JP2006189151A - Damper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a damper capable of providing large braking force for travel of a movable body irrespective of its small size. <P>SOLUTION: A rod 3 is inserted into a tube 2 so as to slide freely in the axial direction and is provided with a braking body 5 having a smooth surface and made of a flexible and elastic material in a condition in which a brake face 5a formed into a tapered shape in which a tip becomes narrower comes into contact with an inner face of the tube. The braking body 5 is elastically deformed in the direction in which it comes into pressure-contact with the inner face of the tube by contact pressure of the brake face 5a and the inner face of the tube for traveling force applied on the rod 3 to provide braking force. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a damper that exerts a braking force against a moving force of a movable body such as a sliding door of a building or furniture, a rotary door, a lift shelf or the like.

  For various movable devices that move sliding doors (including hanging doors), rotary doors, drawers, cabinets, elevating shelves (hereinafter referred to as movable bodies) of joinery or furniture, against the moving force of the movable body A device provided with a damper that applies a braking force and suppresses a rapid movement is known (see Patent Document 1).

Conventionally, as this type of damper, a cylinder structure is known in which a rod with a piston is inserted into a tube and a braking force is applied to a movable body using spring force, air pressure, or hydraulic pressure.
Japanese Utility Model Publication No. 57-77570

  However, according to a conventional damper that acts as a resistance by spring force or fluid pressure, a certain volume or more is required, so that the damper size tends to increase with respect to the obtained braking force.

  In particular, when used for a heavy-weight movable body (for example, a sliding door with several tens of kilograms), the damper is enlarged in both diameter and length, requiring a large space for installation, making installation complicated, and costly. There was a difficulty that it was expensive.

  On the other hand, the maximum value of the braking force is constant regardless of the magnitude of the load, so when a large movable body is operated suddenly with a strong force, the braking force is insufficient, and the movable body does not stop. There is a problem that the reliability of the damper function is inferior.

  Therefore, the present invention provides a damper capable of obtaining a large braking force against movement of a movable body while being small.

  The present invention also provides a damper in which the braking force changes according to the load and exhibits a sufficient braking force even with a large load.

  According to the first aspect of the present invention, a rod is slidably inserted into the tube in the axial direction, and a brake body made of an elastic material having a smooth surface is inserted into the rod in a state where the outer periphery is in contact with the inner surface of the tube. The brake body is configured so as to exert a braking force by elastically deforming in a direction in which the moving force applied to the rod is pressed against the inner surface of the tube by a contact pressure with the inner surface of the tube.

  According to a second aspect of the present invention, in the configuration of the first aspect, the brake body is provided with a tapered brake surface that tapers in one direction, and the brake surface is applied in one direction applied to the rod. The moving force is elastically deformed to a degree corresponding to the magnitude of the moving force to exert a braking force, and the moving force in the opposite direction is restored to release the braking force.

  According to a third aspect of the present invention, in the configuration of the second aspect, a concave groove is provided on the outer peripheral surface of the rod over the entire circumference, while the ring-shaped brake body is tapered so that the outer peripheral surface is directed in one direction. The taper is fitted in the concave groove.

  According to a fourth aspect of the present invention, in the configuration of the third aspect, a ring-shaped brake body in which a plurality of concave grooves having different depths are provided continuously in the axial direction on the outer peripheral surface of the rod, and the outer peripheral surface is flat. Are fitted across the plurality of concave grooves in a state in which the flat outer peripheral surface is tapered toward one direction.

  According to a fifth aspect of the present invention, in the configuration of the fourth aspect, the inner diameter dimension of the brake body is made different between the two halves in the axial direction, and a plurality of the brake bodies are fitted in a state where the portion having the smaller inner diameter is fitted into the deepest concave groove. It is fitted over the concave groove.

