JPH0533657Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] This invention relates to a hydraulic door closer. The present invention relates to an improvement of the conventional door closer, which is gradually closed when the door is closed, and after stopping once in the final stage of closing the door, the door is locked again and closed without a shock.

[Conventional technology]

Conventionally, in door closers that have been widely used, a rack is supported by a spring installed in a hydraulic chamber, and this rack is engaged with a pinion, which creates a link. is configured to operate.

[The problem that the idea attempts to solve]

However, conventional door closers use the entire interior as a hydraulic chamber, while the pinion is easily engaged with the lower end, in other words, the point of force is off-center, making it difficult to open the door. Sometimes it takes time and effort, and when the door is released, the return force rebounds quickly and strongly, causing the door to close quickly and strongly, which requires sealing both ends of the main body and both sides of the pinion. There are also structural complexities,
There were also many concerns about oil leaking through these sealed parts. In addition, when opening the door at any angle, there are many inconveniences when handling the door, such as having to secure the bottom end of the door with a separate support stand, and the length and thickness of the spring. Since the closer body is made large in order to prepare the installation space due to the size, there are problems in that the appearance is not very good and the product quality cannot be improved.

In addition, in order to connect two relatively thin and long arms with a hinge so that the arms can be folded, the entire force is applied to the linkage, causing wear and tear on the hinge. There is also the problem that the arm is distorted and bent.

As mentioned above, conventional door closers that have problems with the inner component and the outer link have a correspondingly high operating load, often break down, and have a short service life. .

Therefore, the first problem of this invention was to create a point-connected relationship between the cam and the piston in a hydraulic door closer so that the force would be uniform, the load would be reduced, and flexible operation would be possible. In addition, by downsizing the door closer with a simple structure, it is possible to simplify the production, improve the marketability, and enable long-term use without failure.

Another problem with this device is that during the final closing process of the door, the restoring force is temporarily eliminated to provide a safe distance to prevent the door from being shocked when closing. The purpose is to allow the door to be opened easily and quickly during the opening process, and to be able to stop by selecting various angles, thereby making the door convenient for use and entry and exit.

Another challenge of this invention was to form the arm (ARM) structure into a slide cylinder type instead of a hinge type so that it could move forward and backward in a straight line, thereby eliminating undue influence on the arm. The purpose is to improve the return force of the door.

[Means to solve the problem]

In order to solve the above problems, the hydraulic door closer according to claims 1 to 9 is provided with a piston 4 installed in an oil cylinder 2 filled with oil so as to be energized by a spring 8, and a piston rod 5. A cam 12 in a concave groove 3 that can move forward and backward in a passage 6 and is separated from the oil cylinder 2 is connected to an annular protuberance 11 at the tip of the piston rod 5.
A hydraulic passage 15 having an intermediate auxiliary passage 21 in the lower body of the oil cylinder is rotated by arms 14 and 25 connected to the door to move the piston 4 forward and backward when engaged with the oil cylinder. , and a check valve 1 is installed at its front end.
6 is installed, and the rear end constitutes small passages 18, 19, 20 that are opened and closed by a direction change valve 17, and auxiliary hydraulic pressure that communicates the front side and the rear side of the oil cylinder is installed at other positions on the main body. aisle 2
2, and the arm 14 connected to the cam drive shaft 13 is formed of a cylinder 26, and the slide arm 25 connected to the door attachment bracket 23 is inserted into the arm 14 to move forward and backward.

In the hydraulic door closer according to the second aspect of the present invention, the distance Q between the check valve 16 and the small passages 18, 19, 20 is set to the maximum reciprocating distance of the piston 4.

The hydraulic door closer according to claim 3 is such that the distance T between the rear end 22a of the auxiliary hydraulic passage 22 and the intermediate auxiliary passage 21 of the hydraulic passage 15 is made the same as the dimension of the piston 4. I made it.

In the hydraulic door closer according to claim 4, the small passages 18, 19,
The first passage 18 of 20 is located at an angle of 80 degrees to the door, and the second passage 19 is located at an angle of 90 degrees to the door.
A third passageway 20 in a position opened at an angle of
was adjusted to fit the opening position of the door with a free angle of more than 100 degrees.

In the hydraulic door closer according to a fifth aspect of the present invention, the tension of the spring 8 supporting the piston 4 can be adjusted by an adjustment bolt 10.

