WO2011145576A1 - ダンパー - Google Patents
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- Publication number
- WO2011145576A1 WO2011145576A1 PCT/JP2011/061229 JP2011061229W WO2011145576A1 WO 2011145576 A1 WO2011145576 A1 WO 2011145576A1 JP 2011061229 W JP2011061229 W JP 2011061229W WO 2011145576 A1 WO2011145576 A1 WO 2011145576A1
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- WO
- WIPO (PCT)
- Prior art keywords
- ring
- silicone rubber
- damper
- torque
- housing
- Prior art date
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Classifications
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- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
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- 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
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/12—Devices with one or more rotary vanes turning in the fluid any throttling effect being immaterial, i.e. damping by viscous shear effect only
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- C—CHEMISTRY; METALLURGY
- C08—ORGANIC MACROMOLECULAR COMPOUNDS; THEIR PREPARATION OR CHEMICAL WORKING-UP; COMPOSITIONS BASED THEREON
- C08G—MACROMOLECULAR COMPOUNDS OBTAINED OTHERWISE THAN BY REACTIONS ONLY INVOLVING UNSATURATED CARBON-TO-CARBON BONDS
- C08G77/00—Macromolecular compounds obtained by reactions forming a linkage containing silicon with or without sulfur, nitrogen, oxygen or carbon in the main chain of the macromolecule
- C08G77/04—Polysiloxanes
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- C—CHEMISTRY; METALLURGY
- C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
- C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
- C09K3/00—Materials not provided for elsewhere
- C09K3/10—Materials in mouldable or extrudable form for sealing or packing joints or covers
- C09K3/1006—Materials in mouldable or extrudable form for sealing or packing joints or covers characterised by the chemical nature of one of its constituents
- C09K3/1018—Macromolecular compounds having one or more carbon-to-silicon linkages
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- 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
- F16F9/36—Special sealings, including sealings or guides for piston-rods
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- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
Definitions
- the present invention relates to a damper that brakes the rotation of a driven gear that meshes with a gear or a rack, for example.
- Patent Document 1 describes a damper in which a part of a rotating shaft protrudes from a housing filled with damper oil, and a rotor braking plate rotatably housed in the housing is connected to the lower end portion of the rotating shaft. Has been. An annular seal member is provided between the housing and the rotating shaft to prevent the damper oil from leaking out of the housing.
- an O-ring formed of ethylene propylene diene rubber (EPDM) having non-swelling property with respect to silicone oil is used as an annular sealing material.
- EPDM ethylene propylene diene rubber
- the present invention provides a damper that can reduce the starting torque and suppress variations in torque in the low speed region in consideration of the above facts.
- a housing, a damper oil filled in the housing, a rotating shaft partially protruding from the housing, and a lower end portion of the rotating shaft are connected to the housing.
- the annular sealing material provides a damper made of silicone rubber having a hardness of 25 degrees or more and 45 degrees or less according to a durometer hardness test (A type) of JIS K6253. .
- the annular sealing material is disposed between the rotating shaft of the rotor and the housing.
- the silicone rubber has a loss tangent of 0.12 at a temperature of 23 ° C. ⁇ 2 ° C. determined from dynamic viscoelasticity measurement at a frequency of 1 Hz. It is good also as 0.25 or less.
- the silicone rubber constituting the annular sealing material has a loss tangent of not less than 0.12 and not more than 0.25 at a temperature of 23 ° C. ⁇ 2 ° C. determined from dynamic viscoelasticity measurement at a frequency of 1 Hz. . For this reason, stick slips caused by the annular sealing material are hardly generated, and the torque waveform is stabilized.
- loss tangent loss elastic modulus (viscous component) / storage elastic modulus (elastic component).
- the first aspect of the present invention has the above-described configuration, it is possible to reduce the starting torque and to suppress the torque variation in the low speed range.
- the torque waveform is stable.
- FIG. 3 is a cross-sectional view taken along the line 1-1 in FIG. It is a top view which shows the rotation damper which is this Embodiment. It is a top view which shows the O-ring which is this Embodiment.
