufficient centrifugal force. In addition, high friction material 1
As the material 8d, rubber or a rubber-like material is used, which provides high frictional resistance and excellent wear resistance. Note that the braking means 18 is not limited to the illustrated example;
Various governor mechanisms may be used, such as a wind blower fixed to the worm 17, a friction arm made of elastically deformable rubber, an eddy current type, an electromagnetic type, and a brake brake type.

Now, the operation of the embodiment configured as above will be explained.

2 and 3 show a state in which a door (not shown) is closed. In this state, the slider 11
is pushed by the elasticity of the coil spring 12, and brings the back surface of the spring seat 11c into contact with the cylindrical portion 3d of the input shaft 3. Further, in this state, the slider 11 has its first rack portion 11a meshed with the toothed portion 3c of the input shaft, and its second rack portion 11b meshed with the partial toothed portion 20b of the second gear. The partial tooth portion 20c of the second gear 20 meshes with the small diameter tooth portion 21b of the third gear 21.

Now, when a door (not shown) is opened, the door closer
1 is rotated together with the door in the direction indicated by the arrow in FIG. When the door rotates in the opening direction, in Fig. 2,
The input shaft 3 rotates clockwise. The rotation of the input shaft 3 is controlled by the slider 11 engaged with it at the first rack portion 11a.
Move to the right in the door opening direction as shown in the figure. As shown in FIG. 9, the slider moving action by the input shaft 3
This continues only as long as c is engaged with the first rack portion 11a.

In FIG. 9, when the input shaft 3 is further rotated in the direction of the arrow mark, which is the rotation direction of the door opening direction, the cylindrical portion 3d is moved to the non-toothed portion li of the first rack portion 11a, as shown in FIG.
It comes to face d. Non-rack part lid is cylindrical part 3
The slider 11, which has been moved to the position opposite d, can no longer be displaced any further. When the slider 11 is displaced in the door opening direction, the spring 12 pushed by the spring seat 11c is compressed and stored. Spring 1
As shown in FIG. 11, the accumulation of energy in step 2 is completed when the displacement of the slider 11 is restricted.

Now, when the door is opened and the slider 11 is displaced,
The second gear 20 engaged with the second rack portion 11b of this
is rotated in the direction of arrow C, as shown in FIG. The rotation of the second gear 20 is accelerated through the third gear 21 and transmitted to the fourth gear 22, causing the gear 22 to move in the direction of arrow a.
direction (see Figure 3).

The rotation of the fourth gear 22 in the direction of the arrow a is caused by the clutch means 19.
Since the direction is to tighten the coil spring 19a of
The rotation of the No. 4 gear 22 rotating in the figure is caused by the rotation of the sleeve 2
3a, that is, it is not transmitted to the worm wheel 23. Therefore, the displacement of the slider 11 moving in the door opening direction is
The clutch means 19 will disconnect the brake means 18.
Since it does not operate, there is no load on the door opening operation.

Now, as shown in FIG. 9, when the opening operation for the door that has been opened until the tooth portion 3c of the input shaft 3 and the first rack portion 11a of the slider are engaged is released, the input shaft 3 The rotation of the 6-input shaft 3, which is rotated in the direction opposite to the arrow by the slider 11 which is biased by the biased coil spring 12 and moves in the opposite direction to the arrow, is caused by the rotation of the input shaft 3 by the arm 6.
(See FIG. 1) to rotate the door (not shown) in the closing direction (in the direction opposite to the arrow in FIG. 1).

When the slider 11 moves in the door closing direction, the second gear 20 engaged with the second rack portion 11b of the slider 11 moves into the first gear.
As shown in Figure 2, it is rotated in the direction of the arrow ca force. 2
The rotation of the No. 4 gear 20 is controlled by the No. 4 gear 2 via the No. 3 gear 21.
2, which is rotated in the direction opposite to the arrow a in FIG. When the fourth gear 22 rotates, its sleeve 22b expands the coil spring 19a, causing the sleeve 23a integrated with the worm wheel 23 to rotate at high speed. That is, when the door is closed, the clutch is engaged and the worm wheel 23 rotates the worm 17 at high speed. As the worm 17 rotates, in FIG.