In the hydraulic door closer according to claim 6, the cam 12 has one part on one side of the cam 12.
The pieces were formed.

In the hydraulic door closer according to a seventh aspect of the present invention, two annular protrusions 11 are formed at the tip of the piston rod 5.

In the hydraulic door closer according to an eighth aspect of the present invention, the hydraulic passage 15 is connected to the piston 4.
It is formed with a length that communicates from the position just before the top dead center of the forward movement to the bottom dead center of the reverse movement.

In the hydraulic door closer according to the present invention, the slide arm 25 is connected to the upper and lower blocks of the bracket 23 so as to be freely rotatable upward, downward, leftward, and rightward.

[Effect]

With this hydraulic door closer,
The relationship between the cam and the piston is formed in a point connection type, which makes the force uniform, reduces the load, provides flexible operation, has a simple structure and is compact, and is easy to manufacture and has good marketability. In addition to improving performance, it also enables long-term use without failure. In addition, since the arm is a linear sliding type using a cylinder, compared to the conventional folding type,
It looks good, does not easily deform, and provides good force transmission.

〔Example〕

A preferred embodiment of this invention as described above will be described below based on the drawings.

In the hydraulic door closer according to this invention, for example, as shown in FIG. 1, the main body 1 is fixed to the upper edge of the door, and the tips of arms 14 and 25 extending from the main body 1 are fixed to the frame of the doorway. It is designed to be connected to a bracket 23 which is attached to the frame.

As shown in FIGS. 2 to 7, an oil cylinder 2 filled with oil is formed on one side of the door closer body 1, and a recessed groove portion 3 is formed on the opposite side.
The rod 5 of the piston 4 installed in the oil cylinder 2 is inserted into the passage 6 so that it can move forward and backward along the passage 6, and a packing 7 is formed between the oil cylinder 2 and the passage 6. This prevents oil from flowing out.
The piston 4 is elastically supported by a spring 8 and always receives a force that tends to move it forward. The tension (elastic force) of the spring 8 is adjusted by being supported by a spring seat 9 inserted into the threaded portion of the adjustment bolt 10. Two annular protuberances (ring jaws) 11 are formed near the tip of the piston rod 5, which is formed to be relatively thin. It is meshed with one tooth of the cam 12. Therefore, the piston 4 is operated to move forward and backward by the rotation of the cam 12. On the other hand, cam 1
The second drive shaft 13 is located externally through the side wall of the main body and connected to the arm 14. Therefore,
The cam 12 has arms 14 and 25 connected to the door.
The piston 4 can be moved forward and backward within the passage 6.

A hydraulic passage 15 is formed below the oil cylinder 2 in the door closer body 1, and this hydraulic passage 15 communicates with the piston 4 immediately before the top dead center of the forward movement and the bottom dead center of the piston 4 in the backward movement. A check valve 16 is installed at the front end of the oil cylinder 2, and three small passages 18, 19, 20, which are opened and closed by a direction change valve 17, are formed at the rear end. Hydraulic passage 1
An intermediate auxiliary passage 21 equipped with an adjustment tool 21a is connected to the rear side of the check valve 16 at 5. Therefore, as shown in FIG. 3, the check valve 1 installed on the front end side of the oil cylinder 2
The distance Q between the piston 4 and the small passages 18, 19, 20 (the location of the direction change valve 17) is
This corresponds to the maximum reciprocating distance of .

An auxiliary hydraulic passage 22 is provided on the side of the hydraulic passage 15. The front end of the auxiliary hydraulic passage 22 communicates with the front end of the oil cylinder 2, and the rear end 22a communicates with the front position of the small passage. This rear end 2
The distance T between the piston 2a and the auxiliary passage 21 is
The piston 4 can close both holes at the same time. The position of the door at this time will be at an angle of approximately 30 degrees from the closed state,
The brake is applied to the closing operation at a position just before the door is completely closed, thereby alleviating the shock during closing.

The opening and closing of the small passages 18, 19, and 20 are controlled by the direction control valve 17. When the direction control valve 17 is aligned with the first small passage 18 and opened, this small passage 18 opens the door approximately 80 degrees.
The second mini-passageway 19 stops the door at an angle of about 90 degrees. On the other hand, the third small passage 20 is for stopping the door at a free angle.