- FIG. 4 is a cross-sectional view taken along the line 4-4 in FIG. It is a torque characteristic figure which shows rotation follow-up property when the said hardness of the silicone rubber which comprises O ring of a rotation damper is 27 degree
- FIG. 1 is a cross-sectional view taken along the line 1-1 in FIG. 2, and FIG. 2 is a plan view of the rotary damper according to the present embodiment.
- the rotary damper 10 of the present embodiment includes a housing 12, and the housing 12 includes a housing main body 14 formed of a synthetic resin and a cap 16 formed of a synthetic resin.
- the inside of the housing 12 is filled with silicone oil (damper oil) 18 as damper oil.
- the rotor 20 of the rotary damper 10 includes a rotating shaft 22 that partially protrudes from the housing 12, and a rotor braking plate 24 that is connected to the lower end portion of the rotating shaft 22 and is rotatably accommodated in the housing 12.
- Have An O-ring (annular seal material) 30 as an annular seal material of the rotary damper 10 is disposed between the housing 12 and the rotary shaft 22 so as to prevent the silicone oil 18 from leaking out of the housing 12. It has become.
- a driven gear 40 is attached to the portion of the rotary shaft 22 protruding from the housing 12.
- the housing main body 14 includes a cylindrical portion 14A having a bottom, a support shaft 14B having a circular cross section that is connected to the center of the cylindrical portion 14A and projects upward from the cylindrical portion 14A, and an outer position facing the cylindrical portion 14A. And mounting pieces 14C and 14D which are continuously provided so as to extend outward in the radial direction.
- the attachment piece 14C is provided with an attachment hole 42, and the attachment piece 14D is provided with an attachment recess 44.
- a circular through hole 46 through which the rotary shaft 22 passes is provided at the center of the cap 16.
- the cap 16 includes a circular top plate 16A and a peripheral wall 16B provided around the periphery of the top plate 16A.
- a portion of the top plate 16A that is continuous with the lower end of the through hole 46 is provided with an O-ring accommodating portion 48 that is concentric with the through hole 46 and has a stepped diameter larger than that of the through hole 46.
- the cylindrical portion 14A of the housing main body 14 is fitted.
- the rotary shaft 22 includes a large-diameter shaft portion 22A and an attachment shaft portion 22B concentrically connected to the upper side of the large-diameter shaft portion 22A. Further, the large-diameter shaft portion 22A is formed with a bearing portion 22C formed of a cylindrical recess, and the support shaft 14B of the housing body 14 is rotatably inserted into the bearing portion 22C from below. On the other hand, the driven gear 40 is attached to the attachment shaft portion 22B of the rotary shaft 22 so as to rotate integrally.
- the mounting shaft portion 22B of the rotating shaft 22 is formed in an I-cut shape so as to rotate the driven gear 40 integrally, and a locking recess 22D is provided in a lower portion of the parallel surface.
- the rotor braking plate 24 is provided on the outer periphery of the lower end of the large-diameter shaft portion 22A in a disc shape concentric with the large-diameter shaft portion 22A.
- the driven gear 40 is provided with a mounting hole 52 having an engaging portion 50 corresponding to the locking recess 22D on the inner peripheral surface.
- the rotary damper 10 can be mounted at a desired position by the mounting hole 42 of the mounting piece 14C of the housing main body 14 and the mounting recess 44 of the mounting piece 14D, and the gear or rack that is braked by the driven gear 40. It can be meshed with each other.
- the rotor braking plate 24 rotates in the housing 12 filled with the silicone oil 18.
- the viscous resistance and shear resistance of the silicone oil 18 act on the rotor braking plate 24, thereby braking the rotation of the driven gear 40.
- the rotation damper 10 can brake the rotation or movement of the gear, the rack, etc. with which the driven gear 40 meshes, and can slow the rotation or movement.
- the O-ring 30 is made of silicone rubber. This silicone rubber has no self-lubrication and has a hardness of 25 degrees or more and 45 degrees or less according to a JISK6253 durometer hardness test (A type). The term “no self-lubricating” means that no lubricating oil component is contained.
- silicone rubber has the above-mentioned hardness with a structure that does not contain a self-lubricating additive.
