JPH0536055Y2 - - Google Patents

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 relates to a speed adjustment device that adjusts the door closing speed in a mechanical door closer.

(Prior Art) Oil-type door closers consisting of a cylinder and a piston containing oil and a spring are well known. Since the viscosity of the oil changes depending on the temperature, the closing speed of the door in such a door closer is adjusted by adjusting the flow rate of the oil seasonally or periodically. This oil-type door closer still has the problem of oil leakage, and a mechanical door closer has been proposed as an attempt to solve this problem. The closing speed of the door in a mechanical type is set in a substantially constant pattern by a braking means provided in a gear train.

(Problem to be solved by the invention) Since the mass of a door is not constant depending on its size and structure, if only one spring constant is set for the spring means incorporated in the door closer, the door The closing speed will be different for each case. Therefore, it is desirable that the closing speed of the door by the door closer can be adjusted depending on the type of door, the installation location, and the timing. However, in a mechanical door closer, since the pressure is set at a substantially constant level by the operation of a built-in braking means, there is a problem in that it cannot be adjusted or cannot be easily adjusted. Another problem is that if the braking means deteriorates over time, the speed at which the door closes becomes faster.

(Means for Solving the Problems) The present invention aims to provide a speed regulating device that solves the problems of the mechanical door closers described above, and includes an input shaft that rotates in conjunction with the opening and closing of the door, and an input shaft that rotates in conjunction with the opening and closing of the door. a spring means that stores energy and biases the input shaft in the door closing direction when the input shaft is rotated in the door opening direction; and a spring means that accelerates the rotational speed of the input shaft rotated by the biasing means. A door closer having a speed-increasing gear train for transmitting speed and a braking means for braking the rotation of the input shaft including a worm shaft provided at the final stage of the speed-increasing gear train, the direction of approaching and separating from the worm shaft. a speed regulating member movably disposed on the worm shaft; a biasing means for urging the speed regulating member in a direction to substantially press the worm shaft; and adjusting a pressing force between the speed regulating member and the worm shaft. It consists of adjustment means.

(Operation) When the door is opened, the input shaft rotates and the spring means is energized. When the door opening action is released, the spring means biased input shaft rotates to close the door. At this time, the rotation of the input shaft is accelerated by the speed increasing gear train and transmitted to the braking means, and the braking means is actuated to brake the rotation of the input shaft, that is, the closing of the door. At this time, the speed regulating member that is in pressure contact with the worm shaft also contributes to braking. When the pressure contact force of the regulating member against the worm shaft is adjusted by the adjusting means, the degree of braking of the braking means is varied, and the closing speed of the door is changed.

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

First, an example of a mechanical door closer to which the present invention is applied will be explained. FIG. 1 shows an example of a retractable door closer, and the door closer 1 includes a frame 2, an input shaft 3 rotatably supported by the frame, and an input shaft 3 whose end protrudes from the frame, and various components described below. It is made up of elements. Frame 2 is
It is stored and fixed in a storage portion formed at the upper end of door D (see FIG. 2). At the protruding end of the input shaft,
One end 4a of the arm 4 is connected. The other end 4b of the arm 4 is slidably fitted into a guide rail provided on a door frame (not shown).

In FIGS. 3 and 4, the frame 2 consists of a frame 2a and a frame 2b that are superimposed on each other and are fixed to each other. Input shaft 3
is a bearing 5 fixed approximately at the center of the frame 2;
5 is rotatably supported. Input shaft 3 has
A toothed portion 3a and a cylindrical portion 3b having a diameter substantially equal to the tip circle of this toothed portion are formed.

A slider 6 is slidably provided on the frame 2. As shown in FIG. 10, the slider 6 has a rack portion 6 that meshes with the tooth portion 3a of the input shaft.
a, and a cam portion 6b that abuts against a transmission member to be described later.
Then, a non-easy part 6c that engages with the cylindrical part 3b of the input shaft and an engaging part 6d that can engage with the guide 7 are formed, respectively, at the position where the spring means is fully loaded (see FIG. 3). There is. Cam portion 6b of slider 6
A spring receiving portion 6 receives one end of a coil spring 8 as a spring means.
e is fixed. A spacer 9 made of synthetic resin is provided between the inner surface of the frame 2 made of sheet metal and the slider 6.