An arm 14 connected to the drive shaft 13 of the cam 12
A cylinder 26 is provided inside the cylinder 26, and a circular bar slide arm 25 is inserted into the cylinder 26.
is constructed so that it can only move forward and backward in a straight line in that state. The rear end of the slide arm 25 is rotatably connected to an upper and lower block 24 which is pivotally connected to a bracket 23 attached to the door so as to be rotatable in the vertical direction. That is, the rear end of the slide arm 25 is connected in a universal joint type.

The operating state of this device constructed as described above will be explained in detail below.

First, the door closer body 1 is attached to the door, and the bracket 23 is attached to the wall surface. On the contrary, the door closer body 1 can be attached to the wall and the bracket 23 can be attached to the door.

The arms 14, 25 rotate around the drive shaft 13, and the door rotates around its own hinge H, so the longer the distance between the drive shaft 13 and the hinge, the longer the arms 14, 25 become. Therefore, in the device according to this invention, it is preferable to install the drive shaft 13 close to the hinge side. In other words, it is advantageous in the force transmission process to mount the drive shaft 13 so that the radius of rotation of the drive shaft 13 is as short as possible when viewed from the hinge portion.

On the other hand, the internal cam 12, which is integrally formed with the drive shaft 13, rotates in the opposite direction to the direction of rotation of the door by the angle generated when the door is opened. Displayed as A, B, and C. Therefore, the piston rod
The annular protrusion 11 provided on the rod 5 moves to the right while compressing the spring 8 due to the movement of the cam 12. At this time, the hydraulic pressure moves to the left via the hydraulic passage 15 and the auxiliary hydraulic passage 22 due to the movement pressure of the piston 4, thereby pushing the piston 4 in the opposite direction. In particular, since the amount of hydraulic pressure transferred through the two hydraulic passages 15 and 22 is relatively large, the door opens easily and can be opened effortlessly and easily without requiring a large amount of human power. .

In contrast to the above, when the door is pulled open, the main body 1 of the device according to the invention can be turned over and installed so that the drive shaft 13 is at a lower position. In this case, the drive shaft 13 can be mounted so as to be located near the hinge.

The operating states of the arms 14, 25 and the main body 1 will be explained below.

When a closed door is pushed open,
Since the drive shaft 13 rotates around the hinge H, the slide arm 25 connected to the bracket 23 moves the drive shaft 13 by the rotational distance of the drive shaft 13.
from the cylinder 26 of the arm 14 connected to. This state is represented by A, B, and C in FIG. If the door is opened more than about 100 degrees in the above-described manner, the piston 4 closes the small passage and blocks the movement of hydraulic pressure, and in this case, the cam 12
teeth are separated from the annular ridge 11 of the piston rod 5. Therefore, the cam 12 only rotates idly, and the piston 4 no longer moves. In this state, the hydraulic pressure and spring force do not reach the door, so the control force is completely removed from the door, and the idling door can be stopped at any position. be.

In other words, after the door angle exceeds about 100 degrees,
No matter where it is placed, the annular raised part 11
has come off from the cam 12, and the piston 4
receives forward force from spring 8, but cam 1
2 and cannot move forward, so the door is in a free rotation state.

When the door in such a free state is pulled within a range of about 100 degrees for the purpose of closing, or when the door is placed within a range of about 100 degrees when opening the door, the cam 12 is reversed. As it rotates, its teeth mesh with the annular protrusion 11, the piston rod 5 begins to retreat, and the piston 4 begins to move forward due to the elastic restoring force of the spring 8. At this time, the arms 14 and 25 receive rotational force in the direction of rotation of the cam 12, but since the slide arm 25 is received in the cylinder 26 of the arm 14 and its working length is shortened, the door It rotates smoothly due to the conniversal joint type joint that absorbs shock at different angles.

This movement of the piston 4 opens the small passage section, and the hydraulic pressure moves from the left side to the right side via the intermediate auxiliary passage 21 and the hydraulic passage 15.
The check valve 16 is closed and the intermediate auxiliary passage 21
In such a state that the hydraulic pressure is transferred through the chisel, the moving speed of the hydraulic pressure becomes very low, so the forward speed of the piston 4 becomes slow, and as a result, the door is controlled to close quickly. It is. Such a situation is shown in FIG. 8A. Thus, the speed at which the door is closed is proportional to the speed of hydraulic movement. Therefore, the speed at which the door is closed is slower than the speed at which the door is opened.

