JPH052077B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) This invention relates to a door closer that automatically closes an open door.

(Prior Art) Conventionally, the door closer that has been put into practical use most often is an oil-type door closer, as shown in FIG. This door closer 80 houses a spring, oil, rack, pinion, etc. (not shown), and includes a door closer main body 81 fixed to the upper edge of a door (not shown), and a base end 8 thereof.
2a is rotatably attached to a door frame (not shown), and its base end 83a.
is integrally connected to the shaft of the pinion in the main body by a screw 84, and the other end 83b of the second link arm 8 is pivotally connected to the other end 82b of the first link arm.
It consists of 3. When the door is opened, the relative angle between the door closer body 81, which is integrated with the door, and each link arm changes, and the pinion inside the body 81 moves the rack, thereby accumulating the spring. When the door is closed by the release force of the spring, the flow resistance of the stored oil is used to exert a damper effect on the closing speed of the door. The door closer 80 shown in FIG. 13 is attached to a left-opening door that rotates around the left edge of the door (not shown), and is attached to the base end 8 of the second link arm 83.
3a is fixed to a pinion shaft (not shown) protruding from the upper surface 81a of the main body 81 in the figure. To attach the door closer 80 to a right-hand door, the main body 81 is turned upside down and the base end of the second link arm is attached to the pinion shaft (not shown) protruding from the bottom surface 81b in the figure. 83a
to fix. The protruding end of the pinion shaft to which the link arm is not fixed is closed with a cap to prevent oil leakage and to maintain aesthetic appearance.

In addition, as a door closer, the mainspring is charged when the door is opened, and when the door is closed, the full release force is transmitted to the mechanical (centrifugal force) governor or electromagnetic governor using a gear train, creating a damper effect. So-called mechanical door closers have also been proposed. and,
Even in this mechanical type, the main components are the door closer body, the first link arm, and the second link arm.
It consists of a link arm. For example, as shown in Japanese Patent Publication No. 52-3227, the end of the shaft to which the base end of the first arm is connected projects from the upper and lower surfaces of the main body, and the projecting end is opened to the left. It is selectively used for doors that open to the right and those that open to the right.

(Problem to be solved by the invention) Oil-type door closers use the flow resistance of the oil sealed in the cylinder to obtain a damping effect, so the damping effect varies depending on changes in temperature. . In addition, in the oil type,
There is a drawback that the sealed oil leaks,
There is a problem with durability. Furthermore, since it is necessary to prepare a casing including a cylinder that can withstand large spring force and hydraulic pressure, there is a problem that the door closer itself has to be bulky and heavy. If the weight of the door closer is large, the installation work becomes troublesome. In particular, when the opening direction of the door and the left and right specifications of the door closer are different, changing the mounting position of the link arm relative to the main body is troublesome and the efficiency of the mounting work is reduced.

Additionally, mechanical door closers do not suffer from variations in damper effectiveness due to temperature changes or oil leakage, but the gear train is longer and the overall structure, including the door closer itself, is larger. There is a problem in that the mounting process is complicated, as mentioned above, which makes the installation work troublesome.

Regardless of the method, door closers have
It goes without saying that the door must be closed reliably, but it is also important that the door have an appearance that does not spoil the beauty of the area around the door. However, the door closers that are currently in practical use are oriented toward practicality, and the reality is that the door closer body is attached to the door, which spoils the aesthetic appearance of the area around the door.

An object of the present invention is to provide a door closer that has no variation in damper effect due to changes in temperature, does not leak oil, is small in size and lightweight, and does not impair the beauty of the area around the door.

(Means for Solving the Problems) The door closer of the present invention includes a first arm whose both ends are symmetrically formed, and whose one end is pivotally connected to the door (or door frame); a second arm pivotally connected to the door frame (or door);
a pivoting means for selectively pivoting the other end of the front or back surface of the first arm to the other end of the second arm; a driving force accumulating means for accumulating driving force in the direction of closing the door as the door rotates; a gear train for transmitting the rotation to the driving force accumulating means and transmitting the driving force accumulated in the driving force accumulating means to the door; a braking means that rotates and applies a brake to the release force; and a braking means that is stored in the first arm along its longitudinal direction and is disposed between the braking means and the driving force accumulation means, and that a speed increasing gear train for transmitting the releasing force of the accumulating means to the braking means, and by reversing the front and back of the first arm and selectively pivotally connecting it to the second arm, It is characterized by being able to be switched between left-hand and right-hand doors.

