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WO2019188810A1 - Amortisseur - Google Patents

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Publication number
WO2019188810A1
WO2019188810A1 PCT/JP2019/012155 JP2019012155W WO2019188810A1 WO 2019188810 A1 WO2019188810 A1 WO 2019188810A1 JP 2019012155 W JP2019012155 W JP 2019012155W WO 2019188810 A1 WO2019188810 A1 WO 2019188810A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
damper
rod
cylinder
end side
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/012155
Other languages
English (en)
Japanese (ja)
Inventor
加藤　幸一
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Piolax Inc
Original Assignee
Piolax Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Piolax Inc filed Critical Piolax Inc
Priority to JP2020509976A priority Critical patent/JP6961801B2/ja
Publication of WO2019188810A1 publication Critical patent/WO2019188810A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F7/00—Vibration-dampers; Shock-absorbers
    • F16F7/08—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other
    • F16F7/09—Vibration-dampers; Shock-absorbers with friction surfaces rectilinearly movable along each other in dampers of the cylinder-and-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics

Definitions

  • the present invention relates to a damper used for braking such as opening / closing operation of an automobile glove box.
  • a damper may be used in order to prevent the lid from opening suddenly and open it gently.
  • Patent Document 1 discloses a cylinder, a rod inserted into the cylinder, a piston provided on the rod proximal end side and provided with an air flow passage, and a buffer fixed on the rod distal end side.
  • a damper is described having a member and a cap mounted on the proximal opening of the cylinder.
  • a spring is interposed inside the buffer member and is biased so that the buffer member protrudes from the opening at the tip of the cylinder.
  • a cylindrical wall having an elongated cylindrical shape is formed inside the cylinder, a rod is inserted into the cylindrical wall, and an annular gap is formed between the inner periphery of the cylindrical wall and the outer periphery of the rod.
  • a recess having a predetermined length is formed in a space in the inner periphery of the cylinder where the piston is disposed (see FIG. 4).
  • the buffer member When the buffer member is pushed and pulled into the opening at the tip of the cylinder, the buffer member protrudes from the cylinder tip opening by the biasing force of the spring when the pressing force to the buffer member is not applied. At this time, the buffer member is braked by the frictional force between the piston and the inner circumference of the cylinder, and the resistance when the air flows through the air gap of the piston between the inner circumference of the cylindrical wall and the outer circumference of the rod. Is done.
  • the air in the cylinder is It flows through the annular gap between the outer periphery of the rod, the air flow passage of the piston, and between the piston and the recess provided in the inner periphery of the cylinder, and is released from the cap opening to release the braking force, and the buffer member It is accommodated in the tip opening of the cylinder.
  • the damper of the above-mentioned Patent Document 1 reduces the return resistance by allowing air to flow through a recess formed in the inner periphery of the cylinder when the piston moves in the return direction. In this case, if the cross-sectional area of the recess is increased, the return resistance can be further reduced. However, since the recess is formed on the inner periphery of the cylinder, it is necessary to increase the outer diameter of the cylinder, which may increase the size of the damper. is there.
  • an object of the present invention is to provide a damper that can easily return the piston to a predetermined position of the cylinder and can suppress an increase in size.
  • the present invention is a damper that is attached between a pair of members that are close to and away from each other, and that applies a braking force when both members are close to or separate from each other.
  • a piston, and the rod has an engaging portion that engages with the piston when the rod moves in a return direction opposite to the damper braking direction, and the piston has a damper braking direction.
  • a notch is provided from one end on the opposite side to the other end on the damper braking direction side.
  • the piston is provided with a notch from one end opposite to the damper braking direction to the other end of the damper braking direction side.
  • the closed incision is pushed open by the air pressure, making it easier for the air between the cylinder and the piston to escape, so that the piston is in the return direction of the damper It is possible to reduce the resistance when moving to the piston and to easily return the piston, and it is possible to suppress the increase in size of the cylinder and the piston.
  • FIG. 6E is a cross-sectional view taken along the line BB of FIG. 6B, and FIG.