- the self-lubricating additive is methyl phenyl silicone oil, dimethyl silicone oil or the like. Therefore, by setting the hardness of the silicone rubber to 25 degrees or more and 45 degrees or less, the torque caused by the O-ring 30 is suppressed, so that the starting torque of the rotary damper 10 is reduced and the low speed of the rotary damper 10 is reduced. Variation in torque in the rotation region is reduced.
- the hardness of the silicone rubber is preferably 25 degrees or more and 40 degrees or less.
- the hardness of the silicone rubber is more preferably 30 degrees or more and 40 degrees or less.
- the hardness of the silicone rubber constituting the O-ring 30 exceeds 45 degrees, the above effect cannot be obtained. If the hardness of the silicone rubber constituting the O-ring 30 does not reach 25 degrees, the silicone rubber Due to the insufficient hardness of the rubber, it becomes difficult to mold the annular sealing material.
- this silicone rubber has a loss tangent (tan ⁇ ) of 0.12 or more and 0.25 or less at a temperature of 23 ° C. ⁇ 2 ° C. determined from dynamic viscoelasticity measurement at a frequency of 1 Hz.
- the loss tangent at 1 Hz of the silicone rubber constituting the O-ring 30 does not reach 0.12, the above effect cannot be obtained, and the frequency of the silicone rubber constituting the O-ring 30 is 1 Hz. If the loss tangent exceeds 0.25, it becomes difficult to mold the annular sealing material due to insufficient hardness of the silicone rubber.
- the loss tangent (tan ⁇ ) of the silicone rubber is preferably 0.13 or more and 0.25 or less.
- the torque characteristic indicating the rotational followability of the rotary damper 10 is measured.
- the O-ring 30 used in this measurement 1 has an outer diameter D1 of 5.62 mm, an inner diameter D2 of 3.5 mm, and a circular cross section diameter (cross section diameter) D3 of 1.06 mm shown in FIGS.
- the crushing margin is 14.14% and the inner diameter elongation rate is 3.43%.
- the torque characteristic measurement method showing the rotation follow-up is arranged by rotating the rotary damper 10 on the lower attachment of the minute torque measuring device (MD-202R type manufactured by Ono Sokki Co., Ltd.), and rotating the upper side of the minute torque measuring device. Torque is measured by the torque detector. Note that the number n of measurement samples for each hardness is 30, and the temperature during measurement is 23 ° C. ⁇ 2 ° C.
- FIG. 5 is a torque characteristic diagram showing the rotational followability when the hardness of the silicone rubber constituting the O-ring 30 is 27 degrees.
- FIG. 6 is a torque characteristic diagram showing the rotational followability when the hardness of the silicone rubber constituting the O-ring 30 is 30 degrees.
- FIG. 7 is a torque characteristic diagram showing the rotation follow-up property when the hardness of the silicone rubber constituting the O-ring 30 is 40 degrees.
- FIG. 8 is a torque characteristic diagram showing rotation follow-up performance when the hardness of the silicone rubber constituting the O-ring 30 is 45 degrees.
- FIG. 9 is a torque characteristic diagram showing the rotational followability when the hardness of the silicone rubber constituting the O-ring 30 is 50 degrees.
- FIG. 10 is a torque characteristic diagram showing the rotational followability when the hardness of the silicone rubber constituting the O-ring 30 is 80 degrees.
- the vertical axis represents torque (mN ⁇ m) and the horizontal axis represents rotation speed (r / min).
- a range X1 in each figure shows variation in the number n of measurement samples.
- the method for measuring the empty torque waveform is as follows.
- the rotational damper 10 is placed on the lower attachment of the minute torque measuring device (MD-202R type manufactured by Ono Sokki Co., Ltd.) and rotated, and the upper torque detector of the minute torque measuring device is rotated.
- the measurement temperature is 23 ° C. ⁇ 2 ° C.
- FIG. 11 shows a change in torque over time when the hardness of the silicone rubber constituting the O-ring 30 is 27 degrees.
- FIG. 12 shows the time variation of the torque when the hardness of the silicone rubber constituting the O-ring 30 is 30 degrees.
- FIG. 13 shows a change in torque over time when the hardness of the silicone rubber constituting the O-ring 30 is 40 degrees.
