JPH0562192B2 - - Google Patents

Abstract

PURPOSE:To prevent the generation of backlash noises by disposing a transmission member with a cam section between a slider and a speed-increasing wheel row and increasing the speed of travel of the slider at a position immediately before a door is closed. CONSTITUTION:When the opening operation of a door is released, a tooth section for an input shaft 3 is engaged with a rack section 11a for a slider 11 energized by a spring 12 and moved in the direction of the arrow (b), and the input shaft 3 is burned in the counterclockwise direction. A metallic transmission member 18 for a speed-increasing wheel row 19 is rotated in the counterclockwise direction, double gears 23 are revolved through sleeves 26a, 27a made of a synthetic resin, and a small-diameter gear 24 is turned in the direction of the arrow (a). A clutch means is brought to the position of contact, and a worm wheel 25 rotates and drives a worm shaft 20 at high speed. An arm section 21a is expanded, the inner circumferential surface of a cup section 21b is slid and rubbed and the revolution of the worm shaft 20 is braked, and the rotation of the door is braked.

Description

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

(Conventional technology) The most popular door closers are:
It is an oil type door closer. This door closer allows the door to close quickly at the beginning.
A plurality of oil passages with different cross-sectional areas are switched depending on the opening angle of the door so that the opening is relaxed just before the door is completely closed. In FIG. 9, the broken line shows the relationship between the door opening angle and the closing speed of the oil-type door closer. For example, a door that opens to an opening angle of 90°,
Although it closes at a relatively high speed until the opening angle is around 20°,
If the opening angle is less than that, it will close at a low speed. That is, when the opening angle of the door reaches a predetermined angle close to the closed position, the flow of oil in the oil passage is restricted and the closing speed is rapidly reduced. This is to prevent the door from closing too quickly and to prevent fingers or objects from getting caught.

(Problem to be Solved by the Invention) In order to switch the oil passage, the conventional oil-type door closer has two steps as shown by the broken line in FIG.
The closing speed of the door changes rapidly with a large speed difference. By slowing down the speed just before it closes, this solves the problem of preventing fingers from being caught, but the speed difference between the speed at the beginning of closing is so large that the closing speed decreases significantly. There is a problem in that the door hinge makes a rattling noise when the door is pressed. Further, the impact of the door at this time creates a problem in that unnecessary stress is generated on the support structure of the door.

Therefore, it is conceivable to provide many oil passages to reduce the difference in closing speed, but this would result in an increase in the size of the door closer, and furthermore, it would not be possible to eliminate the gradual difference in speed. Additionally, oil-type door closers have the problem of fluctuations in closing speed due to oil leaks and changes in temperature.

(Means for Solving the Problems) The present invention aims to provide a continuously variable speed door closer that solves the problems of the oil-type door closers described above, and includes an input shaft that rotates in conjunction with opening and closing of the door; A slider that moves 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 the spring moves the slider. a speed-increasing gear train for increasing the moving speed of the slider to be moved; a braking means connected to the speed-increasing gear train for braking the rotation of the input shaft; and between the slider and the speed-increasing wheel train. a cam portion disposed and abutting against an end of the slider, the cam portion increasing the moving speed of the slider as the door approaches the closed position and transmitting the increased speed to the speed-increasing gear train; and a transmission member that meshes with the speed-increasing wheel train.

(Function) When the door is opened, the input shaft rotates and moves the slider in the door opening direction. When the slider moves, the spring is compressed and stored. 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 moving speed of the slider moving at this time is transmitted to the speed-increasing wheel train via the transmission member, and actuates the braking means to brake the rotation of the input shaft, that is, the closing door. As the door approaches the completely closed position, the moving speed of the slider is increased by the cam part of the transmission member and transmitted to the speed increasing gear train, increasing the braking force of the braking means to close the door. Gradually reduce speed. The moving speed of the slider does not change stepwise, but smoothly and continuously.

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

FIG. 1 shows an example of a retractable door closer, and the continuously variable door closer 1 includes a frame 2, an input shaft rotatably supported by the frame 2, and an input shaft whose end protrudes from the frame. 3 and each component described below. frame 2
is stored and fixed in a storage portion formed at the upper end of door D (see FIG. 2). On the other hand, the door frame (not shown) has a U-shaped guide rail 4.
is fixed. A slider 5a pivotally attached to one end of an arm 5 is slidably fitted into the guide rail 4. The other end 5b of the arm 5 has a square hole 5c formed therein connected to the protruding end of the input shaft 3.