  • the piston which comprises the damper it is a perspective view which shows a state when a rod moves to the return direction on the opposite side to the braking direction of a damper.
  • the cap which comprises the damper is shown, (a) is the assembly perspective view, (b) is an exploded perspective view.
  • the use state of the damper is shown, (a) is an explanatory view of the state where the rod is stationary, (b) is an explanatory view of the state where the braking force of the damper is applied. It is an explanatory view of a state where the use state of the damper is shown and the braking force of the damper is released. It is a principal part expansion explanatory view of the damper.
  • (A) is a principal part expanded sectional view in the state where a rod stopped still
  • (b) is a principal part expansion explanatory view explaining a pressure contact state of a piston to a cylinder inner circumference in (a).
  • (A) is a principal part expanded sectional view of the state which the rod moved to the damper braking direction
  • (b) is a principal part expansion explanatory view explaining the pressure contact state of the piston with respect to the cylinder inner periphery in (a).
  • (A) is a principal part expanded sectional view of the state which the rod moved to the return direction on the opposite side to the braking direction of a damper
  • (b) is the principal part explaining the press-contact state of the piston with respect to a cylinder inner periphery in (a).
  • FIG. 12 shows a state where the piston has returned from the contracted state shown in FIG. 12, (a) is an enlarged cross-sectional view of the main part, and (b) explains the pressure contact state of the piston against the inner circumference of the cylinder in (a).
  • FIG. It is principal part expansion explanatory drawing of the damper which made the braking direction of the damper reverse with respect to the damper of the said embodiment.
  • a damper 10 shown in FIG. 1 is attached to a pair of members that are close to and away from each other, and applies a braking force when the pair of members approaches or separates.
  • the damper 10 is provided on an instrument panel of an automobile. It can be used for braking, such as a glove box and a lid, which are attached to the opening of the accommodating portion so as to be opened and closed.
  • one member is a fixed body such as an instrument panel housing, and the other member is attached to the opening of the fixed body so as to be openable and closable, such as a glove box and a lid.
  • the pair of members is not particularly limited as long as they are close to and away from each other.
  • the damper 10 of this embodiment is mounted on a cylinder 20 having a substantially cylindrical shape, a rod 30 movably inserted into the cylinder 20, and an axially distal end side of the rod 30.
  • the piston 50 is made of an elastic resin material, and the cap 80 is attached to the opening 22 of the cylinder 20.
  • the cylinder 20 of this embodiment has a substantially cylindrical wall portion 21 extending at a predetermined length, and one end side in the axial direction is opened to form an opening portion 22. ing. Further, the other end side of the wall portion 21 is closed by an end portion wall 23. An annular mounting portion 24 is provided outside the end wall 23, and the cylinder 20 is attached to one member such as an instrument panel via the mounting portion 24. . Furthermore, circular fitting holes 25, 25 are formed on one end side of the wall portion 21 so as to oppose each other in the circumferential direction (see FIG. 1).
  • a cap provided with an orifice may be attached by opening the other end side of the wall portion 21, and a mounting portion may be provided at a predetermined axial position on the outer periphery of the wall portion 21.
  • the outer diameter of the cylinder 20 is 12 mm or less, and it is more preferable that it is 8 mm or less.
  • the cap 80 in this embodiment has a pair of halves 81, 81 in the form of a half cylinder. They are integrated by engaging with each other via a locking piece 88 and a locked portion 90 locked to the locking piece 88.
  • Each halved body 81 is provided with a flange portion 83 on the outer periphery of the base end thereof, and a fitting protrusion 84 is provided on the outer periphery in the axial direction.
  • the cap 80 is inserted into the opening 22 of the cylinder 20 from the distal end side thereof, and the flanges 83 are locked to the base end surface of the cylinder 20 and the fitting protrusions 84 are fitted to the cylinder 20.
  • the cylinder 20 is mounted on the base end side (see FIGS. 7 and 8).
  • the rod 30 is inserted into the cylinder 20 through the opening 22 of the cylinder 20 so as to be movable from the tip side thereof, and is connected to a columnar shaft portion 31 and the tip side thereof. And a piston mounting portion 32 to which the piston 50 is mounted.
  • An annular attachment portion 33 is provided on the proximal end side of the shaft portion 31, and the rod 30 is attached to the other member such as a glove box via the attachment portion 33. Yes.
