WO2022234731A1 - ロータリダンパおよびブレーキシステム - Google Patents
ロータリダンパおよびブレーキシステム Download PDFInfo
- Publication number
- WO2022234731A1 WO2022234731A1 PCT/JP2022/012934 JP2022012934W WO2022234731A1 WO 2022234731 A1 WO2022234731 A1 WO 2022234731A1 JP 2022012934 W JP2022012934 W JP 2022012934W WO 2022234731 A1 WO2022234731 A1 WO 2022234731A1
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- WIPO (PCT)
- Prior art keywords
- rotor
- rotary damper
- case
- arm
- pedal
- Prior art date
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- 229920005992 thermoplastic resin Polymers 0.000 claims abstract description 10
- 238000005192 partition Methods 0.000 claims description 59
- 239000012530 fluid Substances 0.000 claims description 29
- 230000002093 peripheral effect Effects 0.000 claims description 27
- 239000003566 sealing material Substances 0.000 claims description 14
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 230000000149 penetrating effect Effects 0.000 claims description 2
- 238000000638 solvent extraction Methods 0.000 claims 1
- 238000007789 sealing Methods 0.000 description 15
- 230000005489 elastic deformation Effects 0.000 description 6
- 239000004033 plastic Substances 0.000 description 6
- 230000000881 depressing effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 239000004952 Polyamide Substances 0.000 description 3
- 239000012141 concentrate Substances 0.000 description 3
- 230000007257 malfunction Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 229920002647 polyamide Polymers 0.000 description 3
- 229920005989 resin Polymers 0.000 description 3
- 239000011347 resin Substances 0.000 description 3
- 229930182556 Polyacetal Natural products 0.000 description 2
- 238000005452 bending Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 229920006324 polyoxymethylene Polymers 0.000 description 2
- 244000043261 Hevea brasiliensis Species 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 229920003052 natural elastomer Polymers 0.000 description 1
- 229920001194 natural rubber Polymers 0.000 description 1
- 229920006122 polyamide resin Polymers 0.000 description 1
- 229920001296 polysiloxane Polymers 0.000 description 1
- 229920003051 synthetic elastomer Polymers 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 239000005061 synthetic rubber Substances 0.000 description 1
Images
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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
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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
- F16J15/54—Other sealings for rotating shafts
- F16J15/545—Other sealings for rotating shafts submitted to unbalanced pressure in circumference; seals for oscillating actuator
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T7/00—Brake-action initiating means
- B60T7/02—Brake-action initiating means for personal initiation
- B60T7/04—Brake-action initiating means for personal initiation foot actuated
- B60T7/06—Disposition of pedal
-
- 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
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
- G05G1/00—Controlling members, e.g. knobs or handles; Assemblies or arrangements thereof; Indicating position of controlling members
- G05G1/30—Controlling members actuated by foot
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/81—Braking systems
Definitions
- the present invention relates to a rotary damper, and more particularly to a rotary damper suitable for use as a brake pedal damper.
- Patent Literature 1 discloses a rotary damper that has a simple structure and can be manufactured at low cost.
- the rotary damper disclosed in Patent Document 1 includes a case having a cylindrical chamber, a rotor rotatably accommodated in the cylindrical chamber, a viscous fluid filled in the cylindrical chamber, and a cylindrical body attached to the end surface of the case on the opening side. and a lid that encloses the rotor with the viscous fluid in the chamber.
- the rotor has a cylindrical rotor body and vanes that protrude radially outward from the outer peripheral surface of the rotor body so as to form a small gap with respect to the side wall surface of the cylindrical chamber.
- the vanes are formed with flow passages extending from one side surface (referred to as the first side surface) to the other side surface (referred to as the second side surface) along the rotational direction of the rotor.
- a sealing member is attached to the tip end surface of the vane (the surface facing the side wall surface of the cylindrical chamber) to fill a small gap with the side wall surface of the cylindrical chamber.
- This sealing member has an elastic check valve that opens and closes the flow path formed in the vane.
- a partition portion protruding radially inward is formed on the side wall surface of the cylindrical chamber so as to form a slight gap with the outer peripheral surface of the rotor body.
- the rotary damper described in Patent Document 1 causes the rotor to rotate from the first side surface of the vane to the second side surface (forward rotation direction).
- the fluid pushes the check valve against the second side of the vane, blocking the flow path with the check valve.
- the movement of the viscous fluid is restricted by the gap between the partition of the cylindrical chamber and the outer peripheral surface of the rotor body, and the gap between the closed-side end surface (bottom surface) of the case and the lower surface of the vane (surface facing the closed-side end surface of the case).
- the pressure on the viscous fluid on the second side of the vane increases and strong braking torque is generated.
- the rotary damper described in Patent Document 1 can be used as an automobile brake pedal damper by interlocking with the brake pedal so as to generate a strong braking torque when the automobile driver steps on the brake pedal.
- the present invention has been made in view of the above circumstances, and its object is to provide a rotary damper suitable as a brake pedal damper having a fail-safe function and a brake system using this rotary damper.
- the present invention provides a rotary damper for a brake pedal of an automobile, which generates braking torque when the case rotates in the forward direction with respect to the rotor, in which the case is made of a thermoplastic resin,
- the case is provided with a pair of radially outwardly protruding arms that sandwich a plate that rotates about the center of rotation of the pedal in conjunction with the brake pedal.
- a curved portion having a constant width is provided in the arm portion located downstream in the normal rotation direction of the pair of arm portions, and the plate is supported on the distal end side of the curved portion of the arm portion.
- the rotary damper of the present invention is A rotary damper for a brake pedal of an automobile, comprising a rotor and a case that accommodates the rotor in a relatively rotatable manner, and that generates braking torque when the case rotates in a normal direction with respect to the rotor.
- Said case is It is made of thermoplastic resin, having a pair of radially outwardly protruding arms sandwiching a plate that rotates around the pedal rotation center in conjunction with the brake pedal; Of the pair of arm portions, the arm portion located on the downstream side in the forward rotation direction is a curved portion of constant width; and a support portion located on the distal end side of the curved portion and supporting the plate.