(Function) The first arm is pivotally connected to the second arm with its front and back sides selected depending on the opening direction of the door. Opening the door energizes the drive force storage means via a gear train. When the door opening function is released, the door is rotated in the closing direction by the driving force accumulated in the driving force accumulating means. At this time, the releasing force of the driving force storage means is braked by the braking means operated via the speed increasing gear train.

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

In FIG. 1, a door closer 1 consists of a first arm 2 and a second arm 3, both arms being pivotally connected to each other by an arm shaft 4. As shown in FIG. Although details will be described later, the first arm 2 is pivotally attached to the second arm 3 with its front and back sides (indicated by an upper case 2b and a lower case 2c) selected depending on the opening direction of the door to which it is attached. As shown in FIG.
is pivotally attached to the door 5 at one end 2a via a first arm fitting 6 fixed to the door 5 and a first shaft 7. One end 3a of the second arm 3 is pivotally attached to the door frame 8 via a pin 10 and a second arm mounting bracket 9 fixed to the upper frame (not shown) of the door frame 8. The door 5, which is a right-hand door, is supported by a door frame 8 by a door hinge 12 so as to be openable and closable. In FIG. 2, a solid line indicates a state in which the door 5 is closed, a dashed-dotted line 5A indicates a state in which the door is opened approximately 90 degrees, and a dashed-double line 5B indicates a state in which the door is braked as it rotates in the closing direction. The first arm 2 shows the position where the door starts to open (or the position opened at a predetermined angle from the closed position), and the first arm 2
The relative positions of the second arm 3 and the second arm 3 have changed. Although the door 5 can be opened more than 90 degrees, it is shown in FIG. 2 at an approximately 90 degree opening position for convenience of illustration.

The details of the structure of the door closer 1 will be explained based on FIGS. 3, 4, and 5.

The second arm mounting bracket 9 has its bent portion 9a fixed to the upper frame of the door frame 8 (see FIG. 2). Second
One end 3a of the arm 3 and the mounting bracket 9 are pivotally connected to each other by a pin 10. The first arm 2 is
It consists of an upper case 2b and a lower case 2c,
These cases are overlapped with each other and then fixed by a plurality of fixing screws 13, 13, . . . . A first shaft 7 consisting of a square shaft is inserted into one end 2a of the first arm 2, and both ends thereof are fitted into square holes 6a, 6a of the first arm mounting bracket 6, and then screws 14, It is fixed at 14. The front and back surfaces of one end 2a of the first arm 2 (the outer surfaces of the upper case 2b and the lower case 2c) are formed in a symmetrical shape. The first arm fitting 6 is bent to have a U-shaped cross section, and its base 6b is fixed at a proper position on the door 5 (see FIG. 2).

An arm shaft 4 is inserted through the other end 3b of the second arm 3 and the other end 2d of the first arm 2, and the two arms are pivotally connected. One end 4a of the arm shaft 4 has a shaft hole 2l that passes through the upper case 2b and the lower case 2c.
2m, and the E-ring 15 is engaged with the protruding end thereof, and the other end 4b is passed through the shaft hole 3d passing through the second arm, and the protruding end thereof is caulked. Therefore, when the E-ring 15 is removed from the arm shaft 4, the first arm 2 and the second arm 3 can be separated from each other. The shaft holes 2l and 2m formed in the first arm are formed symmetrically on the front and back sides of the first arm 2 (upper case 2b and lower case 2c), and constitute a pivoting means with the arm shaft 4. ing. The other end 2d of the first arm 2 has shaft holes 2l, 2
The shapes of the front and back sides including m are formed symmetrically.

The first shaft 7 located within the first arm 2 has a
The No. 1 gear 16 is supported by fitting into the square hole 16a. Therefore, the No. 1 gear 16 is substantially integrated with the door 5 (see FIG. 2) via the first arm fitting 6. Boss portions 16b, 16b at both ends of the No. 1 gear 16 are rotatably fitted into shaft holes 2e, 2e of the upper and lower cases 2b, 2c.

The lower case 2c includes a mainspring storage box 17, a fourth shaft 18 as a driving force output shaft, and one end 19 thereof.
Engagement notch 17a formed at the winding opening of the storage box
A driving force accumulating means 21 consisting of a mainspring 19 (see FIG. 9) whose other end 19b is fixed to a locking pin 20 fixed to the fourth shaft is disposed. A cover 17b is fixed to the mainspring storage box 17. The mainspring storage box 17 is fixed by tightening the cover 17b to the lower case 2c with fixing screws 22, 22. The fourth shaft 18 is rotatably supported by the mainspring storage box 17 so as not to move in the axial direction. The protruding end 18a of the No. 4 shaft 18 protruding from the cover 17b has a part of its peripheral surface cut off, and engages with and supports the No. 4 gear 23 as a cylinder gear.