  • the piston mounting portion 32 is provided at the foremost end of the rod 30 in the axial direction, and includes a first engagement portion 34 having a substantially disc shape,
  • the first engagement portion 34 has a stopper portion 35 provided at a predetermined interval on the rod proximal end side.
  • the first engaging portion 34 is a portion that engages with the piston 50 as shown in FIG. 11 when the rod 30 moves in a braking direction in which the damper applies a braking force (see FIG. 11).
  • the first engaging portion 34 is engaged with one end side of the piston 50).
  • the braking direction of the damper in this embodiment means that the first engagement portion 34 is separated from the end wall 23 (see FIG. 7) of the cylinder 20 and the rod 30 is pulled out from the opening 22 of the cylinder 20. Means an increasing direction (see arrow F1 in FIGS. 7, 10 and 11).
  • the stopper portion 35 has a substantially circular protrusion shape as a whole, and cut portions 35a, 35a formed by cutting wall portions at positions on the first engagement portion 34 side on both sides in the circumferential direction. Are formed respectively.
  • Each cut portion 35a is provided with a flat surface continuous with the flat surface 40 provided on the second column portion 39 described later (see FIG. 2A).
  • the first engaging portion 34 and the stopper portion 35 are formed so that the outer diameter is larger than the inner diameter of the piston 50, and the distance between the first engaging portion 34 and the stopper portion 35 is the distance of the piston 50. It is formed longer than the axial length, and the piston 50 is mounted between the first engaging portion 34 and the stopper portion 35 so as to be extendable and contractable in the axial direction.
  • the piston mounting portion 32 is connected to the substantially columnar first column portion 36 extending from the inner surface side of the first engagement portion 34 toward the rod proximal end side, and the extending direction distal end of the first column portion 36. And a second engagement that engages with the piston 50 when the rod 30 moves in the return direction opposite to the braking direction of the damper (see arrow F2 in FIGS. 12 and 13).
  • a second column portion 39 having a substantially cylindrical shape extending from the proximal end side of the portion 37 and the second engagement portion 37 to the proximal end side of the rod via the recess 38 and connected to the stopper portion 35. And have.
  • the return direction opposite to the braking direction of the damper means that the first engagement portion 34 is placed on the end wall 23 of the cylinder 20 (see FIG. 7). This means that the rod 30 moves in the direction in which the pushing amount of the rod 30 into the cylinder 20 increases (see arrow F2 in FIGS. 8, 12 and 13).
  • the second engagement portion 37 is arranged on the return direction side of the damper from the press contact portion 53 described later of the piston 50. Yes. Further, the second engagement portion 37 and the second column portion 39 are larger in diameter than the first column portion 36 and smaller in diameter than the first engagement portion 34 and the stopper portion 35, and the first column The second pillar portion 39 is formed longer than the portion 36.
  • the second engagement portion 37 when the rod 30 moves in the return direction of the damper, as shown in FIGS. 12 (a) and 13 (a), the second engagement portion 37 will be described later of the piston 50. It engages with the engaged portion 61. That is, the “engagement portion” of the rod in the present invention means the second engagement portion 37.
  • the piston 50 in the state of being contracted in the axial direction and pressed against the inner periphery of the cylinder is elastically returned to the extended state.
  • the stopper portion 35 in the state where the piston 50 extends the longest, the stopper portion 35 abuts on the other end side of the piston 50 and the movement of the piston 50 is restricted. It has become so.
  • the flat surfaces 40, 40 which are cut in a planar shape along the axial direction of the rod 30, are formed so as to be parallel to each other.
  • the flat surface 40 formed on the second pillar portion 39 is flush with the flat surfaces of the cut portions 35a and 35a provided on the stopper portion 35.
  • the flat surface 40 forms a gap with respect to the inner periphery of the cylinder 20 and the inner periphery of the piston 50.
  • the protrusion 41 that contacts the inner periphery of the piston 50 extends in the axial direction from the second engagement portion 37 side to the proximal end side of the rod 30, and A plurality are formed side by side at a predetermined interval in the circumferential direction.
  • protrusions extending along the axial direction of the rod 30 on the outer periphery of the second column portion 39 on both sides of the flat surface 40 in the circumferential direction.