  According to a sixth aspect of the present invention, in the configuration of the third aspect, a plurality of concave grooves having different depths are continuously provided in the axial direction on the outer peripheral surface of the rod, and on the outer peripheral surface of the ring-shaped brake body. A brake surface tapered toward one direction is formed, and the inner diameter of the brake body is changed stepwise in the axial direction corresponding to the plurality of concave grooves. It is fitted across the plurality of concave grooves.

  According to a seventh aspect of the present invention, in the configuration of the third aspect, the inner diameter dimension of the ring-shaped brake body is made different in both axial halves, and the brake body is advanced in one direction by contact pressure with the tube inner surface. It is fitted into the concave groove in a state where the brake surface is formed by being deformed into a tapered tapered shape.

  According to an eighth aspect of the present invention, in the configuration of the second aspect, a shaft-like brake body is attached to the tip of the rod, and a tapered brake surface that is tapered toward one direction on the outer peripheral surface of the brake body. Is formed.

  According to a ninth aspect of the present invention, in the configuration of the eighth aspect, one end side of the brake body is hollow, and a brake surface is formed on an outer periphery of the one end side.

  According to a tenth aspect of the present invention, in the structure according to any one of the second to ninth aspects, a push spring that urges the rod in a brake releasing direction is provided in the tube.

  An eleventh aspect of the present invention is the structure according to any one of the second to tenth aspects, further comprising an air intake / exhaust mechanism that restricts the amount of air discharged from the tube and exerts a braking force.

  According to a twelfth aspect of the present invention, in the configuration according to any one of the first to eleventh aspects, a section in which the braking force is relatively increased and a section in which the braking force is relatively decreased are obtained by making the inner diameter dimension of the tube different in a plurality of sections in the axial direction. Formed.

  According to the present invention, the brake body is elastically deformed by the contact pressure with the inner surface of the tube and brought into pressure contact with the inner surface of the tube, and the brake force is exerted by this pressure contact force (friction force). A large volume like a pneumatic type becomes unnecessary.

  Therefore, the damper can be reduced in size and length, and the structure is simple and inexpensive.

  According to the second to eleventh aspects of the present invention, the brake body is formed of an elastic material having a smooth surface and a soft surface, and the brake surface is tapered so as to be tapered in one direction. As a result, for a moving force in one direction, the brake surface is elastically deformed so that the brake surface is turned up to exert the braking force, and in the opposite direction, the brake is restored and the brake is released.

  For this reason, in sliding or rotary doors and drawers, elevating shelves, etc., one-way damper characteristics, that is, a brake acts in the required direction and the resistance in the opposite direction can be easily achieved with a small resistance. The property of being able to be moved automatically (by a spring) can be obtained.

  In addition, as a characteristic of the brake body material and brake surface shape, the greater the moving force (the faster the moving speed), the larger the braking force, so it is particularly large when used as a damper that suppresses the sliding door opening speed. A favorable characteristic as a damper can be obtained, for example, a high braking force is exhibited when the heavy suspension door is suddenly opened with a strong force.

  In particular, when configured as a damper that also uses air pressure as in the invention of claim 11, when the movable body is rapidly pushed in with a strong force in the conventional air damper, it is pushed back by the air pressure on the moving end side. Bumping may occur, but the movable body is not pushed in rapidly, so bumping does not occur.

  The inventor has confirmed that oil-containing urethane, silicone-containing polyester, silicone resin, and the like are suitable as specific materials for the brake body for obtaining the above characteristics and ensuring wear resistance to withstand long-term use. .

  On the other hand, according to the invention of the twelfth aspect, since the inner diameter dimension of the tube is made different in a plurality of sections in the axial direction, a section in which the braking force is relatively increased and a section in which the brake force is decreased are formed. If you set it to a large brake section, a small brake section in the middle, and a large brake section at the end of closing, you can get a favorable damper function according to the application, such as slowly starting to close and accelerating and finally closing slowly be able to.