A gear train 26 including a second gear 24 and a third gear 25 is disposed between the fourth gear 23 and the first gear 16. 2nd gear 24 and 3rd gear 25
connect the respective ends to upper case 2b and lower case 2.
It is rotatably supported by the second shaft 27 and the third shaft 28 which are fitted into the shafts c. The second gear 24 is
A small-diameter tooth portion 24a that meshes with the No. 1 gear 16 and a large-diameter tooth portion 2 that meshes with the small-diameter tooth portion 25a of the No. 3 gear 25.
It consists of 4b. The third gear 25 is made up of the small-diameter tooth portion 25 a and a large-diameter tooth portion 25 b that meshes with the fourth gear 23 . The details will be explained later, but
This gear train 26 transmits the rotation of the No. 1 gear 16 to the No. 4 shaft 18 at an increased speed to wind up the mainspring 19 and store the power when opening the door, and decelerates the releasing force of the mainspring 19 when closing the door. The signal is then transmitted to the No. 1 gear 16.

The first arm 2 is provided with a braking means 29 . This braking means 29 includes a worm shaft 31 on which a worm 30 is formed, a pair of friction plates 32, 32 press-fitted into this shaft, a friction plate holder 33 press-fitted into the shaft, and a friction plate restraining ring 34. and friction plate 32
It consists of a braking cup 35 that is close to and surrounds the outer periphery of the brake. Braking cup 35
is fixed by press-fitting its flange 35a into a mounting groove 2f formed in the lower case 2c and a mounting groove (not shown) formed in the upper case 2b. The worm shaft 31 is rotatably supported by fitting one end 31a into a bearing hole formed in the ceiling of the cup and fitting the other end 31b into a bearing groove 2g formed in the lower case 2c. ing. A shaft holding portion (not shown) formed in the upper case 2b engages with the bearing groove 2g, and supports the shaft end 31b engaged with the groove. The friction plates 32, 32 are
In the illustrated example, it is made of an elastic material of rubber or rubber-like material. Each of the friction plates 32 has an elastically deformable arm portion 3 extending in a toe shape.
2a and 32a are formed. This arm portion 32a
The outer peripheral edge of the worm shaft 31 is separated from the inner peripheral surface of the cup when the worm shaft 31 rotates at a predetermined speed or less, but when the worm shaft 31 rotates at a predetermined speed or higher, it is elastically deformed outward in the circumferential direction due to centrifugal force. The inner circumferential surface of the braking cup 35 is rubbed to apply a brake to the rotation of the shaft.

A one-way clutch means 36 and an intermittent transmission means 37 are provided between the driving force storage means 21 and the braking means 29.
A speed increasing gear train 38 is provided.

The speed increasing gear train 38 includes a large-diameter fifth gear 39 that meshes with the fourth gear 23, a full-periphery tooth portion 40a, and a tooth portion 40.
A small-diameter No. 6 gear 40 formed with a toothless portion 49b having a diameter of
Second tooth portion 41 that meshes with tooth portion 41a and tooth portion 40c
b, the large-diameter No. 7 gear 41, and the first
A No. 8 gear 42 is formed with a small-diameter tooth portion 42a and a large-diameter tooth portion 42b that mesh with either the tooth portion 41a or the second tooth portion 41b, and a No. 9 gear 43 with a small diameter that meshes with the large-diameter tooth portion 42b. This consists of a worm gear 44, which together with this No. 9 gear constitute a one-way clutch means 36, and the aforementioned worm 30 located at the final stage of the gear train. This speed increasing gear train 3
Reference numeral 8 increases the speed of the release force of the mainspring 19 of the driving force accumulating means 21 and transmits it to the worm shaft 31 of the braking means 29. Note that the speed increasing gear train 38 in the illustrated embodiment includes an intermittent transmission means 37, which will be described later.
Since the one-way clutch means 36 is incorporated, the releasing force of the mainspring 19 is not always transmitted at increased speed.

The fifth gear 39 is the cover 17 of the mainspring storage box.
It is rotatably supported by a support shaft 45 fixed to b. The other end of the support shaft 45 is fitted into the upper case 2b. The 6th gear 40, the 7th gear 41, the 8th gear 42, the 9th gear 43, and the worm gear 44 are
No. 6 shaft 46, No. 7 shaft 47, No. 8 shaft 4 whose respective ends are engaged with lower case 2c and upper case 2b.
They are rotatably supported by shafts 49 No. 8 and No. 9, respectively.