- the braking system of the present invention is A braking system comprising the rotary damper described above, a shaft arranged at the center of rotation of the pedal; a brake arm rotatably mounted on the shaft and coupled to a brake master cylinder; a brake pedal attached to the tip of the brake arm; a plate attached to the brake arm so as to rotate around the pedal rotation center in conjunction with the brake pedal;
- the rotary damper is The rotor is fixed to the shaft, and rotation of the rotor about the pedal rotation center is constrained, When the brake pedal is stepped on and the plate rotates about the pedal rotation center in the forward direction, the plate is moved to the arm portion of the pair of arm portions located downstream in the forward direction.
- the plate When the brake pedal is released from depression and the plate rotates about the pedal rotation center in the reverse direction, the plate is moved upstream of the pair of arms in the normal rotation direction. It is attached so that it is supported by the arm part located on the side, The plate is It is sandwiched and held between the pair of arm portions so as not to interfere with the root portion between the pair of arm portions.
- the rotary damper is installed so that the plate presses the arm located downstream in the forward rotation direction in conjunction with depression of the brake pedal, thereby generating braking torque in response to depression of the brake pedal. be able to.
- the case is made of a thermoplastic resin and a curved portion is provided in the arm portion positioned downstream in the normal rotation direction, the plate is supported on the distal end side of the curved portion of the arm portion. The stress generated in this arm portion due to is concentrated on the curved portion. Therefore, even if the rotary damper malfunctions and the relative rotation between the case and the rotor is prevented, the brake can be applied by depressing the brake pedal to damage the curved portion.
- the width of the curved portion is constant, variations in the pressing force of the brake pedal required to break the curved portion due to variations in the pressing direction of the plate applied to the distal end side of the curved portion of the arm are minimized. can do.
- FIGS. 3(A) and 3(B) are enlarged views of A portion and B portion of the rotary damper 1 shown in FIG. 2(A).
- 4A is an enlarged view of the C portion of the rotary damper 1 shown in FIG. 2A
- FIG. 4B is an enlarged view of the D portion of the rotary damper 1 shown in FIG.
- FIG. 5(A) is a front view of the case 11
- FIG. 5(B) is a CC cross-sectional view of the case 11 shown in FIG. 5(A)
- FIG. FIG. 5D is an enlarged view of part E of the case 11 shown in FIG. 5A
- FIG. 5E is a DD cross section of the case 11 shown in FIG. 5A
- 5(F) is an enlarged view of the EE section of the case 11 shown in FIG. 5(A).
- 6(A) and 6(B) are a front view and a side view of the rotor 12
- FIG. 6(C) is a cross-sectional view of the rotor 12 taken along line FF of FIG. 6(A).
- FIG. 10(A) to 10(D) are a front view, a top view, a bottom view, and a side view of the axial force generating member 17, and FIG. 10(E) is the axial force shown in FIG. 10(C).
- 10(F) is an enlarged sectional view along JJ of the generating member 17, and
- FIG. 10(F) is an enlarged sectional view along KK of the axial force generating member 17 shown in FIG. 10(D).
- FIG. 11A shows the axial force generating member 17 attached to the protrusion 18 of the partition 115 of the case 11 in the rotary damper 1 according to the embodiment of the present invention, viewed from the center of the rotary damper 1.
- FIG. 11(B) is an enlarged cross-sectional view of the axial force generating member 17 shown in FIG. 11(A) taken along line LL.
- 12(A) and 12(B) are diagrams showing an example of an automotive brake system to which a rotary damper 1 according to an embodiment of the invention is applied.
- FIGS. 13(A) and 13(B) are diagrams showing an operation example when a problem occurs in the rotary damper 1 in the brake system of the automobile shown in FIG. 12.
- FIG. FIG. 14 is a diagram for explaining the positional relationship between the rotary damper 1 and the plate 5 of the brake pedal 4. As shown in FIG.
- FIG. 1(A) to 1(C) are a front view, a side view, and a rear view of a rotary damper 1 according to one embodiment of the present invention.
- 2(A) is a sectional view taken along the line AA of the rotary damper 1 shown in FIG. 1(A)
- FIG. 2(B) is a sectional view taken along the line BB of the rotary damper 1 shown in FIG. 1(B).
- It is a diagram. 3(A) and 3(B) are enlarged views of part A and part B of the rotary damper 1 shown in FIG. 2(A)
- FIG. 4(B) is an enlarged view of the D portion of the rotary damper 1 shown in FIG. 2(B).
- the rotary damper 1 includes a case 11, a rotor 12 accommodated in the case 11 so as to be relatively rotatable with respect to the case 11, and oil filled in the case 11. , silicone or other viscous fluid (not shown), a lid 15 for enclosing the rotor 12 together with the viscous fluid in the case 11, and a pair of axial force generating members 17.
- This rotary damper 1 is a damper for a brake pedal of an automobile. When the case 11 rotates in the forward rotation direction N relative to the rotor 12, a strong braking torque is generated. When it rotates relatively in the reverse direction R, a weak braking torque is generated (see FIGS. 1(C) and 2(B)).
- FIG. 5(A) is a front view of the case 11
- FIG. 5(B) is a CC cross-sectional view of the case 11 shown in FIG. 5(A)
- FIG. FIG. 5D is an enlarged view of part E of the case 11 shown in FIG. 5A
- FIG. 5E is a DD cross section of the case 11 shown in FIG. 5A
- 5(F) is an enlarged view of the EE section of the case 11 shown in FIG. 5(A).
- the case 11 is made of a thermoplastic resin such as polyacetal.
- An opening 113 for inserting the rotor 12 is formed in the bottom portion 112 .
- the rotor 12 is arranged such that the rotation shaft 120 of the rotor 12 is aligned with the center line 110 of the cylindrical chamber 111 by inserting the lower end 123a (see FIG. 6) of the rotor body 121, which will be described later, into the opening 113. It is accommodated in the cylindrical chamber 111 (see FIG. 2(A)). Further, a side wall surface 114 of the cylindrical chamber 111 protrudes radially inward, and a tip end surface 116 is adjacent to an outer peripheral surface 124 (see FIG. 6) of a rotor body 121 (described later) of the rotor 12 to partition the cylindrical chamber 111 .