In FIGS. 3 and 4, the frame 2 consists of a frame 2a and a frame 2b which are superimposed on each other. Frame 2a and frame 2b are
They are fixed to each other by screws not shown.

An input shaft 3 whose rotation center axis extends vertically is disposed approximately in the center of the frame 2 . In consideration of the load applied to the input shaft 3, it is made of metal and has bearings 9, 9 fixed to the frame.
It is rotatably supported. Ends 3a and 3b of the input shaft 3 protruding from the frame are formed into square shafts, and a square hole 5c of the arm 5 (see FIG. 1) is engaged with the end 3a. Input shaft 3 has
A toothed portion 3c and a cylindrical portion 3d having a diameter substantially equal to the tip circle of this toothed portion are formed.

A metal slider 11 is slidably provided on the frame 2. Slider 11 has
As shown in FIG. 6, a rack part 11a that meshes with the teeth 3c of the input shaft, a cam part 11b provided at the end that abuts against a transmission member to be described later, and a spring that has finished storing energy. A non-easy part 11c that engages with the cylindrical part 3d of the input shaft at the position (see FIGS. 3 and 8), and an engaging part 11 that can engage with the guide 16.
d are formed respectively. Slider 11
A spring seat 11e that receives one end 12a of the spring 12 is fixed to the end opposite to the cam portion 11b. 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 parts.

Two springs 12 are arranged vertically in parallel, and the other ends 12b, 12b are supported by a receiving plate 14. The receiving plate 14 is supported at both ends by stays 15 fixed to the frame 2. The springs 12, 12 are precompressed and stored within the frame to the extent that they can engage the door latch.

As shown in FIG. 8, the slider 11 includes
When the door opens at a predetermined angle, the cylindrical part 3 of the input shaft 3
The brake member 17 that comes into contact with d has two screws 17
It is attached at a, 17a.

Inside the frame 2, there is a cam portion 1 of the slider 11.
Cam part 18a and large diameter tooth part 18b that abut against 1b
A transmission member 18 formed with a transmission member 18, a speed increasing gear train 19 that increases the moving speed of the slider, a worm shaft 20 that meshes with the final stage of the speed increasing wheel train 19, and a braking means 21 provided on the worm. A clutch means 22 for transmitting only the movement of the slider 11 in the door opening direction to the braking means 21 is housed. The speed-increasing gear train 19 includes the toothed portion 18b of the transmission member 18, a two-stage gear 23, a small diameter gear 24, and a worm wheel 25. These wheel trains are rotatably supported by metal support shafts 26, 27, and 28, which are arranged horizontally and have both ends caulked to the frame 2. Support shaft 26,2
7 each have a sleeve 26 made of synthetic resin.
a, 27a are rotatably inserted.

Transmission member 18 is substantially integral with sleeve 26a. A return lever 29 is attached to the sleeve 26a.
are integrally fitted. This lever 29 is
Its tip 29a is engaged with a pin 30 fixed to the slider 11, and the transmission member 1 follows the movement of the slider 11 when the door is opened, which will be described later.
8 clockwise (in FIG. 7).
Note that instead of the return lever 29, the transmission member 18 may be biased by a spring. In addition, the transmission member 18 of the illustrated embodiment is constructed by stacking two press-formed plates and engaging the notches formed at the inner edges of the rotation center holes with the protrusions 26aa of the sleeve 26a. They are integrated in the direction of rotation. The cam part 18 is a slider 11 that moves linearly.
The contact point changes depending on the rotational position of the transmission member 18. As shown in FIG. 4, when the door is open, the point of contact between the cam portion 18a of the transmission member and the cam portion 11b of the slider is located at a distance l from the support shaft 26, which is the rotation center of the transmission member. It is in. The open position of the door is approximately 20° from the closed position (symbol DB in Figure 2)
), both cam portions 18a, 11b
As shown in Figure 5, the meeting point of is at a distance l1 (<l)
It is located at The door is in the closed position (symbol D in Figure 2)
), both cam portions 18a, 11b
As shown in Figure 7, the meeting point of is at a distance l2 (<l1)
It is located at That is, the cam parts 11b, 11a
However, the abutment point approaches the support shaft 26 as the opening angle of the door becomes smaller. In other words,
The rotation speed of the transmission member 18 pushed by the slider 11 becomes gradually faster as the abutment point of both cam portions approaches the support shaft 26.