  • the ridges 41 and 41 are projected in a length extending from the distal end portion of the rod 30 closer to the second engagement portion 37 to the front portion of the stopper portion 35 (in this embodiment, the ridges are provided at a total of four ridges). 41).
  • a gap is formed between the inner periphery of the piston 50 and the outer periphery of the second column portion 39.
  • the groove portion 43 is formed at a predetermined depth along the axial direction of the first column portion 36 from one circumferential direction on the inner surface of the first engagement portion 34. Is formed. As shown in FIG. 2B, the groove 43 is provided between the flat surfaces 40 and 40 provided in the first engagement portion 34 and in the middle thereof. As shown in FIG.
  • an inclined portion 44 that is gradually reduced in diameter toward the proximal end side of the rod 30 is formed on the outer periphery on the distal end side of the shaft portion 31, that is, on the outer periphery of the connecting portion between the shaft portion 31 and the stopper portion 35.
  • an inclined portion 45 having a diameter gradually reduced toward the proximal end side of the rod 30 is also formed on the outer periphery on the distal end side of the first column portion 36.
  • the rod 30 having the above structure is inserted into the cylinder 20 from the first engaging portion 34 side at the tip and is disposed so as to be movable in the cylinder 20.
  • the first chamber R1 of the rod 30 located on the return direction side of the damper with the first engagement portion 34 of the rod 30 as a boundary, and the braking direction side of the damper of the rod 30
  • a second chamber R2 positioned at the same position.
  • a first chamber R 1 is formed on the end wall 23 side of the cylinder 20
  • a second chamber R 2 is formed on the opening 22 side of the cylinder 20.
  • the rod 30 described above includes the shaft portion 31, the attachment portion 33, the first engagement portion 34, the stopper portion 35, the second engagement portion 37, the other first pillar portion 36, and the second pillar portion 39.
  • the plurality of protrusions 41 and the like are all integrally formed.
  • the rod 30 is attached to the base end side of the first engagement portion 34 of the rod 30 so as to surround the rod 30 along the axial direction of the rod 30.
  • the piston 50 made of an elastic resin material will be described.
  • the piston 50 is made of, for example, a rubber elastic material such as rubber or elastomer, or a resin material such as sponge.
  • the piston 50 When the piston 50 is compressed in the axial direction, the diameter is increased and the piston 50 is pulled in the axial direction. In some cases, the diameter is reduced.
  • the piston 50 follows the rod 30 when moving in the braking direction of the damper and moves in the braking direction of the damper. On the other hand, the piston 50 also follows when the rod 30 moves in the returning direction of the damper. Move in the return direction of the damper.
  • the piston 50 of this embodiment has a main body 51 that extends in a predetermined length so as to form a substantially cylindrical shape, and whose outer periphery has a circumferential shape.
  • the outer periphery of one end 52 (the end located on the first engagement portion 34 side when the piston 50 is attached to the rod 30) of the main body 51 on the side opposite to the braking direction of the damper is It has a tapered shape that gradually decreases in diameter toward one end surface in the axial direction.
  • the outer periphery of the other end portion of the main body 51 on the braking direction side of the damper (the end portion positioned on the stopper portion 35 side in a state where the piston 50 is attached to the rod 30) is always on the inner periphery of the cylinder 20.
  • a pressure contact portion 53 is provided for applying a braking force to the piston 50 when the rod 30 is moved in pressure contact (both in the movement direction of the damper and in the return direction of the damper).
  • one end or one end of the piston on the opposite side to the braking direction of the damper is simply referred to as “one end” or “one end”, and the other end or the other end on the braking direction side of the damper is defined as the piston. This will be described simply as “the other end” or “the other end”.
  • the outer periphery of the piston 50 has a tapered shape in which the diameter increases from one end side to the other end side of the piston 50.
  • the outer periphery of the main body 51 constituting the piston 50 is formed in a tapered shape in which the diameter gradually increases from the other end side of the tapered one end portion 52 toward the press contact portion 53.
  • a cutout portion 54 extending in the axial direction is formed on the outer periphery of the main body 51 from the other end side of the tapered one end portion 52.
  • the notch 54 forms an air escape path between the inner circumference of the cylinder and the outer circumference of the piston (the main body 51 and the press-contact portion 53) to facilitate the expansion and contraction of the piston 50, and the damper control by the piston 50. It is intended to adjust the power.
