JPH09317315A - Door closer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the buffering property of a door and dispense with an oil-sealing treatment, by generating a braking force by making use of induction currents when the door is closed. SOLUTION: The first pinion 3 and the second pinion 5 mesh with a rack 9 when a door is in a closed state and only the first pinion meshes with the rack and the second pinion does not mesh therewith, when the door is in an opened state. A brake cap 41 is fixed to the brake shaft 34 and the skirt 41a is made of a nonmagnetic conductive material. The first cylindrical magnet holder 42 is arranged at the outside thereof and the second magnet holder 44 is arranged in the inside thereof. Further, an outside magnet 43 and an inside magnet 45 made of permanent magnets are arranged in these first and second magnet holders 42, 44. Magnetic lines of force flow between the outside and inside magnets 43, 45, in this arrangement of magnetic poles and induction currents flow in the direction crossing at right angles against the traveling direction of the skirt 41a and eddy currents occur. The eddy currents act to prevent the movement of the skirt 41a cutting the magnetic flux.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a novel door closer which does not use hydraulic oil.

[0002]

2. Description of the Related Art An example of a conventional door closer often used is disclosed in Japanese Utility Model Laid-Open No. 2-85780.

This closer is designed to dampen an excessive closing force due to a return spring and inertia when the door is closed, by a hydraulic oil, a cylinder filled with the hydraulic oil, a first chamber in front of the cylinder and a rear chamber. Provided on the piston, a piston for partitioning the second chamber into a second chamber, an oil guide passage that connects the first chamber and the second chamber through an orifice, a return spring that biases the piston toward the first chamber, It consists of a rack, a pinion that meshes with the rack, and a rotating shaft that is supported by the cylinder and to which the pinion and the arm are fixed.

[0004]

However, in the above-mentioned conventional closer, since the closing movement of the closer is buffered by utilizing the viscous resistance when the hydraulic oil passes through the orifice, The sealing process (sealing process) around the cylinder is troublesome and costly.
There was a problem such as oil leakage during long-term use.

Further, since the viscous resistance of hydraulic oil changes with temperature, it is necessary to adjust the shock absorbing condition depending on the season, which is troublesome for maintenance management.

Furthermore, since the viscous resistance of the hydraulic fluid buffers the closing movement of the closer from the start of the door closing to the full closing, it takes a long time to close the door, and therefore a quick door closing is desired. For him, there remains dissatisfaction with the fact that closing the door is redundant.

Therefore, in order to solve the above-mentioned problems, the door closer of the present invention is a non-oil type which does not use hydraulic oil, and the closing action force of the return spring is attenuated in the initial stage of door closing. Instead, it was proposed for the purpose of damping the closing action force of the return spring only in the latter stage of closing the door.

[0008]

In order to achieve the above object, the invention according to claim 1 is a hollow frame body attached to a door or a door frame, and is guided so as to be movable in the longitudinal direction in the frame body. Slider, a return spring for urging the slider toward the normal position, a first pinion that meshes with a rack formed on the side surface of the slider, and a rotatably supported frame body that is coaxial with the first pinion. When the door is open, it is separated from the main rotating shaft, which is connected to the main arm and the linking arm is attached to the part protruding outside the frame,
A second pinion disposed at a position where it meshes with the rack on the way to the closed state of the door, and is coaxially coupled to the second pinion and rotatably supported by the frame body, and through a one-way clutch. It has a sub-rotary shaft connected to the gear speed increasing mechanism and a brake mechanism connected to the output side of the gear speed increasing mechanism.

Further, the invention according to claim 2 is, as a brake mechanism, a brake cup made of a non-magnetic conductor mounted on the brake shaft on the output side of the gear speed increasing mechanism,
It is characterized in that an eddy current damper having a magnet arranged in proximity to the inner and outer surfaces of the skirt of the brake cup is sandwiched.

Furthermore, the invention according to claim 3 is, as a brake mechanism, a brake cup mounted on the brake shaft on the output side of the gear speed increasing mechanism, and a brake band wound around the outer peripheral surface of the brake cup. It is characterized by adopting a friction brake having and.

According to a fourth aspect of the present invention, as a brake mechanism, a guide rod connected to an output side brake shaft of the gear speed increasing mechanism at a right angle thereto, and slidably guided by the guide rod. In addition, an inertia governor having a weight and a return spring for urging the weight toward the base end side of the guide rod is adopted.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to an embodiment shown in the drawings. 1 and 2 show a door closer according to an embodiment of the invention described in claim 2, and in these drawings, reference numeral 1 is a frame body having a slender square cross-section which is attached to a door 10 or a door frame with a screw or the like. , 11 are cover plates mounted so as to cover the opening of the frame body 1.