Two coil springs 8 are arranged vertically in parallel, and the other end is supported by a receiving plate 10. A brake member 11 that slides against the cylindrical portion 3b of the input shaft 3 when the door is opened to a predetermined angle is attached to the slider 6 with two screws 11a, 11a.

The frame 2 includes a transmission member 12 formed with a cam portion 12a that abuts against the cam portion 6b of the slider 6 and a tooth portion 12b. Gear train 13 and
A worm shaft 14 forming the final stage of this gear train 13,
The braking means 15 provided on this worm shaft and the braking means 1 only control the movement of the slider 6 in the door closing direction.
Clutch means 16 for transmitting power to the clutch 5 are housed therein.

Speed-up gear train 13, transmission member 12, two-stage gear 1
7, a small diameter gear 18, a worm wheel 19, and a worm shaft 14. The transmission member 12, the two-stage gear 17, the small-diameter gear 18, and the worm wheel 19 are rotatably supported by support shafts 21, 22, and 23 that are caulked to the frame 2 at both ends thereof. Sleeves 21a and 22a made of synthetic resin are fitted onto the support shafts 21 and 22, respectively.

The transmission member 12 is rotatable with respect to the sleeve 21a. A return lever 24 that is substantially integral with the transmission member is fitted into the sleeve 21a.
This lever 24 has its tip 24a engaged with a pin 25 fixed to the slider 6,
The transmission member 12 is rotated clockwise (in FIG. 4) following the movement of the slider 6 when the door is opened, which will be described later. Further, the transmission member 12 in the illustrated embodiment is formed by stacking two plate materials formed by pressing. The cam portion 12a collides with the cam portion 6b of the slider 6 that moves linearly.
The abutment point changes depending on the rotational position of the transmission member 12. As shown in Figure 4, the cam part 1 when the door is opened approximately 90 degrees (see DA in Figure 2)
The abutment point between the cam portion 2a and the cam portion 6b is located at the farthest position from the support shaft 21, which is the rotation center of the transmission member.
When the door is in the closed position (see reference numeral D in FIG. 2), the abutment point of both cam portions 12a, 6b is at the first
As shown in Figure 1, when the door is at the position closest to the support shaft 21 and in the open position approximately 10 degrees from the closed position (see reference numeral DB in Figure 2), the abutting point of both cam parts 12a and 6b As shown in Figure 9,
It is located close to the closed position (see Figure 11). That is, the abutment point of the cam portions 6b, 12a approaches the support shaft 21 as the opening angle of the door becomes smaller. In other words, the slider 6 rotates the transmission member 12 faster as the abutment point of both cam portions approaches the support shaft 21.

The two-stage gear 17 is a speed increasing gear that includes a small diameter tooth portion 17a that meshes with the tooth portion 12b of the transmission member 12, and a large diameter portion 17b. A tooth portion 18a of a small diameter gear 18 meshes with the large diameter tooth portion 17b. As clearly shown in FIG. 8, the two-stage gear 17 has a rib 17d extending in the radial direction in the recess 17c of the large diameter portion.
is formed.

The small diameter gear 18 and the worm wheel 19 constitute the clutch means 16. A coil spring 26 is disposed between the small diameter gear 18 and the worm wheel 19 and has only one end locked to the small diameter gear. The worm wheel 19 has teeth 19a formed on its outer peripheral surface. coil spring 26
is given an expanding habit in the direction of pressing against the inner circumferential surface of the worm wheel 19, and its free end is free. Then, the small diameter gear 18 is the fourth
When rotating in the door opening direction shown by arrow a in the figure, the rotation of the small diameter gear 18 is not transmitted to the worm wheel 19 because the coil spring 26 is tightly wound. When the small diameter gear 18 rotates in the door closing direction opposite to arrow a, the coil spring 26 expands and transmits the rotation of the small diameter gear 18 to the worm wheel 19. Therefore, the rotation of the transmission member 12 is accelerated and transmitted to the worm wheel 19, and the worm shaft 14 meshed with the worm wheel 19 is rotated at a high speed.