The arms 18c, 18c expand due to centrifugal force, and the high friction material 18
d and L8d rub the inner peripheral surface of the cup 18e to brake the rotation of the worm 17. When the rotation of the worm is braked, the speed-increasing wheel train 16 that drives the worm is also braked. The braking applied to the speed-increasing wheel train 16 applies braking to the rotation of the input shaft 3 that is engaged with the slider 11. When the input shaft 3 is braked, the door, which is rotating in the closing direction, is slowly closed.

Next, as shown in FIG. 11, it has already been explained that when the cylindrical portion 3d of the input shaft 3 corresponds to the non-rack portion lid of the slider 11, the slider 11 cannot be displaced any further. When the input shaft 3 and slider 11 are placed in the state shown in FIG. 11, when the door is further opened,
The input shaft 3 is rotatable in the direction of the arrow. In this state, when the force to open the door is released, the door stops at that position. That is, the non-rack part li
If d corresponds to the cylindrical portion 3d, the slider 11, which is biased by the coil spring 12, cannot rotate the input shaft 3 and must remain in this position. Therefore, 1. After opening the door for a certain amount of time, the door can be stopped at any open position. To close the door placed in such a state, the input shaft 3 is rotated as shown by the arrow ba in FIG. All you have to do is rotate the door in the closing direction until it reaches the engaged position. Thereafter, the door is closed by the input shaft 3 rotated by the slider 11 biased by the coil spring 12.

In the embodiment described above, the input shaft 3 and the slider 11 are coupled by a rack and a pinion (the first rack part ILa and the tooth part 3c), but they can also be coupled by a cam. This example will be explained based on FIG. 13. Input shaft 3
A is formed with a small diameter cam portion 3Aa and a large diameter cam portion 3Ad. On the other hand, the slider 11A is formed with a contact portion 11Aa that abuts against the cam portion of the input shaft, and a rack portion 11Ab that meshes with the second gear. 13th
The figure shows a state in which the door is closed, and the slider 11A has its contact portion 11Aa engaged with the small diameter cam portion 3Ab of the input shaft by the elasticity of the coil spring 12. When the door is opened, the input shaft 3A rotates in the direction indicated by the arrow, and its cam slope 3A pushes and displaces the slider IIA to the right in the figure, thereby accumulating the coil spring 12. When the input shaft 3A rotates to the position where the large diameter cam portion 3Ad engages with the contact portion 11Aa, that is, when the door is opened to this position, the slider cannot push the input shaft, so the door opens. Can be stopped at any open position. When the door opening operation is released while the cam slope 3Ac and the pushing part 11Ad are engaged, the input shaft 3A is rotated by the slider 11A, which is displaced in the door closing direction by the stored force of the coil spring 12. and close the door.

The difference in height between the small diameter cam portion 3Aa and the large diameter cam portion 3Ad is determined as appropriate. Further, it goes without saying that a speed increasing wheel train 16 as shown in FIG. 3 is connected to the rack portion 11Ab. Also, slider 11. The IIA and the speed-increasing wheel train 16 may be coupled to each other in a coupling relationship in which the second gear follows the displacement of the slider instead of a rack-pinion coupling. In this case, a part of the No. 2 gear is given a rotational behavior such that it comes into contact with a part of the slider, and the No. 2 gear follows the slider, which is displaced in conjunction with the input shaft that rotates as the door opens and closes. The number gear rotates.

By the way, since the door is provided with a latch, it may be better not to apply a brake to the door that is about to close. In FIG. 14, only one tooth is formed on the second rack portion of the slider 11B, and this tooth 118b
a meshes with the small diameter tooth portion 20b of the second gear 20.

When the door closes, the tooth 11Bba rotates the second gear 20 in the direction of the arrow, but since there is only one tooth on the rack part, at the end of the slider displacement, that is, just before the door closes, Because there are no teeth to rotate the 2nd gear.

Only the slider moves and the second gear does not rotate. Therefore, at the final stage of closing the door, the speed-increasing gear train does not rotate, so the braking means does not operate, and no braking is applied to the closing operation of the door.

Additionally, doors installed in places that are being heated or cooled or used in cold regions are required to be closed as soon as possible. However, braking on the door cannot eliminate this.