The one-way clutch means 36 is a spring clutch having a No. 9 gear 43 as an input portion and a worm gear 44 as an output portion. coil spring 50
is wound around the cylindrical portion 43a of the gear 43, and its one end 50a is locked in the notch 43b. The spring 50 has its coil portion in sliding contact with the inner circumferential surface 44a of the worm gear 44 (see Fig. 4), and when the door is opened when the No. 9 gear 43 rotates in the direction of arrow a (see Fig. 3), this By rotating in the tightening direction, the rotation of the No. 9 gear is not transmitted to the worm gear 44. No. 9 gear 43 is arrow a
When closing the door, which rotates in the opposite direction, the coil spring 50 is expanded to transmit the rotation of the gear 43 to the worm gear 44, thereby driving the worm 30 to rotate at a high speed.

The intermittent transmission means 37 is incorporated in a part of the speed-increasing gear train 38, and is connected to the sixth gear 49 and the seventh gear 4.
It consists of No. 1 and No. 8 gears 42. As shown in FIG. 3, FIG. 5, FIG. 7, and FIG.
a is formed, and a toothless portion 40b having one tooth portion 40c is formed in the lower half. Tooth portion 40c
is formed continuously with one tooth of the full-periphery tooth portion 40a. The No. 7 gear 41 has a first toothed portion 41a in which a first toothless portion 41c is formed on the half circumference of the upper half in the axial direction, and a second toothed portion 41a in which a second toothless portion 41d is formed on the half circumference of the lower half. It consists of a tooth portion 41b and a full circumference toothless portion 41f that is formed at the lower end of the second toothed portion 41b and has the same diameter as the second toothless portion 41d. First tooth portion 4
The teeth located at both ends of the second tooth portion 1a and the teeth located at both ends of the second tooth portion 41b are formed continuously with each other, as shown by reference numerals 41e and 41e. The tooth thickness of the small diameter tooth portion 42a of the No. 8 gear 42 is formed to a thickness that allows meshing with the second tooth portion 41b of the No. 7 gear 41. At the lower end of the small diameter tooth part of No. 8 gear 42,
A circumferential portion 42c with a diameter slightly larger than the tip circle of the small diameter tooth portion 42a is formed, and from this circumferential portion, an arc portion 42d (with a diameter slightly larger than the full circumference missing tooth portion 41f of the No. 7 gear 41) is formed. (See Fig. 6)
2e is formed. When the full circumferential tooth portion 40a of the rotating No. 6 gear 40 is engaged with the first tooth portion 41a of the No. 7 gear 41, the rotation of the gear 40 advances the No. 7 gear 41 one tooth at a time, but Part 40c
corresponds to the first toothless portion 41c, the tooth portion 4
0c engages with the second tooth portion 41b of the No. 7 gear 41, so that one rotation of the No. 6 gear 40 advances the No. 7 gear 41 by two teeth. In addition, No. 8 gear 42
The protruding portion 42e is the entire circumference missing tooth portion 41 of the No. 7 gear 41.
When facing f (see FIG. 6), the rotation of the No. 7 gear is not transmitted to the No. 8 gear 42. These intermittent feeding actions will be explained in detail later.

In FIGS. 3, 4, and 10, a stopper mounting recess 2h is formed in the other end 2d of the upper case 2b. A door positioning means 53 for positioning the door 5 in the open position is housed in the stopper mounting recess 2h. The other end 3b of the second arm 3
A positioning cam 51 inserted through the arm shaft 4 is fixed to the lower surface of the arm shaft 4 with screws 52, 52. The positioning cam 51 has a recess 51a formed therein. A base plate 54 is fixed to the bottom of the recess 2h by screws 55a and 55b. screw 5
5a, 55b pass through holes 2n, 2n of the upper case 2b, and are female threaded portions 2 formed in the lower case 2c.
It is screwed to ia and 2i. The stopper lever 5 is attached to the main plate 54 by a pin 56 fixed thereto.
7 is pivoted. A spring guide 58 is pivotally attached to the free end of the stopper lever. One end of the spring guide 58 is slidably inserted into a guide hole 54b of a rising portion 54a of the base plate. Step part and rising part 5 of spring guide 58
4a is an extensible coil spring 59.
is wound around the stopper lever 57 to urge the stopper lever 57 closer to the arm shaft 4. A cam follower 60 is rotatably mounted on the stopper lever 57. The cam follower 60 has its peripheral surface pressed against the positioning cam 51 by the elasticity of the coil spring 59, but the two are shown separated in FIG.