The worm shaft 14 is rotatably supported at both ends 14a, 14b by bearing members 27, 28 fixed to the frame.

The braking means 15 includes a worm shaft 14 and a friction member 2 that is press-fitted onto the shaft and elastically deforms and expands in the radial direction when the shaft is rotated at high speed.
9, and the weight portions 29a, 29a of the friction member that surround this friction member and are expanded (see FIG. 5).
is comprised of a braking cup portion 30 which applies a brake to the rotation of the worm shaft 14 by slidingly contacting the inner circumferential wall thereof. The cup portion 30 is fixed to the bearing portion 28. The friction member 29 is made of an elastic material such as rubber, and includes a pair of arm portions 29b that are elastically deformed and expanded, and a weight portion 29a formed at the tip of the arm portions 29b. The friction member 29 is a receiving plate 31 that is press-fitted by D-cutting the worm shaft 14.
and a presser plate 32 connected by a pin 31a, and are held loosely between them to prevent any movement in the direction of the rotational axis. The boss portion 31b of the receiving plate 31 is
As shown in FIG. 6, one end 1 of the worm shaft 14
It is formed to be slightly longer towards 4a. Note that the braking means is not limited to the friction method shown in the drawings, and other types of governor mechanisms such as a wind-flow method or an eddy current method may be employed, but a worm shaft is used as the central axis of rotation. .

The configuration of the speed adjusting device will be explained based on FIG. 3, FIG. 4, FIG. 6, and FIG. 7.

The speed adjusting device 33 includes a speed regulating lever 34 as a speed regulating member disposed adjacent to the braking means 15 and substantially movable toward and away from the worm shaft 14, and this lever. a spring 35 as a biasing means for pressing 34 into contact with the worm shaft 14;
and an adjustment shaft 36 as an adjustment means for adjusting the pressing force of the lever by this spring.

The speed regulating lever 34 is swingably supported by a support shaft 37 supported by the frame 2 . The speed regulating lever 34 has a receiving plate 3 fixed to the worm shaft 14.
Brake piece 3 that approaches and separates from the circumferential surface of boss portion 31b of No. 1
4a, and a spring receiving portion 34 inserted through the adjustment shaft 36.
b. In the illustrated embodiment,
One end 34c of the speed regulating lever extends into the recess 17c of the two-stage gear 17 while avoiding the clutch means 16, and engages an engaging portion 34d formed at the end thereof.
It is positioned so as to be able to engage with the rib 17d of the gear (see FIG. 8). At one end 36a of the adjustment shaft 36,
A spring receiving E-ring 38 is attached, and a compressed extensible spring 35 is wound around the shaft portion between the E-ring and the spring receiving portion 34b. The speed regulating lever 34 is given a swinging habit by the spring 35 in a direction in which the braking piece 34a is brought into pressure contact with the boss portion 31b. The adjustment shaft 36 has a threaded portion 36b formed at one end thereof screwed into a threaded hole of the frame 2a so as to be movable forward and backward, thereby protruding from the frame. As shown in FIG. 1, the end 3 of the adjustment shaft protrudes from the frame.
6b faces an adjustment window hole formed in the upper edge of the door (not shown). The other end portion 36c of the adjustment shaft is made to protrude from a hole formed in the frame 2. Inner surface of frame 2 and E-ring 3
8, a spring 39 for preventing loosening is wound. Then, when the adjustment shaft 36 is rotated in an appropriate direction, the spring constant of the spring 35 increases, and the pressing force of the brake piece 34a of the speed regulating lever against the worm shaft (boss portion 31b), that is, the braking force, increases. Rotating the adjustment shaft in the opposite direction reduces the braking force. The speed regulating lever 34 is connected to the two-stage gear 1
The braking piece 34a is separated from the boss portion 31b by the rib 17d of No. 7, and this operation will be described later.