The two-stage gear 23 is a speed increasing gear consisting of a small diameter gear 23a that meshes with the tooth portion 18b of the transmission member 18 and a large diameter tooth portion 23b. A tooth portion 24a of a small-diameter gear 24 meshes with the large-diameter tooth portion 23b.

The small diameter gear 24 and the worm wheel 25 constitute clutch means. The small diameter gear 24 has
A sleeve 24b is formed and locks one end 31a of a coil spring 31 wound around the sleeve 24b.
The worm wheel 25 has teeth 25b formed on the outer peripheral surface of a sleeve 25a surrounding the sleeve 24b. The coil spring 31 is connected to the sleeve 25a.
The free end 31b is free with respect to the sleeve 25a. When the small diameter gear 24 rotates in the direction of arrow a, the coil spring 31
By being tightly wound, the rotation of the sleeve 24b is not transmitted to the sleeve 25a. Small diameter gear 24
When rotates in the opposite direction to arrow a, at this time,
As the coil spring 31 expands, the sleeve 24b
The rotation is transmitted to the sleeve 25a, that is, the worm wheel 25. Therefore, the rotation of the transmission member 18 is transmitted to the worm wheel 25 at an increased speed. It should be noted that the clutch means is not limited to the illustrated example, and other types of clutches that provide the above-mentioned effects may be employed.

The worm shaft 20 is rotatably supported at both ends by bearing members 32 and 33 fixed to the frame.

The braking means 21 includes a worm shaft 20, an arm portion 21a that is press-fitted onto the shaft and expands in the circumferential direction when the shaft is rotated at high speed, and an arm portion 21a that surrounds the arm portion and expands. The arm part is composed of a braking cup 21b that slides on the inner peripheral wall of the arm part and applies a brake to the rotation of the worm shaft. Note that other types of governor mechanisms, such as a wind blowing system or an eddy current system, may be used as the braking means;
A worm shaft is used as the rotation center axis.

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

The door closer shown in FIGS. 3 and 4 is shown in a state where the door is opened approximately 90 degrees, as indicated by the symbol DA in FIG. In this state, the slider 11 is pushed by the teeth 3c of the input shaft 3 against the elasticity of the spring 12, and its non-slip portion 11c is opposed to the cylindrical portion 3d. At this time, the spring 12 is biased and urges the slider 11 in the door closing direction (leftward direction in FIGS. 3 and 4). Further, at this time, the cam portion 11b of the slider 11 and the cam portion 18a of the transmission member 18 abut each other at a position C1 having a radius l around the support shaft 26.

Now, as shown in Figure 2, the door is opened approximately 90 degrees.
When the opening operation for DA is canceled, input shaft 3
is biased by spring 12 and arrow b
Slider 11 that moves in the direction (see Figure 3)
The toothed portion 3c is engaged with the rack portion 11a of the holder and rotated counterclockwise. Rotation of the input shaft 3, via the arm 5 (see FIG. 1), pivots the door towards the closed position indicated by D in FIG.

When the slider 11 moves in the door closing direction,
The transmission member 18, whose cam portion 18a is brought into contact with the cam portion 11b, is rotated in the direction of the arrow, as shown in FIG. The rotation of the transmission member 18 is
As shown in FIGS. 3 and 4, the signal is transmitted to the small-diameter gear 24 via the two-stage gear 23, which is rotated in the direction opposite to the arrow a in FIG. When the small diameter gear 24 rotates, its sleeve 24b expands the coil spring 31, causing the sleeve 25a integrated with the worm wheel 25 to rotate at high speed. That is, when the door is closed, the clutch means is engaged and the worm wheel 25 rotates the worm shaft 20 at a high speed. When the worm shaft 20 rotates at high speed, the arm portion 21a expands due to centrifugal force and rubs against the inner peripheral surface of the cup portion 21b, thereby applying a brake on the rotation of the worm shaft 20. When the rotation of the worm shaft is braked, the speed increasing wheel train 19 that drives the worm shaft is braked. The braking applied to the speed-increasing wheel train 19 applies braking to the rotation of the input shaft 3 that is engaged with the slider 11. This applies braking to the rotation of the input shaft 3. Applying a brake to the input shaft 3 means that a brake is applied to the rotation of the door that is rotating in the closing direction.