1st Embodiment (refer FIGS. 1-5)
The damper 1 according to the first embodiment includes a tube 2, a hollow rod 3 slidably inserted into the tube 2, and a tip portion of the rod 3 (an end portion on the side inserted into the tube 2). The piston 4 is provided, and a ring-shaped brake body 5 made of a material having a smooth surface, a soft surface, and a high elasticity is mounted on the outer periphery of the piston 4.

  As shown in FIGS. 3 to 5, the brake body 5 is formed in a groove 6 provided on the outer peripheral surface of the piston 4 over the entire circumference in a state in which the outer peripheral surface elastically contacts the inner surface of the tube 2. The frictional resistance between the brake body 5 and the inner surface of the tube is configured to act as a braking force.

  More specifically, the outer peripheral surface (brake surface) 5a of the brake body 5 is formed in a tapered shape inclined in a tapered manner toward one direction, and the direction in which the piston 5 is pulled out of the tube 2 (in FIG. 4). When the damper is actuated in the direction indicated by the double-lined arrow and in which the damper 1 extends), as shown in FIG. 4, only the edge on the inclined upper end side of the brake surface 5a moves in the tube 2 while contacting the tube inner surface. To do.

  At this time, from the characteristic that the surface of the brake body 5 is smooth, flexible and rich in elasticity, the contact pressure between the brake surface 5a and the inner surface of the tube, that is, the brake force is in a minimum state (hereinafter referred to as a brake released state).

  Hereinafter, this operation in the brake release direction is referred to as damper extension operation.

  On the other hand, when the damper is actuated in the direction in which the piston 4 is pushed into the tube 2 (the direction indicated by the double arrow in FIG. 5 and the damper 1 is contracted), it is flexible and elastic. As shown in FIG. 4, the brake surface 5a is elastically deformed so as to be turned up from the edge at the upper end of the slope and is pressed against the inner surface of the tube, and this pressure contact force acts as a brake force.

  In this case, the greater the moving force (the faster the moving speed), the higher the contact pressure and the greater the degree of elastic deformation of the brake surface 5a. For this reason, the contact pressure between the brake surface 5a and the tube inner surface also increases, and the braking force increases.

  That is, the characteristic that the braking force changes according to the load is obtained.

  Hereinafter, this operation in the braking action direction is referred to as damper reduction operation.

  In order to obtain such characteristics of the brake body 5, oil-impregnated urethane, silicon-containing polyester, silicon are examples of materials that have a smooth surface, are flexible, are elastic, and have high wear resistance so that they can withstand long-term use. The inventor has confirmed that a resin or the like is appropriate.

  Even when these materials are used, when the brake surface 5a is configured to contact the inner surface of the tube with a flat face instead of being tapered, the brake surface 5a is evenly expanded and contracted with respect to the inner surface of the tube. Since the contact as a single pressure is not possible, the function as a one-way damper cannot be obtained, and if a simple rubber is used as the material, even if the brake surface 5a is tapered, the stability is poor and it is still a one-way damper. It was confirmed at the same time that it was difficult to obtain the functions.

  The tube 2, rod 3, and piston 4 are not particularly limited in material, and various plastics (for example, Duracon) or metals such as aluminum can be used. However, the inner surface of the tube 2 that contacts the brake body 5 is preferably smooth.

  Further, oil reservoirs and O-rings for lubrication may be provided on both axial sides of the brake body 5 on the outer periphery of the piston 4.

  On the other hand, the damper 1 also has a configuration in which air pressure is used as a braking force, that is, a configuration as an air damper.

  That is, as shown in FIG. 3, a check valve 7 is provided at the head side end of the tube 2 as an air intake / exhaust mechanism, while an end cap 9 having an air passage 8 is provided at the rod side end of the tube 2. It has been.

  The check valve 7 includes an intake passage 10, a ball 11 that opens and closes the intake passage 10, and an exhaust passage 12. The intake passage 10 is closed by the ball 11 during damper reduction operation.

  As a result, the first air chamber 13 is pressurized and the second air chamber 14 is depressurized out of the first and second air chambers 13 and 14 defined by the piston 4 with the brake body 5.