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

The door closer 1 shown in FIGS. 3 and 4 shows a state in which the door is opened approximately 90 degrees, as indicated by the symbol DA in FIG. It is rotated by the toothed portion 3a of the input shaft 3, and its non-easy portion 6c is attached to the cylindrical portion 3b. In this state, the coil spring 8
is stored and urges the slider 6 in the door closing direction (leftward direction in FIGS. 3 and 4). At this time, the braking piece 34a of the speed regulating lever 34 is brought into pressure contact with the boss portion 31b by the elasticity of the spring 34, and the rib 17 of the two-stage gear 17 is pressed against the boss portion 31b.
d is located away from the engaging portion 34d, as shown in FIG. The cam portion 6b of the slider 6 and the cam portion 12a of the transmission member 12 abut each other.

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 rotated counterclockwise by engaging its teeth 3a with the rack portion 6a of the slider 6 which is biased by a coil spring 8 and moves in the direction of the arrow (see FIG. 3). The rotation of the input shaft 3 is controlled by the arm 4.
(See Figure 1)
Rotate the door toward the closed position indicated by .

When the slider 6 moves in the door closing direction, the transmission member 12, which abuts the cam portion 12a against the cam portion 6b of the slider 6, is rotated in the direction of the arrow, as shown in FIG. As shown in FIGS. 3 and 4, the rotation of the transmission member 12 is transmitted to the small diameter gear 18 via the two-stage gear 17, which is rotated in the direction opposite to the arrow a in FIG. Small diameter gear 1
8 rotates, the coil spring 26 expands and rotates the worm wheel 19, which causes the worm shaft 14 to rotate at high speed. That is, when the door is closed, the clutch means 16 is engaged and the worm wheel 19 drives the worm shaft 14 to rotate at a high speed. When the worm shaft 14 rotates at high speed, the arm portion 2 of the friction member of the braking means 15
9b (see FIG. 5) expands due to centrifugal force, and its weight portion 29a rubs against the inner circumferential surface of the cup portion 30 to brake the rotation of the worm shaft 14. Since the brake piece 34a is in pressure contact with the worm shaft 14,
This also acts as a brake. The fact that the rotation of the worm shaft is braked means that the speed increasing gear train 13 that drives the worm shaft is braked, and the slider 6
Braking is applied to the rotation of the input shaft 3 that is engaged with 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, braking means 15
When the rotation of the worm shaft 14 decreases, the weight part 29a stops rubbing against the cup part 30, and the braking is released. Therefore, when the rotation of the worm shaft increases, the braking action is started, and when the rotation decreases, the braking action is released. The relationship between the door opening angle and closing speed is shown in FIG. 12, where line a represents the case where the speed adjustment device 33 is adjusted and set so that a door with a standard mass closes at a typical speed. It shows. Line b indicates that the speed adjustment device 33 of the door closer provided on a door having a standard mass is set to adjust the speed slightly faster, and line c indicates that the speed adjustment device 33 of the door closer is set to have a slower closing speed. It shows the case. This speed adjustment is performed by rotating the adjustment shaft 36 to change the spring constant of the coil spring 35, thereby changing the pressure force of the brake piece 34a against the worm shaft, that is, the braking force.