The positioning cam 51 can select the opening position of the door 5 by selecting the angle at which it is attached to the second arm 3. The mounting angle of the cam 51 is
This is determined depending on which hole is selected from the plurality of attachment holes 3c, 3c formed in the other end 3b of the second arm 3.

On the other hand, on the surface of the other end 2d of the lower case 2c (the back surface of the other end of the first arm for right-hand opening), a door positioning means 53 is stored, which is used when the door closer 1 is attached to a left-hand opening door. A recess 2j is formed. The inner surface of this recess 2j has a third
As shown in the figure, screw holes 2k and 2 are used for screwing together screws 55a and 55b for attaching the base plate 54.
i is formed.

The operation of the embodiment configured as above will be explained.

In FIG. 2, when the door 5 is closed, the door closer 1 is moved to the first position as shown by the solid line.
The arm 2 and the second arm 3 are folded so that they overlap each other. At this time, the first arm 2
The relative positions of each means and gear train housed in
The structure is as shown in Figure 5. That is, the mainspring 19 of the driving force accumulating means 21 is in an unwound state, as shown in FIG. 9a. However, the mainspring 19 placed in this state does not have its stored power completely released, but still has some remaining power. The intermittent transmission means 37 connects continuous tooth portions 41e and 41e at both ends of the first and second tooth portions 41a and 41b of the No. 7 gear 41 to the full circumferential tooth portion 40a of the No. 6 gear 40 and the No. 8 gear 42. It meshes with the small diameter tooth portion 42a of. The tooth portion 40c of the No. 6 gear 40 is in the illustrated position, and the protrusion portion 42e of the No. 8 gear 42 is also in the illustrated position. Also, door 5
positioning cam 5 for positioning the
1 is placed in the position shown in FIG. In addition, in FIG. 10, it is assumed that the positioning cam 51 is attached to the second arm 3 so as to hold the door 5 in a position that is open, for example, 120 degrees from the closed position.

When the door 5 placed in the state shown by the solid line in FIG. 2 turns toward the position shown by the two-dot chain line, that is, when the door is opened, the The number gear 16 is the door hinge 12
It can be revolved around. When the No. 1 gear 16 revolves, the No. 2 gear 24 meshing therewith is rotated in the direction of the solid line arrow, as shown in FIG. The rotation of the second gear 24 is transmitted to the fourth gear 23 via the third gear 25. The gear train from No. 4 gear 23 to No. 2 gear 24 is from No. 2 gear 24 to No. 4 gear train.
When transmitted to the number gear 23, it acts as a speed increasing gear train and rotates the fourth gear 23 by a larger rotation angle than the rotation angle of the second gear 24. When the No. 4 gear 23 rotates, the No. 4 shaft 18 is rotated, winding up the mainspring 19 whose one end is locked to the No. 4 shaft 18, and accumulating driving force.

In FIG. 5, when the No. 4 gear 23 is rotated in the direction of the solid line arrow, the gear No. 5 meshing with the No. 4 gear 23 is shown in FIG.
The number gear 39 is rotated, and the number 6 gear 40 is rotated in the direction of the solid line arrow. Since the No. 6 gear 40 has its full circumferential tooth portion 40a engaged with the first tooth portion 41a of the No. 7 gear 41, the No. 7 gear 41 is rotated in the direction of the solid line arrow. At this time, the second tooth portion 41b of the seventh gear 41 is meshed with the eighth gear 42, so the gear 42 is rotated in the direction of the solid line arrow. The large diameter tooth portion 42b of the No. 8 gear 42 is the No. 9 gear 4.
3 and rotate it in the direction of the solid line arrow. When the No. 9 gear 43 rotates in the direction of the arrow,
As the coil spring 50 (see FIG. 3) rotates in the direction of the arrow a and tightens, the frictional force with the inner circumferential surface 44a of the worm gear 41 decreases, and the worm gear 44 meshing with the worm 30 decreases. cannot be rotated. Therefore, door 5
When opening, the one-way clutch means 36 acts to break the speed increasing gear train 38 in the middle, so the braking means 29 does not operate. Therefore, less force is required when opening the door.

When the door is opened to the position shown by the two-dot chain line 5B in FIG. 2, each gear forming the speed increasing gear train 38 changes its position as shown in FIG. 6. Note that the angles of the arms are different between the arm position shown by the two-dot chain line in FIG. 2 and the arm position shown in FIG. 6 for convenience of illustration.