Now, the braking of the braking means 21 is performed by the worm shaft 20.
When the rotation of the arm 21a decreases, the arm 21a moves toward the cup 2.
It is canceled when 1b is no longer rubbed. Therefore, when the number of revolutions of the worm shaft 20 increases to a predetermined number or more, the braking action is started, and when the number of revolutions decreases, the braking action is canceled.

According to the door closer of the present invention, the closing speed of the door changes continuously, as shown by the solid line in FIG. The closing speed of the door, that is, the rotational speed of the input shaft 3 is determined by the moving speed of the slider 11. As shown in Figure 4, the door is approximately 90°
In the open state, the cam portion 11b of the slider
and the cam portion 18a of the transmission member 18 are the support shaft 26
They collide at position C1, which is a distance l from . Further, as shown in FIG. 5, when the door is closed to an opening angle of about 20 degrees, the abutting point of both cam parts is at a position C2 at a distance l1. As already mentioned, when the slider 11 moves in the door closing direction, braking is applied to it, but when the door opens from 90° to 20°
As shown in FIG. 9, the closing speed decreases at a relatively steep slope. The point of contact between the cam portion 11b of the slider 11 and the cam portion 18a of the transmission member 18 approaches the rotation center of the transmission member as the opening angle of the door becomes smaller.
The rotation angle of the transmission member 18 pushed in step 1 gradually increases as the door approaches the closed position. As shown in FIG. 7, when the door is completely closed (see reference numeral D in FIG. 2), both cam portions 11b,
18a abut against each other at a position C3 that is the closest distance l2 from the center of rotation of the transmission member. The abutment point of both cam parts changes most rapidly between the position C2, which is the nearly closed position shown in Fig. 5, where the opening angle is approximately 20°, and the closed position C3 shown in Fig. 7, and the transmission The rotation speed of the member 18 is increased. Therefore, the rotation of the transmission member 18 whose rotational speed has been increased is further increased through the speed-increasing gear train 19 and transferred to the worm shaft 20.
transmitted to. As the rotational speed of the worm shaft increases, the braking force of the braking means 21 increases, so a large braking force acts on the rotation of the speed increasing gear train 19 and the transmission member 18, that is, the movement of the slider 11, and the moving speed of the slider is reduced. lower. Therefore, a large braking force is applied to the input shaft 3 meshing with the rack portion 11a, making the closing speed of the door slow. That is, in FIG. 2, when the door rotates from the open position DB with an opening angle of 20 degrees to the closed position D, the closing speed becomes slow due to the slow moving speed of the slider 11. The door closing speed shown by the solid line in Figure 9 is:
Although the opening angle is reduced from 90° to 20° at a relatively steep slope, this figure only shows one model, and the shape of the cam portion 18a of the transmission member 18 can be modified as appropriate. Therefore, the opening angle can be close to 20° and the opening angle can be closed at a relatively fast speed.

6 and 7 show the relative positions of the transmission member 18 and the slider 11 when the door is completely closed (see reference numeral D in FIG. 2). In this state, when the door is opened, the input shaft 3 rotates in the direction of the arrow, and the slider 11 engaged with the toothed portion 3c is moved to the right in the figure in the door opening direction, and the spring 12 is loaded. do. When the slider 11 moves, the return lever 29, which is engaged with the pin 30, follows and rotates, causing the transmission member 18 to rotate clockwise. The rotation of the transmission member 18 rotates the speed increasing gear train 19, but rotation in this direction
Due to the coiled spring 31 (see FIG. 3) of the clutch means 22 being tightened, no power is transmitted to the worm wheel 25. Therefore, the braking means 21 does not operate when the door is opened.