On the other hand, braking by the regulating lever 34 is continuously applied to the worm shaft 14 . Then, the door is 10° from the closed position as shown by the symbol DB in Figure 2.
When closed to the open position, double gear 1
As shown in FIG. 6, the rib 17d of No. 7 engages with the engaging portion 34d of the speed regulating lever 34 to forcibly swing the lever against the biasing force of the coil spring 35. When the regulating lever 34 is swung, the brake piece 34a is separated from the circumferential surface of the boss portion 31b, and
The braking action on the worm shaft 14 is released. Therefore, the closing speed of the door is subject to only the braking action of the braking means 15, as shown by the two-dot chain line in FIG. In addition, in FIG. 12, the broken line indicates the closing speed of the door in a state where the brake piece 34a remains in pressure contact with the worm shaft 14. The speed at which the door closes, as shown by the dashed line, is too slow to ensure that its latch is engaged, or in other words, the door does not close completely. In this regard, according to the speed adjusting device of the embodiment, since the pressure contact piece 34a is separated from the worm shaft just before the door closing position, the closing speed of the door does not decrease extremely and the door can be closed reliably. .

Now, according to the door closer of the illustrated embodiment,
The closing speed of the door changes continuously as shown in FIG. 12, and when the door closes to an opening angle of 10 degrees, the speed changes to a gentle slope. 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 6. As shown in Figure 4, the door is
In the 90° open state, the cam portion 6b of the slider
and the cam portion 12a of the transmission member 12 are the support shaft 21
It collides at a position far away from. Also, the 9th
As shown in the figure, when the door is closed to an opening angle of about 10 degrees, the abutting point of both cam parts is located closer to the center of rotation than the distance shown in FIG. 4. And the first
As shown in Figure 1, when the door is completely closed (see reference numeral D in Figure 2), both cam parts 6b and 12a are
They collide at the position closest to the center of rotation of the transmission member. The abutting point of both cam portions changes most rapidly between the opening angle of approximately 10°, which is the nearly closed position shown in FIG. 9, and the closed position shown in FIG. 11, and the transmission member 12 Increase the speed and rotate. Therefore, the rotation of the transmission member 12 whose rotational speed has been increased is further increased in speed and transmitted to the worm shaft 14 via the speed increasing gear train 13. As the rotational speed of the worm shaft increases, the period for the braking action of the braking means 15 becomes shorter, so a large braking force acts on the rotation of the speed increasing gear train 13 and the transmission member 12, that is, the movement of the slider 6, and the movement of the slider is reduced. Reduce speed. Therefore, a large braking force is applied to the input shaft 3 meshing with the rack portion 6a.
Make the closing speed of the door slow. The closing speed of the door shown in Figure 12 is reduced relatively steeply from the opening angle of 90° to 10°.
This figure only shows one model, and by suitably devising the shape of the cam portion 12a of the transmission member 12, it is possible to close the opening angle to nearly 10 degrees at a relatively fast speed.

FIGS. 10 and 11 show the transmission member 1 when the door is completely closed (see reference numeral D in FIG. 2).
2 and the slider 6 are shown. In this state, when the door is opened, the input shaft 3 rotates in the direction of the arrow, and the slider 6, which is engaged with the toothed portion 3a, moves to the right in the figure, and the coil spring 8 is energized. When the slider 6 moves, the return lever 24, which is engaged with the pin 25, follows and rotates, causing the transmission member 12 to rotate clockwise. Rotation of the transmission member 12 rotates the speed increasing gear train 13, and rotation in this direction causes the clutch means 1 to rotate.
No. 6 coil spring 26 (see FIG. 3) is wound tightly, so that the power is not transmitted to the worm wheel 19. Therefore, the braking means 15 does not operate when the door is opened. At this time, the two-stage gear 17 is rotated counterclockwise in FIG. 6 to release its rib 17d from the engaging portion 34d. Therefore, as shown in FIG. 4, the regulating lever 34 presses its pressing piece 34a against the boss portion 31b. but,
As described above, since the worm shaft 14 is not rotated, braking by the pressure contact of the pressure contact piece does not work when the door is opened.