- FIG. 14 shows a change in torque over time when the hardness of the silicone rubber constituting the O-ring 30 is 45 degrees.
- FIG. 15 shows a change in torque over time when the hardness of the silicone rubber constituting the O-ring 30 is 50 degrees.
- FIG. 16 shows a change in torque over time when the hardness of the silicone rubber constituting the O-ring 30 is 80 degrees.
- the vertical axis represents torque (gf ⁇ cm) and the horizontal axis represents time (min).
- T1, T3, T5, and T7 indicate measurement start times
- T2, T4, T6, and T8 indicate measurement end times.
- the hardness of the silicone rubber constituting the O-ring 30 of the rotary damper 10 exceeds 45 degrees, the above effect cannot be obtained, and if the hardness of the silicone rubber does not reach 25 degrees, Due to the lack of hardness, it becomes difficult to form the O-ring 30. For this reason, the hardness of the silicone rubber, that is, the hardness according to the JISK6253 durometer hardness test (A type) is set to 25 degrees or more and 45 degrees or less.
- the loss tangent (tan ⁇ ) loss elastic modulus (viscous component) / storage elastic modulus (elastic component) of the silicone rubber (A, B, C, D) at each frequency is calculated.
- the loss elastic modulus was measured using a viscoelasticity measuring device (Rheometer, manufactured by Leo Laboratories), the measurement temperature was constant at 25 ° C., and the measured strain was measured in the linear strain region.
- the O-ring used for measurement 3 has the same shape as measurement 1.
- FIG. 17 is a graph showing the relationship between each measurement frequency and loss tangent when the silicone rubber constituting the O-ring 30 is A, B, C, and D.
- the time change (empty torque waveform) of the torque of the rotary damper 10 when the silicone rubber constituting the O-ring 30 is A, B, C, D is measured.
- the measurement temperature is 23 ° C. ⁇ 2 ° C.
- the O-ring used for this measurement 4 is the same as that for measurement 3.
- FIG. 18 shows a change in torque over time when the silicone rubber constituting the O-ring 30 is A.
- FIG. 19 shows a change in torque over time when the silicone rubber constituting the O-ring 30 is B.
- FIG. 20 shows a change in torque over time when the silicone rubber constituting the O-ring 30 is C.
- FIG. 21 shows the time change of torque when the silicone rubber constituting the O-ring 30 is D.
- the vertical axis represents torque (gf ⁇ cm) and the horizontal axis represents time (min).
- T1, T3, and T5 indicate measurement start times
- T2, T4, and T6 indicate measurement end times.
- the silicone rubber constituting the O-ring 30 has a loss tangent of not less than 0.12 and not more than 0.25 at a temperature of 23 ° C. ⁇ 2 ° C. obtained from dynamic viscoelasticity measurement at a frequency of 1 Hz.
- the rotating damper using the O-ring made of the silicone rubber (with the hardness of 35 degrees) of the present embodiment and the comparative rotating damper using the O-ring made of the EPDM (with the hardness of 50 degrees) are respectively mounted on the same vehicle. It is attached to the open / close door of the console box for measuring the variation in opening operation time. Note that the number of measurement samples n is 30.
- FIG. 22 is a graph showing the distribution of the opening operation time of the open / close door of the in-vehicle console box to which the rotary damper of this embodiment is attached.
- FIG. 23 is a graph showing the distribution of the opening operation time of the open / close door of the in-vehicle console box to which the rotary damper of the comparative example is attached.
- the vertical axis represents the operating time (sec)
- the horizontal axis represents the number n.
- the in-vehicle console box to which the rotary damper according to the present embodiment is attached has less variation in operation time than the in-vehicle console box to which the comparative example rotary damper is attached.
- FIG. 24 is a graph showing the relationship between the passage of time and the angular velocity during the opening operation of the open / close door of the in-vehicle console box to which the rotary damper of this embodiment is attached.
- 25 is a graph showing the relationship between the passage of time and the angular velocity during the opening operation of the opening / closing door of the in-vehicle console box to which the rotary damper of the comparative example is attached. 24 and 25, each angular speed (deg / sec), and the horizontal axis represents time (sec).