  • the notch 54 has a shape obtained by cutting a part of the circumference of the outer periphery of the main body 51 in one plane when the piston 50 is viewed from the axial direction. And formed so as to be parallel to each other at two locations in the circumferential direction of the main body 51.
  • the notch portion 54 in this embodiment is formed so as to penetrate the pressure contact portion 53 in the axial direction and reach the other end of the main body 51.
  • a notch 54 between the outer periphery of the main body 51 from the press-contact part 53 to one end side and the inner periphery of the cylinder 20 in a state where the braking force of the damper is not acting.
  • a gap is formed.
  • the notch portion 54 of the press contact portion 53 can be used when the rod 30 or the piston 50 is stationary, when the damper is braked, or when the damper is released.
  • a gap is formed between the inner periphery of the cylinder 20 and the inner periphery of the cylinder 20.
  • the notch 54 in this embodiment is formed from the other end of the one end 52 of the main body 51 to the other end of the main body 51, but the one end 52 of the main body 51 is tapered. If not, the notch may be formed from one end of the main body 51 to the other end. However, the notch may be formed from one end of the main body 51 to the middle in the axial direction, or may not be formed on the outer periphery of the main body 51, and may be provided only on the pressure contact portion 53 on the other end side of the main body 51.
  • the pressure contact portion 53 in this embodiment protrudes in the outer diameter direction of the main body 51 of the piston 50 and extends elongated along the circumferential direction of the main body 51.
  • a pair of annular convex portions 56, 56 having an annular shape.
  • the pair of annular convex portions 56, 56 are disposed on the outer periphery of the other end portion of the main body 51 and between the notches 54, 54 provided at two places in the circumferential direction of the press contact portion 53. (See FIG. 4 (e)).
  • each annular convex portion 56 is disposed on the outer periphery of the other end of the main body 51, and a first convex portion 57 extending along the circumferential direction of the main body 51, and a piston with respect to the first convex portion 57. 50 is arranged in parallel at one end side with a predetermined interval, and extends along the circumferential direction of the main body 51, and both circumferential ends of the first convex portion 57 and the second convex portion 58. Are connected to each other. Further, inside the convex portions 57, 58, 59, a concave portion 60 having a concave groove shape extending at a predetermined depth along the circumferential direction of the main body 51 is provided.
  • the outermost diameters of the respective convex portions 57, 58, 59 are formed larger than the inner diameter of the cylinder 20, and the respective convex portions 57, 58, 59 are always pressed against the inner periphery of the cylinder 20. ing.
  • an engaged portion 61 that protrudes annularly along the circumferential direction is provided on the inner periphery of one end side of the main body 51.
  • the engaged portion 61 is adapted to engage with the second engaging portion 37 of the rod 30 when the rod 30 moves in the return direction of the damper ( FIG. 12 (a)).
  • a gap is formed between the first engagement portion 34 of the rod 30 and one end of the piston 50.
  • one end of the main body 51 is located on the inner periphery of the main body 51 at a position corresponding to the pair of notches 54 and 54.
  • Air flow grooves 62, 62 having a groove shape extending in the axial direction from the first end to the other end side are formed.
  • the air flow groove 62 is formed so that the second engagement portion 37 of the rod 30 is engaged with the engaged portion 61 of the piston 50 from one end of the main body 51. The length extends beyond the engagement portion 37 and the recess 38 to reach one end of the second column portion 39.
  • the air flow groove 62 forms a gap between the first column portion 36, the second engagement portion 37, and the outer periphery of one end side of the second column portion 39 of the rod 30, and the rod 30 and the piston. It becomes a part which distribute
  • the said air circulation groove should just be formed between the outer periphery of the rod 30, and the inner periphery of piston 50, for example, may be formed in the outer peripheral side of a rod.
  • one notch portion 54 provided on the outer periphery of the main body 51 extends across the entire axial direction of the piston 50 from one end of the piston 50 to the other end.
  • a cut 55 is formed.
  • the notch 55 communicates with one of the air flow grooves 62 and 62 formed on the inner periphery of the piston 50. Yes.
  • the piston 50 moves in the braking direction of the damper, the notch 55 is closed because the inside of the air circulation groove 62 is depressurized (see FIG. 7), while the piston 50 is in the return direction of the damper.