When the door that is being closed is about to be completely closed, the piston 4 will simultaneously block the hydraulic passage 15 and the auxiliary hydraulic passage 22, as shown in FIG. 8B. Since there is no movement at all, a temporary brake is applied to the closing door. While this braking is applied, the piston moves only by the elastic force of the spring 8, and as soon as the piston 4 passes this braking point (complete area),
Hydraulic passage 15 and auxiliary hydraulic passage 22 are re-opened to allow strong movement of hydraulic pressure. The door is then locked with acceleration. In other words, the moment when the piston 4 closes the hydraulic passage 15 and the auxiliary hydraulic passage 22 is when the door is closed to an angle of about 30 degrees, and from that moment on, the auxiliary hydraulic passage 22 gradually opens and the hydraulic pressure shifts slightly to the right side. As the piston 4 continues to move backward and the auxiliary hydraulic passage 22 is completely opened, the door is closed at an accelerated rate (the door is tightened to about 10 degrees). This is what happens. In this way, the door is about 10 degrees below the point of about 30 degrees.
This angular range serves as a safety device, since it gradually closes with a sharp drop in speed up to the point in time.

As shown in FIG. 10, if there is an obstacle S such as a vertical wall or a glass wall within the range in which the door opens, adjust the direction adjustment valve 17 to, for example, 80 degrees to match the small passage 18. If this is done, the moment the piston 4 moves forward to a position where it closes the small passage 18, the hydraulic passage 15 becomes blocked and the piston 4 no longer moves forward. Of course, at this time, since the cam 12 is engaged with the annular protuberance 11 of the piston rod 5, the door will no longer open and a collision with the obstacle S is prevented. This state is shown in Figure 11A.
is shown.

When it is desired to open the door to 90 degrees, the directional valve 17 is adjusted as shown in FIG. 11B to fit the intermediate small passageway 19. Then, based on the same principle, the door will always open to about 90 degrees and stop there.

However, when there is no obstacle S near the door and the door is used under normal conditions, and when it is desirable to open the entire range, the direction control valve 17 is set to the third position as shown in FIG. 11C. small passageway 20
I'll do it accordingly. Then, as explained above, from the moment the piston 4 moves forward and closes the small passage 20, the teeth of the cam 12 are released from the annular protrusion 11, and the cam 12 only rotates idly.

In addition, when it is necessary to change the closing speed of the door due to differences in door size and weight, the door speed can be adjusted by turning the adjustment bolt 10 to adjust the tension of the spring 8. This problem can be solved by making the desired changes.

In addition, the slide arm 25 is attached to the bracket 2 in a conniversal joint type that can rotate vertically and horizontally.
3, it can withstand friction, deformation, distortion, and damage caused by long-term use, and always operates smoothly.

[Effect of idea]

The hydraulic door closer according to the invention according to claims 1 to 9 has an arm configured to slide in a linear direction, so it has a better appearance and does not undergo deformation compared to a conventional folding type. for good force transmission.

In the hydraulic door closer according to this invention, the annular protrusion 11 formed on the piston rod 5 and the cam 12 having one tooth are engaged with each other, so that force can be easily transmitted.

The hydraulic door closer according to this invention also has the advantage of being able to stop the door at any position after it exceeds the normal opening/closing range of 80 to 90 degrees. In addition, a separate hydraulic passage 15
It is also possible to adjust the speed at which the door closes by installing a moving hydraulic pressure adjustment device thereon and adjusting the amount of movement of the hydraulic pressure.

The hydraulic door closer according to this invention does not change the dimensions of the closer according to the size of the door or the weight of the door, but instead adjusts the size of the door by turning the spring tension adjustment bolt 10 to move the spring seat 9 forward or backward. Alternatively, since the tension of the spring 8 can be adjusted to suit the weight, it has the advantage that it can be widely used for doors in any condition.