A slider 7 is arranged in the frame body 1. The slider 7 is fitted with a cylindrical slider receiver 12 fixedly provided in the frame body 1, and is guided so as to be movable in the longitudinal direction of the frame body 1, that is, left and right in FIG.

The slider 7 is, for example, in the shape of a cylinder with a bottom, and a rack 9 is mounted on the outer peripheral surface thereof along the bus bar thereof.
The rack 9 projects to the outside of the slider receiver 12 through a slit formed in the slider receiver 12 along the generatrix thereof.

A return spring 8 is elastically mounted between the bottom surface of the inner cylindrical portion of the slider 7 and the spring receiver 13 that covers the opening of the slider receiver 12, and urges the slider 7 to the left in the figure. are doing.

On the other hand, a vertical main rotating shaft 2 having both ends or one end protruding outward is rotatably supported at the central portion of the frame 1, and the main rotating shaft 2 has the above-mentioned rack. The first pinion 3 meshing with the gear 9 is fixed.

One of the linkage arms (not shown) is fixed to one outer end of the main rotary shaft 2, and the other end of the linkage arm (not shown) is connected to the other linkage arm like the conventional door closer. It is connected to a fixed part such as a door frame.

Further, a sub-rotating shaft 4 parallel to the main rotating shaft is rotatably supported by the frame 1 at a position separated from the main rotating shaft 2 in the urging direction of the slider 7.

A one-way clutch 6 is arranged on the sub-rotating shaft 4, and the drive-side shaft 4a and the driven-side shaft 4 of the sub-rotating shaft 4 are arranged.
It has a structure for engaging and disengaging b with the former in the rotating direction.

A second pinion 5 that meshes with the rack 9 is mounted on the drive side shaft 4a, and a first bevel gear 21 is fixed on the driven side shaft 4b.

The one-way clutch 6 is a drive side shaft which is driven through the rack 9 and the second pinion 5 when the door 10 is opened (for example, when the main rotary shaft 2 rotates counterclockwise in FIG. 1). The rotation of 4a operates so as not to be transmitted to the driven shaft 4b.

On the contrary, when the door is closed, the one-way clutch 6 transmits the rotation of the drive side shaft 4a to the driven side shaft 4b. As such a one-way clutch, various ones can be adopted, for example, one including a ratchet pawl and a ratchet wheel, or one in which a roller is fitted in an inclined hole.

Therefore, the first pinion 3 mounted on the main rotary shaft 2 and the second pinion 3 mounted on the drive side shaft 4a of the sub rotary shaft 4
The relative position of the pinion 5 and the rack 9 in the longitudinal direction is set as follows.

That is, when the door 10 is in the closed state, the rack 9 is in the state shown by the solid line in FIG. 1, and at this time, as shown in FIG. 3, the first pinion 3 and the second pinion 3 are provided.
The pinion 5 meshes with the rack 9.

On the other hand, when the door is in the open state, the rack is in the state shown by the chain line in FIG. 1, and at this time, as shown in FIG. 4, only the first pinion 3 meshes with the rack 9 and The 2 pinion 5 should not engage with the rack 9.

Therefore, as shown in FIG. 5, the second pinion 5 also meshes with the rack 9 in the process of reaching the closed state by the elastic force of the return spring 8 from the open state of the door.

With the above structure, the door closed by the elastic force of the return spring 8 receives no resistance force until the second pinion 5 engages with the rack 9, and moves rapidly in the closing direction, so that the second pinion is closed. Only when the gears 5 mesh with each other, the brake force, which will be described later, is received and the closed state is slowly reached.

Next, the brake mechanism will be described. As described above, the first bevel gear 21 is mounted on the driven shaft 4b on the driven side of the one-way clutch 6.

A second bevel gear 22 is mounted on one end of a first support shaft 31 supported by the bracket 14 (see FIG. 2) and meshes with the first bevel gear 21.

A first large gear 23 is attached to the other end of the first support shaft 31 and meshes with a first small gear 24 attached to one end of a second support shaft 32 supported by the bracket 14.

The second large gear 25 attached to the other end of the second support shaft 32 meshes with the second small gear 26 attached to one end of the third support shaft 33 supported by the bracket 14.

The third large gear 27 mounted on the other end of the third support shaft 33 meshes with the bracket 14 and the third small gear 28 of the brake shaft 34 supported on one end of the frame.

The above structure forms a speed increasing mechanism, and the driven side shaft 4
For the rotation of b, the brake shaft 34 is moved through the three-stage gear speed increasing mechanism.
To rotate at high speed.