  • it When moving to, it is configured to be pushed and opened by the air flowing in from the air circulation groove 62 (see FIGS. 5 and 8).
  • the piston 50 is mounted on the piston mounting portion 32 from the outer diameter side of the rod 30. It is possible.
  • the notch 55 may not be formed in the whole area in the axial direction from one end of the main body 51 to the other end, but may be formed in a length extending in the axial direction from one end of the main body 51 to the other end side. .
  • a gap is formed between the engaging portion 34 and one end of the piston 50, and a cut portion 35 a provided in the stopper portion 35 is also provided between the stopper portion 35 of the rod 30 and the other end of the piston 50.
  • a gap is formed.
  • the first engagement portion 34 comes into contact with the one end portion 52 of the piston 50, and the cylinder 20
  • the axial compression force acts on the piston 50 between the pressure contact portion 53 and the inner circumference of the cylinder 50, whereby the piston 50 expands in diameter and the amount of pressure contact with the cylinder inner circumference increases.
  • the portion S of the piston 50 that is in pressure contact with the inner periphery of the cylinder 20 (the portion expressed by dotted hatching) is increased, and the friction of the piston 50 against the inner periphery of the cylinder 20 is increased.
  • the force can be increased, and the braking force of the damper can be increased.
  • the damper 10 in this embodiment has (1) the flat surface 40 of the first engagement portion 34 of the rod 30 and the inner periphery of the cylinder 20 as a passage for allowing air to pass through the piston 50 in the cylinder 20. (2) a clearance between the first engagement portion 34 of the rod 30 and one end of the piston 50, (3) a clearance between the groove portion 43 of the rod 30 and the inner periphery of the piston 50, and (4) an outer periphery of the rod 30 and the piston. 50, the clearance between the recess 30 of the rod 30 and the inner periphery of the piston 50, and (6) the clearance between the second column portion 39 of the rod 30 and the inner periphery of the piston 50.
  • the other member such as the opening / closing body opens with respect to one member such as the instrument panel, and the rod 30 moves in the braking direction of the damper as shown by an arrow F1 in FIG.
  • the first engaging portion 34 abuts on the one end portion 52 of the piston 50 and an axial compressive force acts on the piston 50 between the first contact portion 53 and the piston 50 to expand its diameter to the inner circumference of the cylinder. Since the amount of pressure contact increases, the portion S of the piston 50 that presses against the inner periphery of the cylinder 20 can be increased (see FIG. 11B) to increase the braking force of the damper, and the moving speed of the rod 30 Accordingly, it is possible to obtain the damper 10 having excellent load response characteristics in which the braking force varies according to the above.
  • the air in the first chamber R1 passes through the gap between the flat surface 40 of the first engaging portion 34 of the rod 30 and the inner periphery of the cylinder 20 in (1) above.
  • the air mainly flows into the gap between the outer periphery of the rod 30 and the air flow groove 62 of the piston 50.
  • the cut 55 in the closed state is pushed by air pressure and is gradually pushed from the inner edge side of the cut 55 (in this case, one end side of the piston 50 is opened).
  • the opening between the rod 30 and the inner periphery of the piston 50 can be discharged from the notch 55 to the other end side of the piston 50. it can.
  • the discharged air can be (7) the gap between the cut portion 35a of the stopper portion 35 of the rod 30 and the other end of the piston 50, or (8) the flat surface 40 of the stopper portion 35 of the rod 30 and the inner circumference of the cylinder 20. Is discharged to the outside of the piston mounting portion 32 of the rod 30.
  • part of the air is (3) the clearance between the groove portion 43 of the rod 30 and the inner periphery of the piston 50, (4) the clearance between the outer periphery of the rod 30 and the air flow groove 62 of the piston 50, and (5 ) Through the clearance between the recess 38 of the rod 30 and the inner periphery of the piston 50, and further through the clearance between the second column portion 39 of the rod 30 and the inner periphery of the piston 50 due to the above (6) protrusion 41, the other end side of the piston 50. Discharged from.
  • the piston 50 that has been reduced in diameter from the expanded state by the rod 30 that moves in the return direction of the damper returns to its original shape by its elastic restoring force. ing.
  • the main body 51 of the piston 50 is provided with the notch 55 from one end opposite to the damper braking direction to the other end of the damper braking direction. Therefore, when the piston 50 moves in the piston return direction, the notch 55 in the closed state is pushed and opened as shown in FIGS. 5 and 8, so that the air between the rod 30 and the piston 50 is discharged. As a result, the resistance when the piston 50 moves in the piston return direction can be reduced, and the piston 50 can be easily returned to the predetermined position of the cylinder 20.