- a pair of partitions 115 are formed axially symmetrically with respect to the center line 110 of the cylindrical chamber 111 .
- a groove 181 for inserting an adjusting portion 174 (described later) of the axial force generating member 17 is formed in the upper surface 180 of the convex portion 18 along the radial direction of the cylindrical chamber 111, and the groove bottom 182 is a partition portion. It is positioned closer to the lid 15 than the upper surface 119 of 115 .
- Both side surfaces 183 of the protrusion 18 along the radial direction of the case 11 are provided with grooves 184 for mounting a first pressure contact portion 175 of the axial force generating member 17 (to be described later). formed along the
- a female threaded portion 117 is formed to be screwed with a male threaded portion 152 (see FIG. 9) of the lid 15, which will be described later.
- a pair of arm portions 19a and 19b sandwiching the plate 5 that rotates around the pedal rotation center O in conjunction with the brake pedal 4 of the automobile are formed in the radial direction. It is formed to protrude outward (see FIG. 12).
- the arm portion 19a is located downstream of the arm portion 19b in the forward rotation direction N (see FIG. 2B) of the case 11 with respect to the rotor 12 in which the rotary damper 1 generates strong braking torque. Further, the arm portion 19 a has a curved portion 191 that curves in the rotational direction N, a support portion 192 and a connecting portion 193 .
- the curved portion 191 has a radial cross section of the same shape throughout the curved portion 191 with respect to the center of curvature C of the curved portion 191 (see FIG. 5F), and has a constant radial width W. (See FIG. 5(C)).
- the support portion 192 is located on the distal end side of the curved portion 191 and supports the plate 5 rotating in the forward rotation direction N around the pedal rotation center O in conjunction with the brake pedal 4 (see FIG. 12). It has a support surface 195 that contacts and supports the plate 5 .
- a straight line passing through an end portion 197 on the side of the support portion 192 on the inner peripheral surface 196 of the curved portion 191 and an end portion 201 on the side of the curved portion 191 of the support surface 195 forms an angle ⁇ with the support surface 195 (see FIG.
- the angle ⁇ to be formed is preferably 30 degrees to 60 degrees.
- the connecting portion 193 extends radially outward from the outer peripheral surface 190 of the case 11 and connects with the curved portion 191 .
- the arm portion 19b is located upstream of the arm portion 19a in the forward rotation direction N (see FIG. 2B) of the case 11 with respect to the rotor 12 in which the rotary damper 1 generates strong braking torque. Further, the arm portion 19b is formed with a flat surface 194 that faces the arm portion 19a and extends radially outward from the outer peripheral surface 190 of the case 11 . The flat surface 194 supports the plate 5 that rotates in the reverse direction R around the pedal rotation center O in conjunction with the brake pedal 4 .
- FIG. 6(A) and 6(B) are a front view and a side view of the rotor 12, and FIG. 6(C) is a cross-sectional view of the rotor 12 taken along line FF of FIG. 6(A).
- the rotor 12 is formed of a thermoplastic resin such as polyamide resin, and as shown in the figure, has a cylindrical rotor body 121 and a pair of vanes (rotating blades) formed axially symmetrically with respect to the rotating shaft 120 of the rotor 12. 122 and .
- the vane 122 is formed along the rotating shaft 120 of the rotor 12, protrudes radially outward from the outer peripheral surface 124 of the rotor body 121, and has a tip surface 125 close to the side wall surface 114 of the cylindrical chamber 111 of the case 11. It partitions the cylindrical chamber 111 .
- a flow path 126 is formed in the vane 122 so as to extend between both side surfaces 127 a and 127 b of the vane 122 along the direction of rotation of the rotor 12 . Further, the pair of vanes 122 are respectively attached with the second seal members 14 described later (see FIG. 4(B)).
- a through hole 128 with two chamfers for inserting a two chamfer shaft (not shown) that transmits rotational force from the outside to the rotor 12 is formed around the rotation shaft 120. It is The lower end 123a of the rotor body 121 is rotatably inserted into the opening 113 formed in the bottom 112 of the cylindrical chamber 111 of the case 11 (see FIG. 4A), and the upper end 123b of the rotor body 121 is , is rotatably inserted into an opening 150 (see FIG. 9) of the lid 15 (see FIGS. 3A and 3B).
- a sealing material such as an O-ring 16a is interposed between the lower end 123a of the rotor body 121 and the opening 113 of the cylindrical chamber 111. (See FIG. 4A).
- FIG. 7(A) and 7(B) are a front view and a side view of the first sealing member 13, and FIG. 7(C) is a line GG of the first sealing member 13 shown in FIG. 7(A). It is a sectional view.
- the first sealing member 13 has a U-shape that can be attached to the partition portion 115 formed in the cylindrical chamber 111 of the case 11 , and the bottom portion 130 and the tip end surface 116 of the partition portion 115 .
- the clearance between them is closed (see FIG. 4B). Since the first seal member 13 is disposed between the relatively rotating case 11 and rotor 12, it is preferable to use a resin such as polyamide having excellent slidability as the material thereof.
- FIG. 8(A) and 8(B) are a front view and a side view of the second sealing material 14, and FIG. 8(C) is a line HH of the second sealing material 14 shown in FIG. 8(A). It is a sectional view.
- the second seal member 14 has a U-shape that can be attached to the vanes 122 of the rotor 12, and has a width wider than the width t1 (see FIG. 6A) of the vanes 122 in the rotational direction. t2 and a width t4 that is wider than the radial width t3 (see FIG. 6B) of the flow path 126 that is formed integrally with one end 141 of the bottom 140 and formed in the vane 122. and a second leg 144 formed integrally with the other end 142 of the bottom 140 and having a width t5 narrower than the radial width t3 of the flow path 126 formed in the vane 122. , have
- the second sealing member 14 attached to the vane 122 closes the gap by interposing the bottom portion 140 between the tip surface 125 of the vane 122 and the side wall surface 114 of the cylindrical chamber 111 of the case 11 (FIG. 4). (B)). 2B, when the case 11 rotates in the forward rotation direction N relative to the rotor 12, the vane 122 and the partition located downstream of the vane 122 in the forward rotation direction N are rotated. The pressure on the viscous fluid in the region 111a (see FIG.