  At this time, the air in the first air chamber 13 is exhausted to the outside while being constricted in the exhaust passage 12, and resistance is given to the exhaust air by this constricting action, and a braking force acts.

  In this case, in the conventional air damper, when the movable body is rapidly pushed in with a strong force, so-called bumping may occur in which the movable end is pushed back by air pressure. Since a large braking force acts on the load and the movable body can be prevented from being pushed in rapidly, bumping does not occur.

  On the other hand, air is sucked into the second air chamber 14 from the outside through the air passage 8.

  On the other hand, when the damper is extended, the first air chamber 13 is depressurized and the second air chamber 14 is pressurized, so that the intake passage 10 of the check valve 7 is opened and the first air chamber 13 is inhaled. The air in the second air chamber 14 is discharged outside through the air passage 8.

  The damper 1 having the above-described configuration is incorporated between a fixed portion and a movable body in various movable devices, and serves as a brake force and an air damper due to a pressure contact force between the brake body 5 and the inner surface of the tube when the damper is contracted. The braking force of

  Specific usage examples are shown in FIGS.

  FIG. 6 shows a case where the present invention is applied to a sliding door device. A damper 1 is attached to a sliding door 15 as a movable body, for example, with the tip of the rod 3 facing the left and right vertical frames 16 a of the door frame 16. When the damper 1 is opened, the damper 1 is contracted to act as a braking force.

  FIG. 7 shows a case where the present invention is applied to a rotary door device as a door closer. The damper 1 is attached between a door 17 as a movable body and a door frame 18. For example, when the door 17 is closed, the damper 1 is Brake force works by reducing operation.

  FIG. 8 shows a case where the present invention is applied to a storage device. A damper 1 is attached between a storage box 19 and a door 20 as a movable body that opens and closes the opening. For example, when the door 20 is closed, the damper 1 is Brake force works by reducing operation.

  FIG. 9 shows a case where the present invention is applied to a furniture drawer device. When the damper 1 is incorporated in the furniture body 21 and the drawer 22 is closed, the damper 1 is contracted to act as a braking force.

  FIG. 10 shows a case where the present invention is applied to a lifting and lowering shelf device. The damper 1 is incorporated in the main body frame 23, and when the lifting shelf 24 is lowered, the damper 1 is contracted to act as a braking force.

  By using the damper 1 for such various movable devices, the movable body is operated gently while applying a brake in one direction (the sliding door 15 in FIG. 6 is gently closed), and the opposite direction Can be smoothly operated (opened) with a small resistance.

  In addition, when the movable body is suddenly operated with a strong force, a large braking force is applied according to the force, so that the damper action is performed reliably, and the movable body collides with the fixed part or the reaction thereof. Can be prevented from bouncing off.

Second embodiment (see FIGS. 11 and 12)
In the following embodiments, only differences from the first embodiment will be described.

  In the damper 1 according to the second embodiment, two concave grooves 25 and 26 having different depths are continuously provided in the axial direction on the outer periphery of the piston 4, and the outer peripheral surface is not tapered (flat). By fitting the ring-shaped brake body 27 across the both concave grooves 25 and 26, the entire brake body 27 is configured to have a tapered shape in a mounted state. Reference numeral 27a denotes a brake surface.

  Also with this configuration, as in the case of the first embodiment, the brake surface 27a is elastically deformed so as to be turned up from the edge on the upper end of the tilt during the damper reduction operation, and is pressed against the inner surface of the tube, and the braking force is applied.

  Moreover, according to this structure, since the brake body 27 should just be formed in a ring shape, it is easy to process and is advantageous in terms of mass productivity.

3rd Embodiment (refer FIGS. 13-15)
In the damper 1 according to the third embodiment, the brake body 28 is formed by a sufficiently soft elastic material into a ring shape having different inner diameters in both axial halves, and as shown in FIG. 6 is fitted. Reference numeral 28a denotes a flat outer peripheral surface of the brake body 28, that is, a brake surface.