  • the notch 55 is provided in the piston 50, when the rod 30 moves in the return direction of the damper, the notch 55 can be opened and an air flow passage can be secured, so the first engaging portion of the rod 30 can be secured.
  • the gap in the axial direction between 34 and the other end of the piston 50 can be reduced.
  • the first engagement portion 34 of the rod 30 can be quickly brought into contact with the other end of the piston 50 to exert a braking force.
  • the idle running distance of the piston 50 at the time of damper braking can be reduced (the responsiveness of the piston 50 at the time of damper braking can be increased, and the play until the damper starts to be braked can be reduced).
  • the piston 50 can be easily returned to the predetermined position, the cylinder 20 and the piston 50 can be prevented from being enlarged, and the damper 10 can be prevented from being enlarged.
  • the notch 55 is closed, so that the pressure contact force of the outer periphery of the piston 50 against the inner periphery of the cylinder 20 is impaired. Since this can be suppressed, the influence on the braking force of the damper can be reduced.
  • an air circulation groove 62 communicating with the cut 55 is formed between the outer periphery of the rod 30 and the inner periphery of the piston 50. Therefore, when the piston 50 moves in the piston return direction and air enters the air circulation groove 62, the closed cut 55 is pushed and opened as shown in FIGS. The air between 50 can be easily discharged. That is, by providing the air circulation groove 62, the cut 55 in the closed state can be easily opened. As a result, the resistance when the piston 50 moves in the piston return direction can be further reduced, and the piston 50 can be more easily returned to the predetermined position of the cylinder 20.
  • the notch 55 provided in the piston 50 extends from one end of the piston 50 to the other end over the entire axial direction of the piston 50.
  • the notch 55 can be made easier to open by the air that has entered the air flow groove 62, and the piston 50 is predetermined. It can be made easy to return depending on the position. Further, since the entire piston 50 can be opened in the axial direction through the notch 55, the piston 50 can be easily mounted on the outer periphery of the rod 30 (here, the piston mounting portion 32 of the rod 30).
  • the outer periphery of the piston 50 expands from one end side of the piston 50 toward the other end side. It has a tapered taper shape. Therefore, as shown in FIG. 8, when the piston 50 moves in the return direction of the damper, the outer periphery of the portion of the piston 50 where the notch 55 is provided gradually receives the surface pressure from the inner periphery of the cylinder 20. The notch 55 can be easily opened, and the piston 50 can be more easily returned to the predetermined position.
  • a notch portion 54 that forms a gap between the outer periphery of the piston 50 and the inner periphery of the cylinder 20. Is formed from one end side to the other end side, and the notch 54 is provided so that the notch 55 is positioned. According to this, by providing the notch 55 in the notch 54 provided on the outer periphery of the piston 50, the sealing performance (adhesiveness to the inner periphery of the cylinder 20) of the piston 50 other than the notch 54 is provided. The incision 55 can be provided without damaging, and the braking force of the damper can be hardly affected.
  • the first engagement portion 34 of the rod 30 moves in a direction away from the end wall 23 of the cylinder 20
  • a braking force is applied by the damper, and the first engagement portion 34.
  • the first engaging portion of the rod is When moving in the direction close to the end wall (which also includes the cap attached to the cylinder end), the braking force is applied by the damper, and the braking force is released when moving in the direction away from the end wall.
  • FIG. 14 shows an enlarged explanatory view of a main part of the damper 10 ⁇ in which the braking direction of the damper is reversed.
  • This damper 10A is different from the above embodiment in the shape of the rod and the mounting direction of the piston.
  • the rod 30 has a shape in which the first column portion 36 extends longer than the second column portion 39.
  • the piston 50 is disposed on the piston mounting portion 32 of the rod 30 in a state where one end portion 52 thereof faces the stopper portion 35 of the rod 30 and the pressure contact portion 53 of the piston 50 faces the first engagement portion 34 of the rod 30.
  • a piston 50 is mounted, and the mounting direction of the piston 50 is opposite to that of the damper of each of the above embodiments.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Vibration Dampers (AREA)