- FIG. 9A to 9C are a front view, a side view, and a rear view of the lid 15, and FIG. 9D is a cross-sectional view of the lid 15 shown in FIG. 9A along II. is.
- the lid 15 has an opening 150 for inserting the upper end 123b of the rotor body 121 of the rotor 12 at a position facing the opening 113 formed in the bottom 112 of the cylindrical chamber 111 of the case 11. is formed. Further, an outer peripheral surface 151 of the lid 15 is formed with a male screw portion 152 that is screwed with a female screw portion 117 formed on the opening side 118 of the side wall surface 114 of the cylindrical chamber 111 . In addition, the lower surface (back surface) 153 of the lid 15 forms a gap G1 between the upper surface 129 of the vane 122 of the rotor 12 and the gap G1 that functions as a flow path for the viscous fluid filled in the cylindrical chamber 111 (FIG. 3B).
- the gap G1 functioning as a flow path for these viscous fluids can be adjusted by adjusting the amount of screwing of the lid 15 into the case 11 (the amount of screwing between the male threaded portion 152 of the lid 15 and the female threaded portion 117 of the case 11). Adjustable.
- a sealing material such as an O-ring 16b is interposed between the upper end 123b of the rotor body 121 of the rotor 12 and the opening 150 of the lid 15 so that the viscous fluid does not leak outside from the opening 150 of the lid 15.
- a sealing material such as an O-ring 16c is attached to the lid 15 so that the viscous fluid does not leak outside from the threaded portion between the male threaded portion 152 of the lid 15 and the female threaded portion 117 of the cylindrical chamber 111 of the case 11. It may be interposed between the outer peripheral surface 151 and the side wall surface 114 of the cylindrical chamber 111 (see FIGS. 3A and 3B).
- FIG. 10(A) to 10(D) are a front view, a top view, a bottom view, and a side view of the axial force generating member 17, and FIG. 10(E) is the axial force shown in FIG. 10(C).
- 10(F) is an enlarged sectional view along JJ of the generating member 17, and FIG. 10(F) is an enlarged sectional view along KK of the axial force generating member 17 shown in FIG. 10(D).
- FIG. 11A is an enlarged view of the axial force generating member 17 attached to the convex portion 18 of the partition portion 115 of the case 11 in the rotary damper 1 according to the present embodiment, as viewed from the center of the rotary damper 1. 5A), and FIG. 11B is an enlarged cross-sectional view of the axial force generating member 17 taken along line LL shown in FIG. 11A.
- the axial force generating member 17 is made of a thermoplastic resin such as polyacetal, a plastically deformable member such as sintered metal, or an elastically deformable member such as natural rubber, synthetic rubber, or synthetic resin elastomer. are mounted on the convex portions 18 formed on the upper surfaces 119 of the pair of partition portions 115, respectively, and are interposed between the upper surface 119 of the partition portion 115 and the back surface 153 of the lid 15, and the back surface 153 of the lid 15 and the partition portion 115 The gap with the upper surface 119 of the lid 15 is closed and an axial force is generated against screwing of the lid 15 into the case 11 .
- a thermoplastic resin such as polyacetal
- a plastically deformable member such as sintered metal
- an elastically deformable member such as natural rubber, synthetic rubber, or synthetic resin elastomer
- the axial force generating member 17 is formed on a rectangular body portion 170 having an upper surface 171 that contacts the back surface 153 of the lid 15 and a lower surface 172 of the main body portion 170 .
- Each of the pair of arm portions 173 has a first pressure contact portion 175 that is in pressure contact with grooves 184 formed on both side surfaces 183 of the convex portion 18 .
- the first press-contact portion 175 functions, together with grooves 184 formed on both side surfaces 183 of the convex portion 18 , as positioning when the axial force generating member 17 is attached to the convex portion 18 .
- the pair of arm portions 173 strongly grip the axial force generating member 17 by the first pressure contact portion 175 so that the axial force generating member 17 does not drop off from the convex portion 18 .
- the pair of arm portions 173 has a length L2 of the adjusting portion 174 and a length L3 from the upper surface 119 of the partition portion 115 to the groove bottom 182 of the groove 181 of the convex portion 18 formed on the upper surface 119 (FIG. 5(E)). )) and L4 ( ⁇ L2+L3).
- the adjustment portion 174 has a length L2 (>L1) that is longer than the depth L1 (see FIG. 5E) of the groove 181 of the protrusion 18 formed on the upper surface 119 of the partition portion 115, and its tip portion 176 is formed narrower in the thickness direction than the root portion 177 thereof.
- the groove 181 of the convex portion 18 has a size that allows plastic deformation or elastic deformation of the tip portion 176 of the adjustment portion 174 .
- the root portion 177 of the adjustment portion 174 has second pressure contact portions 178 on both side surfaces 179 in the thickness direction, which are in pressure contact with both side walls 185 of the groove 181 of the convex portion 18 .
- the adjustment portion 174 fits into the groove 181 of the convex portion 18 by the second pressure contact portion 178 , thereby more reliably preventing the axial force generating member 17 from coming off the convex portion 18 .
- the pair of arm portions 173 has a length L4 shorter than the sum of the length L2 of the adjustment portion 174 and the length L3 from the upper surface 119 of the partition portion 115 to the groove bottom 182 of the groove 181 of the projection 18, Since the adjusting portion 174 has a length L2 longer than the depth L1 of the groove 181 of the convex portion 18, the tip portion of the adjusting portion 174 can be adjusted without bringing the pair of arm portions 173 into contact with the upper surface 119 of the partition portion 115. 176 can be brought into contact with the groove bottom 182 of the groove 181 of the projection 18 .
- the groove 181 of the protrusion 18 has a size that allows plastic deformation or elastic deformation of the tip portion 176 of the adjustment portion 174, an axial force is generated when the lid 15 is screwed into the case 11.