  According to this configuration, when the brake body 28 is incorporated into the tube 2 together with the rod 3 and the piston 4, the brake body 28 is pushed into the concave groove 6 by being pushed by the inner surface of the tube. At this time, as shown in FIG. 14, the thin and fragile half is pressed inward, so that the brake surface 28a is inclined in a tapered shape.

  Then, during the damper reduction operation, as in both the first and second embodiments, as shown in FIG. 15, it is elastically deformed so as to be turned up from the edge on the inclined upper end side of the brake surface 28a and pressed against the inner surface of the tube. , Brake force works.

Fourth embodiment (see FIGS. 16 and 17)
In the damper 1 according to the fourth embodiment, as in the second embodiment, two concave grooves 25 and 26 having different depths are continuously provided in the axial direction on the outer periphery of the piston 4 while being stepped in the axial direction. A ring-shaped brake body 29 having different inner diameter dimensions in both axial halves, such as the brake body 28 of the third embodiment being reversed in the front-rear direction, is formed across the concave grooves 25 and 26, And it is fitted in a state where almost no gap is generated in the axial direction.

  In addition, a brake surface 29a that slopes downward is provided on the outer peripheral surface of the brake body 29, and when the damper is contracted, the brake surface 29a is elastically deformed so as to be turned up from the edge and is pressed against the inner surface of the tube so that the braking force works. It is configured.

  According to this configuration, since the brake body 29 does not move in the axial direction when the damper is operated, a constant elastic deformation action is always performed, and a more stable brake action can be obtained.

5th Embodiment (refer FIGS. 18-20)
The damper 1 according to the fifth embodiment takes a form in which the second to fourth embodiments are combined.

  That is, three concave grooves 30, 31, and 32 having different depths are continuously provided in the axial direction on the outer periphery of the piston 4, while the outer peripheral surface 33a is flat and the inner diameter dimension is in both axial halves. A different ring-shaped brake body 33 is formed, and the brake body 33 is fitted over the concave grooves 30 to 32 in a state where the small inner diameter portion is fitted into the deepest concave groove 30, thereby implementing the second embodiment. Similar to the configuration, the entire brake body is configured to have a tapered shape in a mounted state.

  Even with this configuration, as in the other embodiments, the brake surface 33a is elastically deformed so as to be turned up from the edge at the upper end of the slope during the damper reduction operation, and presses against the inner surface of the tube to apply the braking force.

  Further, according to this configuration, as in the fourth embodiment, it is possible to obtain a stable braking action by stopping the axial movement of the brake body 33 when the damper is operated.

Sixth and seventh embodiments (see FIGS. 21 and 22)
In the first to fifth embodiments, the brake bodies 5, 27, 28, 29, 33 are formed in a ring shape, whereas in the damper 1 according to the sixth embodiment shown in FIG. In the damper 1 according to the seventh embodiment shown in FIG. 22, the brake body 35 is formed in a shaft shape in which the tip end is hollow, and the brake bodies 34 and 35 are fitted to the tip of the rod 3. It is fixed.

  Both brake bodies 34, 35 are formed with tapered brake surfaces 34a, 35a that taper in one direction on the outer peripheral surface on the front end side, and these brake surfaces 34a, 35a are tubed when the damper is contracted. It is configured to perform a braking action by being pressed against the inner surface.

  Both of these embodiments can basically obtain the same effects as those of the first to fifth embodiments.

Eighth embodiment (see FIG. 23)
In the damper 1 according to the eighth embodiment, a push spring (compression coil spring) 36 is provided in the tube 2 and the spring force of the push spring 36 acts in the damper extension direction (brake release direction), that is, the damper extension. It is configured to assist the movement of the movable body in the direction (for example, the opening operation of the door 17 in the door device of FIG. 7).

  In addition, although the damper configuration of the first embodiment is illustrated here as an example, this spring-loaded damper configuration can be applied to the damper configurations of the second to seventh embodiments.