Therefore, the brake may be applied to the door when the door is close to being completely closed or close to the open position. In other words, the brake may not be applied at the initial position of the door when it rotates in the closing direction. An example of this is shown in FIG. The second rack part of the slider 11C has one tooth 11Cba formed at a position retracted from the end thereof.
A rotation preventing portion 11Cbb is provided to protrude from the end portion. On the other hand, the second gear 20A is formed with a notch 20Ac into which the rotation stopper 11Cbb is fitted. FIG. 15 shows a state in which the slider 11G is displaced in the door opening direction.

At this time, the second gear 20A has its tooth portion 20Ab as the tooth 1.
1Cba and rotated clockwise. Slider 1 from the state shown by the solid line
1C can be further displaced to the right as shown by the chain line, but the second gear 20A cannot rotate because the rotation stopper 11Cbb is located opposite to its teeth 20Ab. When closing the door, the slider lIC is displaced to the left from the chain line position a'fJ1. At this time, slider tooth 11Cba
Rotation of the gear 20A is prevented by the rotation stop portion 11Cbb until the gear 20A meshes with the tooth 20Ab of the second gear. for that.

The speed increasing gear train starting from the second gear 20A does not rotate, and the braking means is not activated. Therefore, no braking is applied to the closing door until the teeth of the slider IIG rotate the second gear, and the initial rotation speed of the door in the closing direction becomes faster. When the tooth 11Cba begins to rotate the second gear 20A, the speed-increasing gear train operates the braking means, so of course the door that is about to close is braked.

Note that the slider 11B shown in FIGS. 14 and 15.

11C is displaced by a toothed manual shaft as shown in FIG. 3 or a cam manual shaft as shown in FIG.

(Effects of the Invention) As described above, according to the door closer of the present invention, since the input shaft is vertical and the rotational center axis of the speed increasing gear train is horizontal, the diameter of the speed increasing wheel train is influenced. The thickness of the closer can be made thinner without being damaged. This is effective not only for built-in types but also for external types. However, since it is purely mechanical, it is not affected by oil leaks or temperature, so it has a long life and constant speed operation.

[Brief explanation of the drawing]

FIG. 1 is an external perspective view of a door closer showing an embodiment of the present invention, and FIG. 2 is an enlarged plan sectional view of the same. Figure 3 is a longitudinal sectional front view of the same as above, Figure 4 is a plan view of essential parts of the same as above, Figure 5 is an exploded perspective view showing an example of the relative relationship between the input shaft, slider, and speed increasing gear train, and Figure 6 is the brake. A plan sectional view showing an example of the means, FIG. 7 is a longitudinal sectional view taken along line A-A in FIG. 6,
Fig. 8 is a longitudinal sectional view taken along line B-B in Fig. 6, Fig. 9 is an action view of Fig. 2 showing the operation when the door is opened, and Fig. 10
The figure is the action diagram of Figure 3 of the same above, Figure 11 is the action diagram of Figure 9 showing only the main parts when the door is opened to the position where it can be stopped at any position, and Figure 12 is the action diagram of Figure 10 of the same above. action diagram,
FIG. 13 is a plan view showing another example of how the input shaft and the slider are coupled, and FIGS. 14 and 15 are front views showing other examples of how the slider and the speed increasing gear train are coupled. 1...Door closer-12...Input shaft, 11...
Slider, 12... Coil spring, 16... Speed increasing gear train, 17... Worm, 18... Braking means, 19...
...Clutch means. Broom 40 Broom 60 Me 70 Form I 9 mouth) 'F> a mouth 16 mouth 740 melσkuni procedural amendment

Claims (1)

[Scope of Claims] An input shaft that rotates in conjunction with the opening and closing of the door about a vertical rotational center axis; a slider that is displaced following the rotation of the input shaft; and the slider moves in the door opening direction. a spring that is stored when the slider is moved and biases the slider in the door closing direction; a speed-increasing gear train that rotates around a horizontal rotation center axis and accelerates the displacement of the slider; a worm that is rotatable about a rotational center axis in the direction and that engages with the last stage of the speed increasing gear train; a braking means that brakes the rotation of the worm; and a worm that applies a brake to the rotation of the worm, and , a door closer comprising clutch means for cutting off rotational transmission between the braking means and the slider.