- the active plastic deformation or elastic deformation of the tip portion 176 of the adjusting portion 174 causes the gap G1 between the rear surface 153 of the lid 15 and the upper surface 129 of the vane 122 to be reduced.
- the adjustment margin can be increased.
- the second seal member 14 moves in the forward rotation direction N side.
- the first leg portion 143 of the second seal member 14 contacts one side surface 127 a of the vane 122 to block the flow path 126 formed in the vane 122 .
- the gap between the tip end surface 116 of the partition portion 115 and the outer peripheral surface 124 of the rotor main body 121 of the rotor 12 is closed by the first seal member 13 attached to the partition portion 115 of the cylindrical chamber 111 of the case 11.
- the gap between the tip surface 125 of the vane 122 and the side wall surface 114 of the cylindrical chamber 111 of the case 11 is closed by the second seal member 14 attached to the vane 122 of the rotor 12 (FIG. 4B). reference). Therefore, the movement of the viscous fluid filled in the cylindrical chamber 111 is restricted only through the gap G1 between the rear surface 153 of the lid 15 and the upper surface 129 of the vane 122, and the vanes 122 and 122 rotate in the normal direction.
- the pressure of the viscous fluid in the region 111a (see FIG. 2B) separated by the partition 115 located downstream of N increases. Therefore, strong braking torque is generated.
- the gap G1 between the rear surface 153 of the lid 15 and the upper surface 129 of the vane 122 is the amount of screwing of the lid 15 into the case 11 (the amount of screwing between the male threaded portion 152 of the lid 15 and the female threaded portion 117 of the case 11). ) can be adjusted. Therefore, by adjusting the movement amount of the viscous fluid that moves through the gap G1, the braking torque generated by the rotation can be adjusted.
- an axial force generating member 17 that imparts a reaction force to the lid 15 between the rear surface 153 of the lid 15 and the upper surface 119 of the partition portion 115 , the screwing of the lid 15 into the case 11 is prevented by placing the axial force generating member 17 therebetween.
- a braking torque is adjusted by increasing the adjustment margin of the gap G1 while generating a force to prevent the viscous fluid from leaking from the threaded portion between the male threaded portion 152 of the lid 15 and the female threaded portion 117 of the case 11. The range can be widened.
- 12(A) and 12(B) are diagrams showing an example of an automobile brake system to which the rotary damper 1 according to the present embodiment is applied.
- This brake system includes a shaft 2 arranged at the pedal rotation center O, a brake arm 3 rotatably attached to the shaft 2 and connected to a brake master cylinder 6, and a brake attached to the tip of the brake arm 3.
- a plate 5 is attached to the brake arm 3 so as to rotate around the pedal rotation center O in conjunction with the pedal 4 and the brake pedal 4, and is attached to the shaft 2 so that the plate 5 is sandwiched between a pair of arm portions 19a and 19b. and a rotary damper 1.
- the tip of the shaft 2 is chamfered, and this tip is inserted into the through-hole 128 of the rotor 12 of the rotary damper 1, whereby the rotor 12 is fixed to the shaft 2.
- Rotation around the pedal rotation center O is constrained.
- the rotary damper 1 supports the plate 5 on the support surface 195 of the support portion 192 of the arm portion 19a.
- the plate 5 is supported by the flat surface 194 of the arm portion 19b.
- the plate 5 is arranged so as not to interfere with the root portion 199 (see FIG. 12A) between the pair of arm portions 19a and 19b. 194 and held by a pair of arm portions 19a and 19b.
- the brake pedal 4 can be strongly pressed as shown in FIGS.
- the curved portion 191 is deformed and possibly broken, releasing the plate 5 from the support of the arm portion 19a, compressing the brake master cylinder 6, and applying the brake.
- the curved portion 191 is deformed toward the space D (see FIG. 13A) secured between the curved portion 191 and the case 11 by the connecting portion 193 . It can be transformed without interference. Also, the curved portion 191 does not hinder the movement of the brake pedal 4 even after being damaged.
- the distance from the center (pedal rotation center) O of the rotary damper 1 to the plate 5 is r1
- the outer circumference of the curved portion 191 at the support portion 192 side end portion 197 from the center O of the rotary damper 1 is
- the distance from the center O of the rotary damper 1 to the outermost peripheral portion of the root portion 199 (the outermost peripheral portion of the connecting portion 193) 200 between the pair of arm portions 19a and 19b is r3.
- the arm portion 19a becomes longer and the rotary damper 1 becomes larger.
- the installation space of the rotary damper 1 on the brake pedal 4 is limited, and the enlargement of the rotary damper 1 makes it difficult to attach it to the brake pedal 4 .
- the plate 5 contacts not only the support surface 195 but also the base portion 199, and when the arm portion 19a is pressed against the plate 5, the stress generated in the arm portion 19a by the force is reduced by the bending portion 191. It becomes difficult to concentrate on
- the rotary damper 1 is installed so that the plate 5 presses the arm portion 19a positioned on the downstream side in the forward rotation direction N in conjunction with the depression of the brake pedal 4, thereby reducing the depression of the brake pedal 4. can generate a strong braking torque against
- the case 11 is made of a thermoplastic resin
- the arm portion 19a located on the downstream side in the forward rotation direction N is provided with a curved portion 191. Since the plate 5 rotating in the forward rotation direction N is supported by the support portion 192 located on the tip side of the arm portion 19a, the stress generated in the arm portion 19a by the rotation torque in the forward rotation direction N transmitted from the plate 5 to the arm portion 19a. concentrates on the curved portion 191 . Therefore, even if the rotary damper 1 malfunctions and prevents the case 11 from rotating in the forward rotation direction N with respect to the rotor 12, the curved portion 191 is damaged by strongly depressing the brake pedal 4, causing the plate 5 to move. is released from the support of the arm portion 19a, the brake master cylinder 6 is compressed, and the brake can be applied.
- the curved portion 191 has the same radial cross section over the entire curved portion 191 with respect to the center of curvature C of the curved portion 191 (see FIG. 5F), and the width W in the radial direction is constant. Therefore (see FIG. 5C), it is possible to reduce variations in the brake pedal stepping force required to break the curved portion 191 due to variations in the pressing direction of the plate 5 applied to the support portion 192 .