[Brief explanation of the drawing]

FIG. 1 is a perspective view showing how the hydraulic door closer according to the invention is installed and used on a door. FIG. 2 is an exploded perspective view showing the overall configuration. FIG. 3 is an arrangement diagram of hydraulic passages in the bottom part. FIG. 4 is a sectional view taken along line a-a in FIG. 3. FIG. 5 is a sectional view taken along the line bb in FIG. 3. FIG. 6 is a sectional view taken along line c-c in FIG. 3. FIG. 7 is a sectional view showing the state in which the piston moves as the door is opened, where A shows the fixed state before operation, B shows the state at the start of reverse movement, and C shows the state after reverse movement. shows. FIG. 8 is a cross-sectional view showing the state in which the piston moves as the door is closed, where A shows the forward movement start state and B shows the safe speed state where the door is closed at an angular position of about 30 degrees. , C indicates the forward completion state.
FIG. 9 is a plan view showing the open and closed states of the door, where A shows the closed state, B shows the free rotation state opened at an angle of 90 degrees, and C shows the open state of the door at an angle of 90 degrees or more. It shows an open and freely rotating state, and D shows a state where it is temporarily stopped at an angular position of 30 degrees in the process of being closed. FIG. 10 is an explanatory diagram of the section operation by angle in the opening/closing process of the door. FIG. 11 is an enlarged sectional view showing the use state of the direction change valve, where A shows the state adjusted so that the door can be opened at an angle of about 80 degrees, and B shows the state adjusted so that the door can be opened at an angle of about 90 degrees. Shows the state where the door is adjusted to open at an angle of
C indicates a state in which the door is adjusted to open at an angle of approximately 100 degrees or more. Explanation of symbols for main parts of the drawings, 2...oil cylinder, 3...concave groove, 4...piston,
5... Piston rod, 6... Passage, 8... Spring, 10... Adjustment bolt, 11... Annular protrusion, 12... Cam, 13... Cam drive shaft, 14,
25...Arm, 15...Hydraulic passage, 16...Check valve, 17...Direction change valve, 18,
19, 20...Small passageway, 21...Auxiliary passageway, 2
2...Auxiliary hydraulic pressure passage (auxiliary hydraulic pressure movement path), 22a
...Rear end, 23... Bracket, T... Spacing,
Q...Distance.

Claims (1)

[Scope of claims for utility model registration] 1. Oil cylinder filled with oil 2.
A piston 4 is installed inside the piston so as to be energized by a spring 8, and the piston rod 5 is inserted into the passage 6.
Oil cylinder 2
The cam 12 in the concave groove 3 separated from the arm 1 connected to the door is engaged with the annular protuberance 11 at the tip of the piston rod 5.
4 and 25 to move the piston 4 forward and backward, a hydraulic passage 15 having an intermediate auxiliary passage 21 is formed in the lower body of the oil cylinder, and a check valve 16 is installed at the front end thereof. There is a direction change valve 17 at the rear end.
Small passages 18, 19, 2 whose opening and closing are adjusted by
0, and an auxiliary hydraulic passage 22 that communicates the front side and the rear side of the oil cylinder is formed in another position of the main body, and an arm 14 connected to the cam drive shaft 13 is formed in the cylinder 26. A hydraulic door closer that moves forward and backward with a slide arm 25 connected to a door mounting bracket 23 inserted into the door. 2 Check valve 16 and small passages 18, 19,
2. The hydraulic door closer according to claim 1, wherein the distance Q between the piston 4 and the piston 20 is the maximum reciprocating distance of the piston 4. 3. The hydraulic door closer according to claim 1, wherein the distance T between the rear end portion 22a of the auxiliary hydraulic passage 22 and the intermediate auxiliary passage 21 of the hydraulic passage 15 is the same as the dimension of the piston 4. 4 The first passage 18 of the small passages 18, 19, 20 is located at a position where the door opens at an angle of 80 degrees, the second passage 19 is located at a position where the door opens at an angle of 90 degrees, and the third passage 19 is located at a position where the door opens at an angle of 90 degrees. The second passage 20 has a door.
The hydraulic door closer according to claim 1, wherein the hydraulic door closer is adjusted to fit an opening position with a free angle of 100 degrees or more. 5. The hydraulic door closer according to claim 1, wherein the tension of the spring 8 supporting the piston 4 can be adjusted by an adjustment bolt 10. 6. The hydraulic door closer according to claim 1, wherein one tooth is formed on one side of the cam 12. 7. The hydraulic door closer according to claim 1, wherein two annular protuberances 11 are formed at the tip of the piston rod 5. 8. The hydraulic door closer according to claim 1, wherein the hydraulic passage 15 is formed with a length that communicates with the piston 4 from a position immediately before the top dead center of the forward movement to the bottom dead center of the backward movement. 9 Place the slide arm 25 on the bracket 23.
2. The hydraulic door closer according to claim 1, wherein the hydraulic door closer is connected to the lower block so as to be freely rotatable upward, downward, leftward, and rightward.