Abstract

La présente invention concerne un amortisseur qui peut empêcher le sur-dimensionnement de l'amortisseur et dans lequel un piston peut être facilement ramené à une position prédéterminée dans un cylindre. Cet amortisseur (10) comporte : un cylindre (20); une tige (30); un piston (50) qui est fabriqué en résine élastique et qui est fixé à la tige (30). La tige (30) comprend une seconde partie de mise en prise (37) qui vient en prise avec le piston (50) lors du déplacement dans une direction de retour qui est opposée à une direction de freinage de l'amortisseur. Une rainure de circulation d'air (62) est formée entre la circonférence externe de la tige (30) et la circonférence interne du piston (50), ledit piston (50) ayant une fente (55) formée d'une extrémité située à l'opposé du côté de la direction de freinage de l'amortisseur vers l'autre extrémité située du côté de la direction de freinage de l'amortisseur, de manière à être reliée à la rainure de circulation d'air (62).
PCT/JP2019/012155 2018-03-28 2019-03-22 Amortisseur Ceased WO2019188810A1 (fr)

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JP2020509976A JP6961801B2 (ja) 2018-03-28 2019-03-22 ダンパー

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Application Number Priority Date Filing Date Title
JP2018061865 2018-03-28
JP2018-061865 2018-03-28

Publications (1)

Publication Number Publication Date
WO2019188810A1 true WO2019188810A1 (fr) 2019-10-03

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ID=68061733

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PCT/JP2019/012155 Ceased WO2019188810A1 (fr) 2018-03-28 2019-03-22 Amortisseur

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JP (1) JP6961801B2 (fr)
WO (1) WO2019188810A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5828138U (ja) * 1981-08-18 1983-02-23 石川　静子 空気式減速装置
JPH024036U (fr) * 1988-06-20 1990-01-11
JPH08105481A (ja) * 1994-10-07 1996-04-23 Nifco Inc エアダンパ
EP1619340A1 (fr) * 2004-07-23 2006-01-25 Lushridge Incorporated Amortisseur pour porte d'armoire
JP2009103270A (ja) * 2007-10-25 2009-05-14 Nifco Inc ダンパ及びこのダンパを備えたドアハンドル

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5970944U (ja) * 1982-11-04 1984-05-14 トヨタ自動車株式会社 シヨツクアブソ−バ
TWM362318U (en) * 2009-03-06 2009-08-01 Sun Chain Trading Co Ltd Structural improvement of pressure bar

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5828138U (ja) * 1981-08-18 1983-02-23 石川　静子 空気式減速装置
JPH024036U (fr) * 1988-06-20 1990-01-11
JPH08105481A (ja) * 1994-10-07 1996-04-23 Nifco Inc エアダンパ
EP1619340A1 (fr) * 2004-07-23 2006-01-25 Lushridge Incorporated Amortisseur pour porte d'armoire
JP2009103270A (ja) * 2007-10-25 2009-05-14 Nifco Inc ダンパ及びこのダンパを備えたドアハンドル

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JP6961801B2 (ja) 2021-11-05

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