- the rotary damper 1 suitable as a brake pedal damper having a fail-safe function.
- the arm portion 19 a has a connecting portion 193 that extends radially outward from the outer peripheral surface 190 of the case 11 and connects with the curved portion 191 .
- the connecting portion 193 secures a space in which the bending portion 191 bends in the forward rotation direction N side. Therefore, even if a problem occurs in the rotary damper 1 and the rotation of the case 11 with respect to the rotor 12 in the forward rotation direction N is prevented, by strongly depressing the brake pedal 4, the curved portion 191 moves in the forward rotation direction N side.
- the brake pedal 4 bends and moves in the normal rotation direction N side, so that a brake feel with little sense of discomfort can be realized.
- the lid 15 is screwed into the case 11.
- the gap G1 between the rear surface 153 of the lid 15 and the upper surface 129 of the vane 122 can be adjusted by adjusting the amount of screwing of the lid 15 into the case 11 . Therefore, it is possible to adjust the amount of movement of the viscous fluid that moves through the gap G1 and adjust the braking torque generated by the rotation with a simple configuration and simple work without increasing the number of parts.
- an axial force is formed between the rear surface 153 of the lid 15 and the upper surface 119 of the partition portion 115 by a member that is plastically or elastically deformable, and generates an axial force that imparts a reaction force to the lid 15 .
- a member that is plastically or elastically deformable
- an axial force is generated against screwing of the lid 15 into the case 11, and the viscous fluid leaks from the threaded portion between the male threaded portion 152 of the lid 15 and the female threaded portion 117 of the case 11. It is possible to widen the adjustment range of the braking torque by enlarging the adjustment margin of the gap G1 while preventing this.
- the convex portion 18 is provided on the upper surface 119 of the partition portion 115 , and a pair of arm portions 173 are provided on the axial force generating member 17 to sandwich and hold the convex portion 18 . Therefore, the axial force generating member 17 can be easily attached to the partition portion 115 .
- the axial force generating member 17 is arranged between the pair of arm portions 173 , protrudes toward the convex portion 18 provided on the upper surface 119 of the partition portion 115 , and extends into the groove 181 of the convex portion 18 .
- An adjusting portion 174 is provided to be inserted and abutted against the groove bottom 182 of the groove 181 , and the groove 181 of the convex portion 18 is sized to allow plastic deformation or elastic deformation of the tip portion 176 of the adjusting portion 174 . Therefore, when the lid 15 is screwed into the case 11, the tip 176 of the adjusting portion 174 presses the groove bottom 182 of the groove 181 and is actively plastically or elastically deformed. can be made even larger.
- the pair of arm portions 173 of the axial force generating member 17 are in pressure contact with the grooves 184 formed on both side surfaces 183 of the convex portion 18 formed on the upper surface 119 of the partition portion 115 respectively.
- 1 pressure contact portion 175 is provided.
- the first pressure contact portion 175 allows the pair of arm portions 173 to strongly grip the axial force generating member 17 so that the axial force generating member 17 does not drop off from the convex portion 18 .
- the first pressure contact portion 175 functions together with grooves 184 formed on both side surfaces 183 of the convex portion 18 to position the axial force generating member 17 when the axial force generating member 17 is mounted on the convex portion 18. It can be correctly attached to the convex portion 18 .
- the adjusting portion 174 of the axial force generating member 17 has second pressure contact portions 178 on both side surfaces 179 of the root portion 177 that are in pressure contact with the side walls 185 of the groove 181 of the convex portion 18 .
- the adjustment portion 174 fits into the groove 181 of the convex portion 18 by the second pressure contact portion 178 , and can more reliably prevent the axial force generating member 17 from coming off the convex portion 18 .
- the first sealing member 13 and the second sealing member 14 are Since it functions as a sliding bearing that slidably supports the outer peripheral surface 124 of the rotor body 121 of the rotor 12, it absorbs rattling due to eccentricity of the shaft 2 that transmits the rotational force from the outside to the rotor 12, and the shaft 2 is supported. It can rotate smoothly.
- the gap G1 between the rear surface 153 of the lid 15 and the upper surface 129 of the vane 122 is used as a viscous fluid flow path other than the flow path 126 formed in the vane 122 has been described as an example. .
- the invention is not so limited.
- the flow path of the viscous fluid other than the flow path 126 formed in the vane 122 is In addition to the gap G1 between the rear surface 153 of the lid 15 and the upper surface 129 of the vane 122, the gap between the rear surface 153 of the lid 15 and the upper surface 119 of the partition portion 115 may be used.
- the case where the cylindrical chamber 111 is provided with the pair of partitions 115 and the rotor 12 is provided with the pair of vanes 122 has been described as an example.
- the invention is not so limited. If the number of the partitions 115 formed in the cylindrical chamber 111 and the number of the vanes 122 formed in the rotor 12 are the same, one or three or more may be formed.
- the second seal member 14 attached to the vane 122 is given the function of a check valve that opens and closes the flow path 126 formed in the vane 122.
- a check valve that opens and closes the flow path 126 formed in the vane 122.
- a check valve that opens the flow path 126 formed in the vane 122 when the vane 122 rotates in the reverse direction R may be provided separately from the second seal member 14 .
- the vanes 122 are formed with the flow paths 126 extending through the side surfaces 127a and 127b of the vanes 122 along the rotation direction of the rotor 12, but the present invention is not limited to this.
- the partitions 115 may have flow paths penetrating both side surfaces of the partitions 115 along the rotational direction of the rotor 12 .
- a check valve is provided to open the flow path formed in the partition portion 115 when it is relatively rotated in the reversal direction R.
- the first seal member 13 has the same shape as the second seal member 14, that is, a bottom portion having a width wider than the circumferential width of the outer peripheral edge of the partition portion 115 and a bottom portion Integrally formed at one end of the first leg having a width wider than the radial width of the channel formed in the partition 115, and the other end of the bottom, and a second leg portion having a width narrower than the radial width of the channel formed in the partition portion 115 .