No. 6 gear 40 rotates as the door opens.
The full circumferential tooth portion 40a is the first tooth portion 4 of the No. 7 gear 41.
1a and rotates it in the direction of the solid line arrow. As shown in FIG. 6, the No. 7 gear 41
When the tooth portion 41a and the full circumferential tooth portion 40a of the No. 6 tooth portion 40 are rotated to a position where they are disengaged,
That is, when the No. 7 gear 41 rotates approximately 450 degrees, the No. 8 gear 42 rotated by the second tooth portion 41b
As shown in FIG.
It is rotated to a position opposite to the number gear 41,
The second tooth portion 41b and the small diameter tooth portion 42a of the No. 7 gear 41
It is disengaged from the mesh. In addition, so that the rotated protrusion 42e can face the circumference toothless part 41f of the No. 7 gear 41, a recess (not shown) into which the protrusion fits is formed in the circumference toothless part 41f. There is.

As shown in FIG. 6, even after the full circumferential tooth portion 40a of the No. 6 gear 40 and the first tooth portion 41a of the No. 7 gear 41 are disengaged, the No. 6 gear continues to move as indicated by the solid line as the door opens. being rotated in the direction The tooth portion 40c of the rotating No. 6 gear 40 (see FIG. 3) is
As shown in FIG. 7, the second tooth portion 4 of the No. 7 gear 41
1c, the gear 41 is rotated by two teeth by the tooth portion 41c. The intermittent feeding action by the tooth portion 40c of the No. 6 gear 40 is repeated until the opening operation of the door 5 is completed, and as shown in FIG. 8, the No. 7 gear 41 is moved in the direction of the solid line arrow.
Since the No. 7 gear 41, which is intermittently fed, has its entire circumferential missing tooth portion 41f facing the circular arc portion 42d of the No. 8 gear 42, the No. 8 gear and the No. 9 gear 43 do not rotate. Therefore, after the seventh gear 41 and the eighth gear 42 are disengaged, the operation of winding and tightening the coil spring 50 is released, and the door opening operation becomes easier.

Returning to FIG. 2, when the door 5, which has been opened to the position shown by the two-dot chain line 5B, is further rotated to the position shown by the one-dot chain line 5A, the first arm 2 and the second arm 3 gradually become larger. As the mainspring 19 assumes an angle, the mainspring 19 is further wound up by the gear train 26 and stored. When the door 5 is opened to a position 120 degrees from the maximum opening position, for example, the closed position, the positioning cam 51 pushes the positioning lever 57 as shown in FIG.
The cam follower 60 is engaged with the recess 51a. The cam follower 60 has a coil spring 5
The cam 51 is fitted into the recess 51a by the elasticity of the cam 51.
Regulates the rotation of. Therefore, the door 5 will be positioned at the set opening position. This positioning position can be released by forcibly rotating the door in the closing direction to disengage the positioning cam 51 and the cam follower 60.

When the above-mentioned positioning is released, or when the pushing force or pulling force on the door that has been opened to the position before the door position is released, that is, when the hand is released from the door, the door returns to the closed position shown by the solid line 5 in FIG. Start turning towards it. When the door 5 is opened, for example, to the position indicated by the two-dot chain line 5A in FIG. 2, the mainspring 19 is wound up and stored as shown in FIG. 9b. The stored force of the mainspring 19 drives the gear train 26 to rotate in the direction shown by the dashed arrow in FIG.

That is, the rotation of the fourth gear 23 rotated by the mainspring 19 is decelerated via the third gear 25, and in other words, is transmitted to the second gear 24 with a large torque. The second gear 24 rotates the first gear 16 in the direction of the dashed arrow with its small diameter tooth portion 24a. Since the number 1 gear 16 is substantially integral with the door 5, the door 5 begins to rotate from the open position towards the closed position due to the release force of the mainspring 19. When the No. 4 gear 23 rotates in the direction of the dashed arrow, the No. 5 gear 39 meshing with it rotates as follows.
As shown in FIG. 8, the No. 6 gear 40 is rotated in the direction of the dashed arrow. At this time, the first gear of No. 7 gear 41
Since the tooth portion 41a has its first missing tooth portion 41c facing the full circumference tooth portion 40a of the No. 6 gear 40, it is not rotated by the full circumference tooth portion 40a of the rotating No. 6 gear 40. However, as shown in FIG.
As shown in FIG. 7, the seventh gear 41 is rotated by two teeth in the direction of the dashed arrow with one rotation of the sixth gear 40.

The intermittent feeding action by the tooth portion 40c of the No. 6 gear 40 continues until the position just before the full-periphery tooth portion 40a of the gear engages with the first tooth portion 41a of the No. 7 gear (see FIG. 6). While this intermittent transmission continues, the one-way clutch means and braking means are not rotated, so that when attempting to manually close the door, only a small pushing force is required. In other words, the door can be closed easily.