- the vehicle-mounted console box to which the rotary damper according to the present embodiment is attached is compared with the vehicle-mounted console box to which the comparative example rotary damper is mounted. 24 and the range of Y1 in FIG. 25) is small, and the variation in the entire opening operation time (the range of T1 in FIGS. 24 and 25) is also small.
- FIG. 26 is a graph showing a distribution of opening operation times of the opening / closing doors of the in-vehicle console box in which the O-ring-use rotary damper subjected to the sandblasting process (SB # 120) is attached to the mold.
- FIG. 27 is a graph showing the distribution of the opening operation time of the opening / closing doors of the in-vehicle console box in which the O-ring-use rotary damper subjected to the sandblasting process (SB # 220) is attached to the mold.
- FIG. 28 is a graph showing the distribution of the opening operation time of the opening / closing doors of the in-vehicle console box in which a rotary damper using an O-ring that has been sandblasted (SB # 320) is attached to the mold.
- FIG. 29 is a graph showing a distribution of opening operation times of the opening / closing doors of the in-vehicle console box in which a rotating damper using an O-ring subjected to sandblasting (SB # 400) is attached to a mold. 26 to 29, the vertical axis represents the operating time (sec) and the horizontal axis represents the number n.
- the NAK55 material made of Daido Steel is used for the mold for manufacturing the O-ring 30 and the molding surface is sandblasted (SB # 120 or SB # 220), and the outer periphery of the O-ring 30 By smoothing the surface, variations in operation time are reduced as compared with the sandblasting process (SB # 320 or SB # 400).
- sandblasting SB # 220 that improves the durability of the O-ring 30 is preferable.
- the silicone oil 18 is used as the damper oil.
- a highly refined paraffinic base oil or the like may be used as the damper oil instead of the silicone oil 18.
- the O-ring 30 having a circular cross section is used as the annular sealing material.
- other annular sealing materials such as an O-ring having a different cross section may be used.
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Abstract
Description
次に、本実施形態の回転ダンパー10の動作について説明する。
次に、本実施形態のOリング30について説明する。
従って、シリコーンゴムの上記硬さを25度以上45度以下とすることで、Oリング30に起因するトルクが抑制されるため、回転ダンパー10の起動トルクが低減すると共に、回転ダンパー10の低速度回転領域でのトルクのばらつきが低減される。なお、シリコーンゴムの上記硬さは25度以上40度以下が好ましい。また、シリコーンゴムの上記硬さは30度以上40度以下がさらに好ましい。
本実施形態では、回転ダンパー10の回転追従性を示すトルク特性を測定している。この測定1に使用されているOリング30は、図3及び図4に示す外径D1が5.62mm、内径D2が3.5mm、円形断面の直径(断面径)D3が1.06mmであって、潰れ代が14.14%、内径伸張率3.43%となっている。
また、本実施形態では、各回転ダンパー10のトルクの時間変化(空トルク波形)をそれぞれ測定している。なお、この測定2に使用されているOリングは測定1と同じOリングとなっている。
図11はOリング30を構成するシリコーンゴムの上記硬さが27度のときのトルクの時間変化である。
本実施形態では、Oリング30を構成するシリコーンゴム(表1のA、B、C、D)の損失正接を算出している。
図17は、Oリング30を構成するシリコーンゴムがA、B、C、Dのときの各測定周波数と損失正接との関係を示すグラフである。
(測定4)
また、本実施形態では、Oリング30を構成するシリコーンゴムがA、B、C、Dのときの、回転ダンパー10のトルクの時間変化(空トルク波形)を測定している。