- the first seal member 13 may function as a check valve for opening the flow path formed in the partition portion 115 by the second leg abutting the other side surface of the partition portion 115. good.
- the second sealing material 14 can close the gap between the tip surface 125 of the vane 122 and the side wall surface 114 of the cylindrical chamber 111 of the case 11. It can be of any shape.
- the first sealing member 13 is attached to the partition portion 115 provided in the cylindrical chamber 111 of the case 11, but the present invention is not limited to this.
- the first sealing material 13 may be omitted.
- the vanes 122 of the rotor 12 are fitted with the second seals 14, but the second seals 14 may also be omitted.
- the axial force generating member 17 formed of a material capable of plastic deformation or elastic deformation is arranged between the rear surface 153 of the lid 15 and the upper surface 119 of the partition portion 115, so that the lid 15 is screwed into the case 11, an axial force is generated.
- the case 11 may be made of a thermoplastic resin, and the upper surface 119 of the partition portion 115 may be formed integrally with the case 11 with a convex portion that contacts the back surface 153 of the lid 15 as an axial force generating portion.
- the axial force generating portion (convex portion) generates an axial force when the lid 15 is screwed into the case 11 , and the male screw portion 152 of the lid 15 and the female screw portion 117 of the case 11 are screwed together.
- Rotary damper 2 Shaft 3: Brake arm 4: Brake pedal 5: Plate 6: Brake master cylinder 11: Case 12: Rotor 13: First sealing material 14: Second sealing material 15: Lid 16a, 16b, 16c: O-ring 17: axial force generating member 18: convex portion 111: cylindrical chamber 19a, 19b: arm portion 112: bottom portion of cylindrical chamber 111 113: Opening of cylindrical chamber 111 114: Side wall surface of cylindrical chamber 111 115: Partition 116: Tip surface of partition 115 117: Female screw 118: Opening side of cylindrical chamber 111 119: Upper surface of partition 115 121: Rotor main body 122: Vanes 123a, 123b: Ends of rotor main body 121 124: Outer peripheral surface of rotor main body 125: Tip surfaces of vanes 122 126: Flow paths 127a, 127b: Side surfaces of vanes 122 128: Through holes of rotor main body 121 130: the bottom of the first seal
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Transportation (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Braking Elements And Transmission Devices (AREA)
- Sealing Devices (AREA)
Abstract
Description
ロータと、前記ロータを相対的に回転可能に収容するケースと、を備え、前記ケースが前記ロータに対して正転方向に回転すると制動トルクを発生させる、自動車のブレーキペダル用のロータリダンパであって、
前記ケースは、
熱可塑性樹脂で形成されており、
前記ブレーキペダルと連動してペダル回転中心回りに回転するプレートを挟む、径方向外方に突出した一対のアーム部を有し、
前記一対のアーム部のうち、前記正転方向の下流側に位置するアーム部は、
一定幅の湾曲部と、
前記湾曲部よりも先端側に位置し、前記プレートを支持する支持部と、を有する。
また、本発明のブレーキシステムは、
上述のロータリダンパを備えたブレーキシステムであって、
ペダル回転中心に配置されたシャフトと、
前記シャフトに回転可能に取り付けられるとともに、ブレーキマスタシリンダに連結されたブレーキアームと、
前記ブレーキアームの先端に取り付けられたブレーキペダルと、
前記ブレーキペダルと連動してペダル回転中心回りを回転するように前記ブレーキアームに取り付けられたプレートと、を備え、
前記ロータリダンパは、
前記ロータが前記シャフトに固定されて、当該ロータの前記ペダル回転中心回りの回転が拘束されており、
前記ブレーキペダルが踏み込まれて、前記プレートがペダル回転中心回りを正転方向に回転したときに、前記プレートを、前記一対のアーム部のうち前記正転方向の下流側に位置するアーム部の前記支持部で支持し、前記ブレーキペダルが踏み込みから解放されて、前記プレートが前記ペダル回転中心回りを反転方向に回転したときに、前記プレートを、前記一対のアーム部のうち前記正転方向の上流側に位置するアーム部で支持するように取り付けられ、
前記プレートは、
前記一対のアーム部間の根元部分と干渉しないように、前記一対のアーム部に挟み込まれて把持される。
4:ブレーキペダル 5:プレート 6:ブレーキマスタシリンダ
11:ケース 12:ロータ 13:第1シール材
14:第2シール材 15:蓋 16a、16b、16c:Oリング
17:軸力発生部材 18:凸部 111:円筒室
19a、19b:アーム部 112:円筒室111の底部
113:円筒室111の開口部 114:円筒室111の側壁面
115:仕切り部 116:仕切り部115の先端面
117:雌ネジ部 118:円筒室111の開口側
119:仕切り部115の上面 121:ロータ本体
122:ベーン 123a、123b:ロータ本体121の端部
124:ロータ本体の外周面 125:ベーン122の先端面
126:流路 127a、127b:ベーン122の側面
128:ロータ本体121の貫通穴 129:ベーン122の上面
130:第1シール材13の底部 140:第2シール材14の底部
141、142:第2シール材14の底部140の端部