In FIG. 6, when the No. 6 gear 40 rotates in the direction of the dashed arrow and its tooth portion 40c advances the No. 7 gear 41 by two teeth, the full circumferential tooth portion 40 of the No. 6 gear and the first tooth portion of the No. 7 gear The teeth 41a come to mesh with each other, and after this, the No. 7 gear is continuously rotated. This continuous rotation starting position is the position shown by the two-dot chain line in FIG. When the No. 7 gear 41 starts to rotate continuously, its second tooth portion 41b meshes with the small diameter tooth portion 42a of the No. 8 gear 42, causing the gear 42 to rotate in the direction of the dashed arrow. When the No. 8 gear 42 rotates, the No. 9 gear 43 (see FIG. 5) that meshes with it rotates in the direction of the dashed arrow. The rotation of the No. 9 gear 43 attempts to rotate the coil spring 50 in the direction opposite to the arrow a in FIG. It will be pressed against the surrounding surface.
Integration of the No. 9 gear 43 and the worm gear 44, so-called clutch engagement, is completed when the coil spring 50, which expands while rubbing against the inner circumferential surface of the worm gear, comes into pressure contact with the inner circumferential surface. 43,
There is no shock in the integration of 44.
Then, as the clutch is engaged, the worm gear 44 moves as shown in FIGS. 5 and 6.
It is rotated in the direction of the dashed arrow.

The worm gear 44 is a transmission means 3 consisting of a speed increasing gear train extending from the fifth gear 39 to the worm gear 44.
8, this rotation is further accelerated and transmitted to the worm shaft 31 via the worm 30. When the worm shaft 31 is rotated at high speed, the friction plates 32, 32 supported by the worm shaft 31 are rotated at high speed. When the friction plate 32 rotates at high speed, its arm portion 32a (see FIG. 3)
is elastically deformed and expanded by centrifugal force, and the braking cup 3
The rotation of the worm shaft 31 is braked by rubbing the inner circumferential surface of the worm shaft 31 to reduce its speed. When the speed of the worm shaft decreases and the arm portion 32a of the friction plate moves away from the inner peripheral surface of the cup, the rotation of the worm shaft 31 increases again, and the arm portion 32a begins to rub the inner peripheral surface of the cup. In this way, the friction plate 32 maintains the rotational speed of the worm shaft 31, which is rotating at low torque, within a certain range by repeatedly sliding in and out of contact with the inner circumferential surface of the braking cup 35. do.

The rotation of the gear train 26 that rotates when the door 5 is closed is transmitted to the braking means 29 via the one-way clutch means 36 and the transmission means 37 consisting of a speed increasing gear train, and from the time this braking means starts operating. , the rotation of each gear train is braked. That is, when the rotation of these gear trains is braked, the first gear 16 that is meshed with the second gear 24 at the starting end of the gear train 26 is braked.
In other words, the door 5, which is substantially integral with the No. 1 gear 16 and rotates in the closing direction, is braked. The braking for the door 5 can be applied, for example, from the open position shown by the one-dot chain line 5A in FIG. 2 to the two-dot chain line 5B.
Although there has never been a door that rotates to the position immediately before the predetermined opening/closing state shown by (the position where braking starts), once the door enters the predetermined opening/closing state shown by the two-dot chain line 5B, the door rotates until it closes. brake is applied to the door. The reason why the closing door 5 is braked is because, as described above, the rotation of the worm shaft 31 is braked by the friction plate. When rotating, the friction plate 32 has not yet rubbed against the inner peripheral surface of the cap 35.
The worm shaft 31 starts rotating without any shock. Therefore, the rotational speed of the door changes smoothly when the door starts to receive braking from a state where no braking has been applied.

The door 5, which has been rotated to the closed position shown by the solid line in FIG. 2, is in a stopped state with each means and each gear train stored in the first arm 2 positioned as shown in FIG. placed in