図18はOリング30を構成するシリコーンゴムがAのときのトルクの時間変化である。
また、本実施形態のシリコーンゴム(上記硬さ35度)からなるOリングを使用した回転ダンパーと、EPDM(上記硬さ50度)からなるOリングを使用した比較例回転ダンパーとをそれぞれ同じ車載用コンソールボックスの開閉扉に取付けて、開放作動時間のばらつきを測定している。なお、測定サンプル数nは30とする。
図22は本実施形態の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時間の分布を示すグラフである。
図23は比較例の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時間の分布を示すグラフである。
なお、図22及び図23の、縦軸は作動時間(sec)で、横軸は個数nである
また、本実施形態のシリコーンゴム(上記硬さ35度)からなるOリングを使用した回転ダンパーと、EPDM(上記硬さ50度)からなるOリングを使用した比較例回転ダンパーとをそれぞれ同じ車載用コンソールボックスの開閉扉に取付けて、開放作動時の時間経過と角速度との関係を測定している。なお、測定サンプル数nは30とする。
(測定6の結果)
図24は本実施形態の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時の時間経過と角速度との関係を示すグラフである。
図25は比較例の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時の時間経過と角速度との関係を示すグラフである。
なお、図24及び図25の、角各速(deg/sec)で、横軸は時間(sec)である。
また、本実施形態では、金型に大同特殊鋼製のNAK55材を使用し、金型の成形表面にサンドブラスト処理(SB♯120、SB♯220、SB♯320、SB♯400)をして製造したOリング30(上記硬さ35度)を使用した回転ダンパーをそれぞれ同じ車載用コンソールボックスの開閉扉に取付けて、開放作動時間のばらつきを測定している。なお、測定サンプル数nは5とする。
図26は金型にサンドブラスト処理(SB♯120)をしたOリング使用の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時間の分布を示すグラフである。
図27は金型にサンドブラスト処理(SB♯220)をしたOリング使用の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時間の分布を示すグラフである。
図28は金型にサンドブラスト処理(SB♯320)をしたOリング使用の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時間の分布を示すグラフである。
図29は金型にサンドブラスト処理(SB♯400)をしたOリング使用の回転ダンパーを取付けた車載用コンソールボックスの開閉扉の開放作動時間の分布を示すグラフである。
なお、図26~図29の縦軸は作動時間(sec)で横軸は個数nである
以上に於いては、本発明を特定の実施形態について詳細に説明したが、本発明は上記実施形態に限定されるものではなく、本発明の範囲内にて他の種々の実施形態が可能であることは当業者にとって明らかである。例えば、上記実施形態では、ダンパーオイルとしてシリコーンオイル18を使用したが、シリコーンオイル18に代えて高度に精錬したパラフィン系基油等をダンパーオイルとして使用してもよい。
Claims (2)
- ハウジングと、
このハウジング内に充填されたダンパーオイルと、
前記ハウジングから一部が突出する回転軸と、この回転軸の下端部に連設されて前記ハウジング内に回転可能に収納されたローター制動板と、を有するローターと、
前記ダンパーオイルが前記ハウジングの外へ漏れるのを防止するために、前記ハウジングと前記回転軸との間に配設された環状シール材と、
を有し、前記環状シール材はJISK6253のデュロメータ硬さ試験(Aタイプ)による硬さが25度以上45度以下のシリコーンゴムからなるダンパー。 - 前記シリコーンゴムは周波数が1Hzでの動的粘弾性測定から求められる温度23℃±2℃での、損失正接が0.12以上0.25以下である請求項1に記載のダンパー。
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201180024661.2A CN102893050B (zh) | 2010-05-19 | 2011-05-16 | 阻尼器 |
ES11783510T ES2851011T3 (es) | 2010-05-19 | 2011-05-16 | Amortiguador |
US13/698,214 US20130153347A1 (en) | 2010-05-19 | 2011-05-16 | Damper |
MX2012013417A MX2012013417A (es) | 2010-05-19 | 2011-05-16 | Amortiguador. |
EP11783510.8A EP2573421B1 (en) | 2010-05-19 | 2011-05-16 | Damper |
KR1020127032394A KR101396651B1 (ko) | 2010-05-19 | 2011-05-16 | 댐퍼 |
HK13107215.9A HK1180027A1 (en) | 2010-05-19 | 2013-06-20 | Damper |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010115262 | 2010-05-19 | ||
JP2010-115262 | 2010-05-19 | ||
JP2010-191191 | 2010-08-27 | ||
JP2010191191A JP5613502B2 (ja) | 2010-05-19 | 2010-08-27 | ダンパー |
Publications (1)
Publication Number | Publication Date |
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WO2011145576A1 true WO2011145576A1 (ja) | 2011-11-24 |
Family
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/061229 WO2011145576A1 (ja) | 2010-05-19 | 2011-05-16 | ダンパー |
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US (1) | US20130153347A1 (ja) |