  In the case of adopting this spring-loaded damper configuration, the brake body 5 is in a brake released state with respect to the damper extension operation, so that the assist action of the push spring 36 works effectively.

Ninth embodiment (see FIG. 24)
For example, in the door device shown in FIG. 7, it is preferable that the door 17 starts closing slowly, accelerates in the middle, and finishes slowly closing.

  In 9th Embodiment, the damper structure as a door closer which implement | achieves such a movement of the door 17 is taken.

  That is, by making the inner diameter dimension of the tube 2 different from small, large, and small in the three sections 2a, 2b, and 2c on the proximal side, the middle, and the distal side, both the proximal and distal sections 2a and 2c are made different. The large brake section and the intermediate section 2b in which the braking force is relatively increased are configured as the small brake section.

  In this way, the door 17 can be closed slowly / faster / slowly.

  As a means for increasing the inner diameter dimension of the tube 2 in the intermediate section 2b, for example, a female die whose tip is configured to be expanded by slitting is placed in the intermediate section 2b of the tube 2, and the tip of this female mold is inserted. A known press technique for expanding the same section 2b outward can be used by press-fitting the male mold into and expanding it. Alternatively, it is also possible to use a processing method in which the intermediate section 2b has a relatively large diameter by pressing both the proximal end section and the distal end section 2a, 2c with a roller from the outer periphery to reduce the diameter.

  Moreover, this damper structure can be employ | adopted for various uses other than the door closer of a door apparatus. Furthermore, the number of large brake sections and small brake sections and the arrangement in the axial direction can also be arbitrarily changed according to the application.

  Furthermore, although the drawing illustrates the damper configuration of the first embodiment as an example, the present invention can be similarly applied to the damper configurations of other embodiments.

  By the way, in each said embodiment, although comprised so that a braking force might work at the time of damper reduction operation | movement, you may comprise so that a braking force may work at the time of damper extension operation | movement conversely. In this case, the brake bodies 5, 27, 28, 29, 33, 34, 35 in each embodiment are in a state where the brake surfaces 5 a, 27 a, 28 a, 29 a, 33 a, 34 a, 35 a are tapered in the reverse direction. The rod 3 can be attached with.

It is a disassembled perspective view of the damper concerning a 1st embodiment of the present invention. It is a perspective view of the assembly state. FIG. FIG. 4 is a partially enlarged view of FIG. 3. FIG. 5 is a view corresponding to FIG. 4 in a state in which the damper is operated in the damper reduction direction from the state of FIG. 4. It is a front view which shows the state which used the damper for the sliding door apparatus. It is a horizontal sectional view showing the state where a damper is used for a door device. It is a perspective view which shows the state which used the damper for the storage apparatus. It is a perspective view which shows the state which used the damper for the drawer apparatus. It is a perspective view which shows the state which used the damper for the raising / lowering shelf apparatus. It is a partial expanded sectional view of the damper concerning a 2nd embodiment of the present invention. FIG. 12 is a view corresponding to FIG. 11 in a state where the damper is operated in the damper reduction direction from the state of FIG. 11. It is a partially expanded sectional view of the rod and brake body in the damper concerning 3rd Embodiment of this invention. It is a partially expanded sectional view of the assembly state of the damper. FIG. 15 is a view corresponding to FIG. 14 in a state where the damper is operated in the damper reduction direction from the state of FIG. 14. It is a partial cross section figure of the damper concerning a 4th embodiment of the present invention. FIG. 17 is a view corresponding to FIG. 16 in a state where the damper is operated in the damper reduction direction from the state of FIG. 16. It is a partial expanded sectional view of the rod and brake body in the damper concerning a 5th embodiment of the present invention. It is a partially expanded sectional view of the assembly state of the damper. FIG. 20 is a view corresponding to FIG. 19 in a state where the damper is operated in the damper reduction direction from the state of FIG. 19. It is a partial cross section figure of the damper concerning a 6th embodiment of the present invention. It is a partial cross section figure of the damper concerning a 7th embodiment of the present invention. It is sectional drawing of the damper concerning 8th Embodiment of this invention. It is sectional drawing of the damper concerning 9th Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Damper 2 Tube 3 Rod 4 Piston 5,27,28,29,33,34,35 Brake body 5a, 27a, 28a, 29a, 33a, 34a, 35a Tapered brake surface 6 Concave groove 7 Consists of air intake / exhaust mechanism Check valve 10 Intake passage 11 Ball 12 Exhaust passage 9 Air passage 25, 26 Two concave grooves with different depths 30, 31, 32 Three concave grooves with different depths 2a, 2c Base end side where braking force increases And tip side section 2b Middle section where brake force becomes small