In the illustrated embodiment, the braking means 29 includes a friction plate 32 made of an elastic body and a braking cup 3.
However, as the braking means of the present invention, a well-known governor mechanism such as a type using a "wind cutter" fixed to a worm shaft may be applied. The combination of the friction plate 32 made of an elastic material such as rubber or rubber-like material and the brake cup has a unique effect, which will be explained below. Generally, when the temperature of the elastic body is high, its hardness decreases and it becomes easy to be elastically deformed. On the other hand, lubricating oil is applied between the individual gears that make up each gear train and their support shafts, and when the temperature is high, the viscosity of this lubricating oil decreases, reducing its flow resistance. . Conversely, when the temperature is low, the friction plate becomes difficult to deform, the viscosity of the lubricating oil increases, and the flow resistance increases. Such temperature characteristics of the lubricating oil and the friction plate are fully exhibited in places where there is a large difference in temperature between summer and winter. In the summer, the viscosity of the lubricating oil decreases, so each gear train rotates with low resistance, so the door that rotates in the closing direction tries to rotate relatively quickly. However, since the friction plate made of an elastic body has a lower hardness and becomes more easily deformed, it quickly expands and deforms and rubs against the brake cup. Then, in the winter, the phenomenon appears as the opposite of that in the summer. Therefore, the rotational speed of the door that closes under braking remains approximately constant regardless of the temperature.
There is no need to adjust the closing speed according to the temperature.

Now, the procedure for attaching the door closer 1 to a door that swings to the left as opposed to a door that swings to the right as shown in FIG. 2 will be described. When installed on a left-hand opening door, the door closer 1 assembled for right-hand opening as shown in FIG.
5 and attach it to the first arm 2 and second arm 3.
It is broken down into. Then, as in the illustrated example, when the door positioning mechanism is installed, the door positioning cam 51 is removed once and re-fixed for a left-hand opening door in accordance with the desired door position holding angle. put. Then, turn the top and bottom of the first arm 2 upside down, that is, as shown in FIG.
(b is not shown), and the door positioning means 53 is attached thereto as shown. In this case, the screw 55b is screwed into the female screw 2i, and the screw 55a is screwed into the female screw 2i.
It is screwed into k. When the door positioning means 53 has been installed, the arm shaft 4 fixed to the second arm 3 is inserted into the shaft hole 2m and the shaft hole 2l (not shown).
(See Fig. 3), and then the E-ring 15 is engaged with the shaft end. As a result, the first arm 2 is turned upside down and pivotally attached to the second arm 3, and a door closer reassembled for a left-hand opening door is obtained.

In the above description, the first arm incorporating the main mechanism is pivoted to the door, but it goes without saying that the first arm may be attached to the door frame and the second arm pivoted to the door.

(Effects of the Invention) As described above, according to the door closer of the present invention, the gear train, the driving force storage means, etc. are incorporated into the arm, and the arm incorporating these main parts is inverted and pivoted to the other arm. By simply putting it on, you can easily switch to the door closer depending on the direction in which the door opens. In this case, since the door closer is composed of a pair of arms, it is extremely easy to change the opening direction of the door and to attach the door closer.

[Brief explanation of the drawing]

Fig. 1 is a perspective view schematically showing the door closer of the present invention, Fig. 2 is a schematic plan view showing the different opening/closing states of the door and the corresponding positions of the door closer, and Fig. 3 is a door closer configured for a right-hand opening door. FIG. 4 is a vertical sectional view of the same as above, FIG. 5 is a plan sectional view of the same with the door in the closed position, and FIG. 7 and 8 are plan views showing the action of the intermittent transmission means, and FIG. 9 is a plan view illustrating the mainspring of the driving force storage means. , FIG. 10 is a plan view showing an example of a door positioning means, FIG. 11 is an operational view of FIG. 10 showing a state in which the door is positioned, and FIG. 12 is a perspective view of main parts showing a state in which the door is reassembled for a left-hand opening door. 13 are perspective views showing a conventional example of a door closer. 2...First arm, 3...Second arm, 5...
Door, 8...Door frame, 21...Driving force storage means,
26... Gear train, 29... Braking means, 36... Intermittent transmission means, 38... Speed increasing gear train, 4... Arm shaft.

Claims (1)

[Scope of Claims] 1. A first arm whose both ends are formed in a symmetrical shape and whose one end is pivotally connected to a door (or door frame); a second arm that is attached to the first arm; a pivoting means that selectively pivots the other end of the front or back surface of the first arm to the other end of the second arm; a driving force accumulating means for accumulating a driving force in the closing direction of the door as the door rotates in the opening direction; and a driving force accumulating means stored in the first arm along its longitudinal direction. , a gear train configured to transmit the rotation of the door when the door is opened to the driving force accumulating means and transmitting the driving force accumulated in the driving force accumulating means to the door; and a gear train stored in the first arm; a braking means that is rotated by the releasing force of the driving force accumulating means and applies a brake to the releasing force; a speed-increasing gear train disposed between the driving force accumulating means and transmitting the releasing force of the driving force accumulating means to the braking means; A door closer that can be applied to left-hand doors and right-hand doors by being pivotally mounted.