EP (1) | EP2573421B1 (ja) |
JP (1) | JP5613502B2 (ja) |
KR (1) | KR101396651B1 (ja) |
CN (1) | CN102893050B (ja) |
ES (1) | ES2851011T3 (ja) |
HK (1) | HK1180027A1 (ja) |
MX (1) | MX2012013417A (ja) |
MY (1) | MY158878A (ja) |
WO (1) | WO2011145576A1 (ja) |
Cited By (1)
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JP7490539B2 (ja) | 2020-11-13 | 2024-05-27 | 株式会社カーメイト | 軸受部の封止構造 |
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AT512300B1 (de) * | 2012-01-25 | 2013-07-15 | Fulterer Gmbh | Vorrichtung zur dämpfung der bewegung eines beweglich gelagerten bauteils |
AT512306B1 (de) | 2012-01-25 | 2013-07-15 | Fulterer Gmbh | Vorrichtung zur dämpfung der bewegung eines beweglich gelagerten bauteils |
US9777513B2 (en) | 2012-01-25 | 2017-10-03 | Fulterer Gesellschaft Mbh | Pull-out device for at least two pull-out furniture parts |
AT512415B1 (de) | 2012-03-20 | 2013-08-15 | Fulterer Gmbh | Zuziehvorrichtung für ein beweglich gelagertes Möbelteil |
US9435154B2 (en) * | 2014-11-05 | 2016-09-06 | Chin-Fu Chen | Blind body positioning mechanism for non pull cord window blind and window blind using the same |
JP6258188B2 (ja) * | 2014-11-27 | 2018-01-10 | 株式会社ニフコ | ダンパー及びダンパーの製造方法 |
JP6359441B2 (ja) * | 2014-12-16 | 2018-07-18 | 株式会社ニフコ | ダンパーの製造方法 |
US11988263B2 (en) * | 2019-05-28 | 2024-05-21 | Piolax, Inc. | Damper device |
WO2022013782A1 (en) * | 2020-07-17 | 2022-01-20 | 3M Innovative Properties Company | Seal component for cable connection |
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-
2011
- 2011-05-16 KR KR1020127032394A patent/KR101396651B1/ko active IP Right Grant
- 2011-05-16 US US13/698,214 patent/US20130153347A1/en not_active Abandoned
- 2011-05-16 MX MX2012013417A patent/MX2012013417A/es unknown
- 2011-05-16 CN CN201180024661.2A patent/CN102893050B/zh active Active
- 2011-05-16 EP EP11783510.8A patent/EP2573421B1/en active Active
- 2011-05-16 ES ES11783510T patent/ES2851011T3/es active Active
- 2011-05-16 WO PCT/JP2011/061229 patent/WO2011145576A1/ja active Application Filing
- 2011-05-16 MY MYPI2012700939A patent/MY158878A/en unknown
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2013
- 2013-06-20 HK HK13107215.9A patent/HK1180027A1/xx unknown
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JP7490539B2 (ja) | 2020-11-13 | 2024-05-27 | 株式会社カーメイト | 軸受部の封止構造 |
Also Published As
Publication number | Publication date |
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KR20130029777A (ko) | 2013-03-25 |
US20130153347A1 (en) | 2013-06-20 |
KR101396651B1 (ko) | 2014-05-16 |
JP2012002347A (ja) | 2012-01-05 |
EP2573421A4 (en) | 2017-12-13 |
EP2573421B1 (en) | 2020-11-25 |
JP5613502B2 (ja) | 2014-10-22 |
MY158878A (en) | 2016-11-30 |
CN102893050B (zh) | 2015-11-25 |
EP2573421A1 (en) | 2013-03-27 |
ES2851011T3 (es) | 2021-09-02 |
HK1180027A1 (en) | 2013-10-11 |
MX2012013417A (es) | 2013-05-09 |
CN102893050A (zh) | 2013-01-23 |
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