In Figure 3, which shows the door opened approximately 90 degrees,
The slider 11 is in the position where the spring 12 is loaded, and its non-slip portion 11c is opposed to the cylindrical portion 3d of the input shaft. In this case, the slider 11, which is biased by the spring 12, is prevented from moving by the rack part 11a engaging with the columnar part 3d, so that the input shaft 3 cannot be rotated. , the action of closing the door is prevented. Therefore, even if the input shaft 3 is rotated any further, in other words, even if the door is opened by more than 90 degrees, the slider 11 will no longer move and will not close the door. Turn the door 90° as shown by the symbol DC in Figure 2.
When the input shaft 3 is opened more than this, as shown in FIG.
Since the non-slip portion 11c of the slider 11 rotates independently, the door can be stopped at any open position. In this state, since the brake member 17 is in contact with the circumferential surface of the cylindrical portion 3d of the input shaft 3, a brake is acting on the input shaft, that is, the door, and the brake member 17 is in contact with the peripheral surface of the cylindrical portion 3d of the input shaft 3. be stopped. Brake member 1
7 is made of a material with high friction and elasticity such as rubber, so when the screws 17a, 17a are tightened against the slider 11, the brake member is deformed under pressure and is pressed against the input shaft 3. The degree can be increased. In other words, the screw 17a
By rotating the door, the strength of the stopping action on the door at any position can be adjusted.
Note that a window hole (not shown) is formed in the frame 2 at a position facing the screws 17a, 17a.

To close the door DC placed at any position with an opening angle of 90° or more in Figure 2, mark the door with the symbol
Rotate it to the position indicated by DA. Then, as shown in FIG. 3, the rack part 11c of the slider and the tooth part 3c of the input shaft 3 engage, so that the slider 11, which is biased by the spring 12,
The input shaft 3 is rotated in the direction to close the door.

In addition, in the illustrated embodiment, the opening angle of the door at which the door automatically closes is 90 degrees, and the opening angle at which the door switches to sudden braking is 20 degrees, but the present invention is not limited to such angles. Of course not. Further, although the illustrated embodiment is a door closer built into the door, the present invention may also be an external door closer fixed to the surface of the door.

(Effects of the Invention) As described above, according to the continuously variable door closer of the present invention, a transmission member having a cam portion is disposed between the slider and the speed-increasing gear train, and when the door is about to close, the slider Since the moving speed of the door is increased, the closing speed of the door changes smoothly. Therefore, no rattling noise is generated at the hinge portion of the door, and no unnecessary impact is generated on the door support structure. Furthermore, since it is a mechanical structure, there is no problem of oil leakage or fluctuations in closing speed due to changes in oil viscosity due to changes in temperature.

[Brief explanation of the drawing]

Fig. 1 is an external perspective view of a continuously variable door closer showing an embodiment of the present invention, Fig. 2 is a plan view illustrating a plurality of opening positions of the door, and Fig. 3 is a diagram showing an embodiment of the invention. A plan sectional view of the continuously variable door closer at the door open position, FIG. 4 is a longitudinal sectional view of the same as above,
FIG. 5 is a side view showing the positional relationship between the slider and the transmission member just before the door closes, FIG. 6 is a plan view showing the relative position of the slider and the input shaft when the door is closed, and FIG. FIG. 6 is a front view, FIG. 8 is a plan view showing the door stopped at an arbitrary position, and FIG. 9 is a diagram showing the relationship between the opening position of the door and its closing speed. 1...Door closer, 3...Input shaft, 11...
...Slider, 12...Spring, 18...Transmission member, 18a...Cam section, 19...Speed-up gear train,
20... Worm, 21... Braking means.

Claims (1)

[Claims] 1. An input shaft that rotates in conjunction with the opening and closing of the door; a slider that moves following the rotation of the input shaft; and an input shaft that stores energy when the slider is moved in the door opening direction. , a spring that biases the slider in the door closing direction; a speed-increasing gear train that increases the moving speed of the slider moved by the spring; and a speed-increasing gear train connected to the speed-increasing gear train, and the input shaft a braking means for braking the rotation of the door; and a braking means disposed between the slider and the speed-increasing gear train, abutting against an end of the slider, and controlling the speed of movement of the slider as the door approaches the closed position. A continuously variable door closer comprising: a cam portion for increasing the speed and transmitting the increased speed to the speed increasing wheel train; and a transmission member having a part of the cam portion meshed with the speed increasing wheel train.