In FIG. 3, which shows the door opened approximately 90 degrees, the slider 6 is in a position where the coil spring 8 is energized, with its non-slip portion 6c facing the cylindrical portion 3b of the input shaft. In this case, the slider 6, which is biased by the coil spring 8, is prevented from moving by the engagement of the rack part 6a with the columnar part 3b, so that the input shaft 3 cannot be rotated. This means that the action of closing the door is blocked. Therefore, even if the input shaft 3 is rotated any further, in other words, even if the door is opened more than 90 degrees, the slider 6
will no longer move. As shown by the symbol DC in FIG. 2, when the door is opened more than 90 degrees, the input shaft 3 rotates with its cylindrical portion 3b engaged with the non-slip portion 6c of the slider 6. can be stopped at any opening position of 90° or more. In such a state, the cylindrical portion 3b of the input shaft 3
Since the brake member 11 is in contact with the door, a brake is acting on the input shaft, that is, the door, and the door can be reliably stopped at any position.

In Figure 2, to close the door DC placed at any position with an opening angle of 90° or more, mark the door with the symbol
Rotate it to the position indicated by DA. Then, as shown in FIG. 3, the rack part 6c of the slider and the tooth part 3a of the input shaft 3 engage, so that the slider 6, which is biased by the coil spring 8, is moved in the direction of closing the door. The input shaft 3 will be rotated.

The closing speed of the door by the door closer is determined by rotating the adjustment shaft 36 to change the constant of the spring 35, and by changing the constant of the spring 35 between the brake piece 34a and the worm shaft 14 (boss part 3).
By changing the pressure contact force with 1b), it can be adjusted as appropriate depending on the mass of the door, the installation position, and personal preference.

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 braking by the speed regulator 33 is released is 10 degrees. Of course, it is not limited.

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.
In this case, if an adjustment knob is attached to either the protruding end 36b or 36c of the adjustment shaft 36, the workability of speed adjustment is improved. In the case of an external type, one end of a single arm is connected to the arm 4 shown in FIG. 1, the other end of which is pivotally attached to the door frame.

(Effects of the Invention) As described above, according to the door closer speed adjusting device of the present invention, the closing speed of the door can be easily and freely adjusted regardless of the mass of the door. Also,
Even if the braking action of the braking means decreases over time, this can be compensated for by operating the adjusting means, and the function and performance of the door closer can be maintained for a long time.

[Brief explanation of the drawing]

Fig. 1 is a schematic perspective view showing an example of a door closer incorporating the speed adjustment device of the present invention, Fig. 2 is a plan view showing multiple opening positions of the door, and Fig. 3 is a machine incorporating an embodiment of the present invention. FIG. 4 is a longitudinal sectional view of the same as above, FIG. 5 is a front view showing the use part of the braking means, and FIG.
The figures are an enlarged front view showing the operation of the speed regulating device of the present invention, FIG. 7 is a perspective view showing an example of the speed regulating member, and FIG.
The figure is a perspective view showing one gear in the speed increasing gear train, Figure 9 is a front view showing the positional relationship between the slider and the transmission member just before the door closes, and Figure 10 is the slider with the door closed. 11 is a front view of FIG. 10, and FIG. 12 is a diagram showing the relationship between the opening position of the door and its closing speed. DESCRIPTION OF SYMBOLS 1... Door closer, 3... Input shaft, 8... Spring means, 13... Speed increasing gear train, 14... Worm shaft, 15... Braking means, 33... Speed governor,
34...speed regulating member, 35...biasing means, 36...
adjustment means.

Claims (1)

[Claims for Utility Model Registration] An input shaft that rotates in conjunction with the opening and closing of the door, and when this input shaft is rotated in the door opening direction, energy is stored to bias the input shaft in the door closing direction. The above-mentioned apparatus includes a spring means, a speed-increasing gear train for increasing and transmitting the rotational speed of the input shaft rotated by the biasing means, and a worm shaft provided at the final stage of the speed-increasing gear train. A door closer having a braking means for braking the rotation of the input shaft, comprising: a speed regulating member movably provided toward and away from the worm shaft; and a speed regulating member substantially pressed against the worm shaft. A speed adjusting device for a door closer, comprising: a biasing device that biases the speed regulating member in a direction; and an adjusting device that adjusts the pressing force between the speed regulating member and the worm shaft.