A brake cup 41 is fixedly mounted on the brake shaft 34, and at least the skirt portion 41a of the brake cup is made of a non-magnetic conductor.

On the other hand, the skirt portion 4 of the brake cup 41
A cylindrical first magnet holder 42 is provided on the outer side of the inner and outer surfaces of 1a (see FIGS. 1 and 6) so as to be close to the inner and outer surfaces thereof.
A cylindrical second magnet holder 44 is also arranged inside.

As shown in FIG. 6, the second magnet holder 44 on the inner side is made of a permanent magnet so that the apex portion in FIG. 6 is the N pole and the different poles are alternately adjacent to each other in the circumferential direction. Individual inner magnets 45, 45 are arranged, and the second magnet holder 44 is fixed to the frame body 1.

On the other hand, on the outer first magnet holder 42,
Similarly, as shown in FIG. 6, six outer magnets 43, 43 each of which is a permanent magnet are arranged so that the apex portion in FIG. 6 serves as an S pole and the different poles are alternately adjacent to each other in the circumferential direction. ing.

In FIG. 6, the magnets 43 and 45 are assumed to be magnetized in the radial direction of the brake cup 41, and the S and N magnetic poles thereof represent the magnetic poles facing the skirt portion 41a. To do.

A sector gear 42a is formed on a part of the outer circumference of the first magnet holder 42. The sector gear 42a is attached to a fourth support shaft 46 rotatably supported at one end of the frame 1. It meshes with the fixed third pinion 47.

Therefore, one end of the fourth support shaft 46 protruding from the frame 1 is rotated by a tool such as a screwdriver to rotate the third pinion 47, whereby the first magnet holder 42 and the second magnet holder 44 are rotated. The relative position in the circumferential direction can be changed.

In the arrangement of magnetic poles shown in FIG. 6, magnetic force lines flow between the outer magnet 43 and the inner magnet 45, and these magnetic force lines are orthogonal to the running direction of the skirt portion 41a. Therefore, an induced current flows through the skirt, and a so-called eddy current is generated.

This eddy current causes the skirt portion 4 to cut the magnetic flux.
Since the brake cup 41 acts to prevent the movement of 1a, the brake cup 41 receives a braking force.

As a result, the door moves from the open state to the closed state, and the second pinion 5 meshes with the rack 9 as shown in FIG. Is done.

The magnetic pole arrangement shown in FIG.
Since the pole or S pole is completely opposed to the S or N pole of the inner magnet 45, the flowing lines of magnetic force are at a maximum.
In other words, the magnetic flux density passing through the skirt portion 41a is maximum.

When the fourth support shaft 46 is rotated to rotate the first magnet holder 42 clockwise as shown in FIG. 7,
A part of the outer magnet 43 and the inner magnet 45 face each other with the same poles, and the magnetic force lines do not flow in this part, so that the number of the magnetic force lines as a whole decreases.

As a result, the induced current generated by the traveling of the skirt portion 41a is also reduced as compared with the state shown in FIG. 6, and the braking force is reduced. That is, the rotation of the shaft 46 acts as an adjustment of the braking force.

FIG. 8 shows the brake mechanism in the invention described in claim 3, and the mechanism up to the rotation of the brake shaft 34 is the same as that in the invention described in claim 1 described above. The description is omitted.

A brake cup 41 is fixed to the brake shaft 34. In this case, the skirt portion 41a of the brake cup does not have to be a conductor, and any material having wear resistance may be used. For example, cast iron, which is widely used as a material for a band brake drum, is suitable.

A brake band 51 is wound around the outer side of the skirt so as to come into contact with the skirt, one end of the brake band 51 is fixed to one end of the frame body 1, and the other end is a spring 5.
It is attached to the adjusting screw 53 at one end of the frame body via 2.

In this embodiment, the tension applied to the brake band 51 can be adjusted by tightening the adjusting screw 53, and the brake shaft 34 is braked by the frictional force between the skirt portion 41a and the brake band 51. Takes.

FIG. 9 shows the brake mechanism in the invention described in claim 4, and the mechanism from the slider 7 to the rotation of the brake shaft 34 is also the same as the invention described in claim 1 described above. Further detailed description is omitted.

In FIG. 9, a guide rod 61 is connected to one end of the brake shaft 34 so as to be perpendicular thereto.
A cylindrical weight 63 is slidably attached to the guide rod 61 along the guide rod 61.

Further, a return spring 64 is elastically mounted between the weight 63 and the head portion 62 of the guide rod.
The weight 63 urges the weight 63 in the direction toward the base end of the guide rod 61.

In this case, when the brake shaft 34 rotates at a high speed, the weight 63 moves toward the head 62 side along the guide rod against the elastic force of the return spring 64 by the centrifugal force.