Claims (12)

  A rod is slidably inserted into the tube in the axial direction, and a brake body made of an elastic material having a smooth surface and a smooth surface is provided on the rod in a state where the outer periphery is in contact with the inner surface of the tube. A damper configured to exert a braking force by elastically deforming in a direction in which it is pressed against the inner surface of the tube by a contact pressure with the inner surface of the tube against a moving force applied to the rod.   The damper according to claim 1, wherein the brake body is provided with a tapered brake surface tapered toward one direction, and the brake surface moves with respect to a one-way moving force applied to the rod. A damper configured to exhibit a braking force by elastically deforming at a degree corresponding to the magnitude of the force, and to restore the braking force by restoring the moving force in the opposite direction.   The damper according to claim 2, wherein a concave groove is provided on the outer peripheral surface of the rod over the entire periphery, and the ring-shaped brake body is in a state where the outer peripheral surface has a tapered shape that is tapered in one direction. A damper characterized by being fitted in the groove.   4. The damper according to claim 3, wherein a plurality of concave grooves having different depths are provided continuously in a stepwise manner in the axial direction on the outer peripheral surface of the rod, and a ring-shaped brake body having a flat outer peripheral surface is provided. A damper characterized in that a brake surface is formed by fitting across the plurality of concave grooves in a state where the surface is tapered in a tapered manner in one direction.   5. The damper according to claim 4, wherein the inner diameter dimension of the brake body is made different in both axial halves, and the brake body is fitted over the plurality of groove grooves in a state where the portion having the smaller inner diameter is fitted into the deepest groove groove. Damper characterized by wearing.   4. The damper according to claim 3, wherein a plurality of concave grooves having different depths are continuously provided in the axial direction on the outer peripheral surface of the rod in a stepwise manner, while the outer periphery of the ring-shaped brake body is advanced in one direction. A brake surface having a tapered taper is formed, and the inner diameter of the brake body is changed stepwise in the axial direction corresponding to the plurality of concave grooves, and the brake body is formed into the plurality of concave grooves. A damper characterized by being fitted across.   4. The damper according to claim 3, wherein the ring-shaped brake body has different inner diameters at both halves in the axial direction, and the brake body is tapered toward one direction by contact pressure with the inner surface of the tube. A damper characterized by being fitted into a concave groove in a state where a brake surface is formed by deformation.   3. The damper according to claim 2, wherein a shaft-like brake body is attached to the tip of the rod, and a tapered brake surface that is tapered toward one direction is formed on the outer peripheral surface of the brake body. A damper.   The damper according to claim 8, wherein one end side of the brake body is hollow, and a brake surface is formed on an outer periphery of the one end side.   The damper according to any one of claims 2 to 9, wherein a push spring that urges the rod in a brake releasing direction is provided in the tube.   The damper according to any one of claims 2 to 10, further comprising an air intake / exhaust mechanism that restricts the amount of air discharged from the tube and exerts a braking force.   The damper according to any one of claims 1 to 11, wherein a section in which the braking force is relatively increased and a section in which the braking force is relatively reduced are formed by making the inner diameter dimension of the tube different in a plurality of sections in the axial direction. Damper characterized by.

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