As a result, the moment of inertia increases, and the increase in the moment of inertia is caused by the main rotary shaft 2 and the brake shaft 34.
Since the speed ratio of and is applied to the main rotating shaft as a square, the rotation of the main rotating shaft 2 is damped due to the increase of the moment of inertia of the rotating system.

In other words, the elastic energy released when the return spring 8 extends is absorbed in the form of being converted into the kinetic energy of the weight 63, and the rotation speed of the main rotating shaft 2 decreases.

In the illustrated embodiment, the brake mechanism utilizing the cushioning effect by the eddy current, the friction brake mechanism and the so-called inertia governor have been exemplified, but the door closer according to the present invention is not limited to the brake mechanism of another type. Of course, it can be adopted.

[0058]

According to the door closer of the present invention described above, for example, for damping the rotational movement, the braking force is generated by utilizing the induced current generated when the electric conductor cuts the magnetic force line, and the closing movement of the door is buffered. Since it is a product, it does not require oil sealing treatment in its production, and not only the cost can be reduced but also there is no fear of oil leakage during use.

According to the door closer of the present invention,
In the early stage of the door closing movement, the door is not cushioned, and the door cushioning is performed only in the later stage of the door closing movement, which requires the door cushion most. The effect of being able to shorten is produced.

According to the third aspect of the invention, since the band brake is used for the brake mechanism, the structure is very simple.

Furthermore, according to the invention described in claim 4,
Since the moment of inertia of the weight is used to buffer the closing movement of the door, there is no wear of the parts and it is possible to endure long-term use.

[Brief description of drawings]

FIG. 1 is a vertical plan view showing an embodiment of a door closer of the present invention.

FIG. 2 is a side view showing the cover plate removed.

FIG. 3 is an explanatory diagram of a relational position between a pinion and a rack, showing a door closed.

FIG. 4 is an explanatory view of a relational position between a pinion and a rack, showing a door opened.

FIG. 5 is an explanatory diagram of a relational position between a pinion and a rack, showing a door being closed.

FIG. 6 is a front view of the brake mechanism according to the second aspect of the invention.

FIG. 7 is a front view of the brake mechanism according to the second aspect of the invention when the brake is adjusted.

FIG. 8 is a front view of the brake mechanism according to the third aspect of the invention.

FIG. 9 is a front view of a brake mechanism according to a fourth aspect of the invention.

[Explanation of symbols]

 1 Frame 2 Main Rotating Shaft 3 First Pinion 4 Sub Rotating Shaft 4a Drive Side Shaft 4b Driven Side Shaft 5 Second Pinion 6 One-way Clutch 7 Slider 8 Return Spring 9 Rack 10 Door 11 Cover Plate 12 Slider Bearing 34 Brake Shaft 41 Brake cup 41a Skirt portion 42 First magnet holder 42a Sector gear 43 Outer magnet 44 Second magnet holder 45 Inner magnet 46 Fourth shaft 47 Third pinion 51 Brake band 53 Adjustment screw 61 Guide rod 62 Head 63 Weights 64 Return spring

Claims (4)

[Claims] 1. A hollow frame body attached to a door or a door frame, a slider movably guided in a longitudinal direction in the frame body, a return spring for urging the slider toward a normal position, and a slider. A first pinion that engages with a rack formed on a side surface, a main rotation shaft that is rotatably supported by the frame body, is coaxially coupled to the first pinion, and has a linking arm attached to a portion protruding outside the frame body. When the door is in the open state, it is separated from the rack, and the second pinion is provided coaxially with the second pinion and is disposed at a position where the door engages with the rack on the way to the closed state. A door claw rotatably supported by the body and having a sub-rotary shaft connected to a gear speed increasing mechanism via a one-way clutch and a brake mechanism connected to an output side of the gear speed increasing mechanism. The. 2. The brake mechanism comprises a brake cup made of a non-magnetic conductor mounted on a brake shaft on the output side of a gear speed increasing mechanism, and a skirt portion of the brake cup sandwiched between the inner and outer surfaces thereof. The door closer according to claim 1, further comprising a magnet disposed in proximity to the magnet. 3. The brake mechanism has a brake cup mounted on a brake shaft on the output side of the gear speed increasing mechanism, and a brake band wound around the outer peripheral surface of the brake cup. The door closer according to Item 1. 4. A guide rod, wherein the brake mechanism is connected to a brake shaft on the output side of a gear speed increasing mechanism so as to be perpendicular to the brake shaft, a weight slidably guided by the guide rod, and The door closer according to claim 1, further comprising a return spring that urges the weight toward the base end side of the guide rod.