143:第2シール材14の第1脚部
144:第2シール材14の第2脚部
150:蓋15の開口部 151:蓋15の外周面
152:雄ネジ部 153:蓋15の下面
170:軸力発生部材17の本体部 171:本体部170の上面
172:本体部170の下面 173:アーム部
174:調整部 175:第1圧接部
176:調整部174の先端部 177:調整部174の根元部
178:第2圧接部 179:根元部177の側面
180:凸部18の上面 181:溝 182:溝底
183:凸部18の側面 184:溝 185:溝181の側壁
190:ケース11の外周面 191:湾曲部 192:支持部
193:連結部 194:平坦面 195:支持面
196:湾曲部191の内周面
197:湾曲部191の支持部192側端部
198:湾曲部191の外周面
199:アーム部19a、19b間の根元部分
200:根元部分199の最外周部
201:支持面195の湾曲部191側端部
Claims (5)
- ロータと、前記ロータを相対的に回転可能に収容するケースと、を備え、前記ケースが前記ロータに対して正転方向に回転すると制動トルクを発生させる、自動車のブレーキペダル用のロータリダンパであって、
前記ケースは、
熱可塑性樹脂で形成されており、
前記ブレーキペダルと連動してペダル回転中心回りに回転するプレートを挟む、径方向外方に突出した一対のアーム部を有し、
前記一対のアーム部のうち、前記正転方向の下流側に位置するアーム部は、
一定幅の湾曲部と、
前記湾曲部よりも先端側に位置し、前記プレートを支持する支持部と、を有する
ことを特徴とするロータリダンパ。 - 請求項1に記載のロータリダンパであって、
前記正転方向の下流側に位置するアーム部は、
前記ケースから径方向外方に延びて、前記湾曲部と連結する連結部をさらに有する
ことを特徴とするロータリダンパ。 - 請求項1または2に記載のロータリダンパであって、
前記ケースは、
粘性流体が充填された円筒室と、
前記円筒室の側壁面から径方向内方に突出して、前記円筒室を仕切る仕切り部と、を有し、
前記ロータは、
外周面が前記仕切り部の先端面と近接する、円筒状のロータ本体と、
前記ロータ本体の外周面から径方向外方へ突出し、先端面が前記円筒室の側壁面と近接して、前記円筒室を仕切るベーンと、を有し、
前記ロータリダンパは、さらに、
前記仕切り部あるいは前記ベーンに形成され、前記ロータの回転方向に沿って前記仕切り部あるいは前記ベーンの両側面間を貫く流路と、
前記ロータが前記ケースに対して前記正転方向に回転した場合に、前記流路を塞ぎ、前記ロータが前記ケースに対して反転方向に回転した場合に、前記流路を解放する逆止弁と、を備える
ことを特徴とするロータリダンパ。 - 請求項3に記載のロータリダンパであって、
前記仕切り部の先端面と前記ロータ本体の外周面との隙間を塞ぐ第1シール材、および前記ベーンの先端面と前記円筒室の側壁面との隙間を塞ぐ第2シール材の少なくとも一方をさらに備える
ことを特徴とするロータリダンパ。 - 請求項1ないし4のいずれか一項に記載のロータリダンパを備えたブレーキシステムであって、
ペダル回転中心に配置されたシャフトと、
前記シャフトに回転可能に取り付けられるとともに、ブレーキマスタシリンダに連結されたブレーキアームと、
前記ブレーキアームの先端に取り付けられたブレーキペダルと、
前記ブレーキペダルと連動してペダル回転中心回りを回転するように前記ブレーキアームに取り付けられたプレートと、を備え、
前記ロータリダンパは、
前記ロータが前記シャフトに固定されて、当該ロータの前記ペダル回転中心回りの回転が拘束されており、
前記ブレーキペダルが踏み込まれて、前記プレートがペダル回転中心回りを正転方向に回転したときに、前記プレートを、前記一対のアーム部のうち前記正転方向の下流側に位置するアーム部の前記支持部で支持し、前記ブレーキペダルが踏み込みから解放されて、前記プレートが前記ペダル回転中心回りを反転方向に回転したときに、前記プレートを、前記一対のアーム部のうち前記正転方向の上流側に位置するアーム部で支持するように取り付けられ、
前記プレートは、
前記一対のアーム部間の根元部分と干渉しないように、前記一対のアーム部に挟み込まれて把持される
ことを特徴とするブレーキシステム。
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KR1020237040003A KR20240004571A (ko) | 2021-05-06 | 2022-03-21 | 로터리 댐퍼 및 브레이크 시스템 |
EP22798838.3A EP4336303A1 (en) | 2021-05-06 | 2022-03-21 | Rotary damper, and brake system |
CN202280032822.0A CN117242278A (zh) | 2021-05-06 | 2022-03-21 | 旋转阻尼器以及制动系统 |
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JP2021-078848 | 2021-05-06 | ||
JP2021078848A JP2022172724A (ja) | 2021-05-06 | 2021-05-06 | ロータリダンパおよびブレーキシステム |
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WO2022234731A1 true WO2022234731A1 (ja) | 2022-11-10 |
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EP (1) | EP4336303A1 (ja) |
JP (1) | JP2022172724A (ja) |
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WO (1) | WO2022234731A1 (ja) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07301272A (ja) | 1994-04-28 | 1995-11-14 | Hitachi Powdered Metals Co Ltd | 流体圧ダンパ |
JPH08290760A (ja) * | 1995-02-24 | 1996-11-05 | Oiles Ind Co Ltd | 足踏みパーキングブレーキ用ダンパ |
JP2008162324A (ja) * | 2006-12-27 | 2008-07-17 | Otsuka Koki Co Ltd | マニュアルブレーキ装置の張力調整機構 |
WO2013145973A1 (ja) * | 2012-03-27 | 2013-10-03 | オイレス工業株式会社 | ダンパおよび操作ユニット |
JP2016023652A (ja) * | 2014-07-16 | 2016-02-08 | オイレス工業株式会社 | ダンパ |
-
2021
- 2021-05-06 JP JP2021078848A patent/JP2022172724A/ja active Pending
-
2022
- 2022-03-21 CN CN202280032822.0A patent/CN117242278A/zh active Pending
- 2022-03-21 KR KR1020237040003A patent/KR20240004571A/ko unknown
- 2022-03-21 WO PCT/JP2022/012934 patent/WO2022234731A1/ja active Application Filing
- 2022-03-21 EP EP22798838.3A patent/EP4336303A1/en active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07301272A (ja) | 1994-04-28 | 1995-11-14 | Hitachi Powdered Metals Co Ltd | 流体圧ダンパ |
JPH08290760A (ja) * | 1995-02-24 | 1996-11-05 | Oiles Ind Co Ltd | 足踏みパーキングブレーキ用ダンパ |
JP2008162324A (ja) * | 2006-12-27 | 2008-07-17 | Otsuka Koki Co Ltd | マニュアルブレーキ装置の張力調整機構 |
WO2013145973A1 (ja) * | 2012-03-27 | 2013-10-03 | オイレス工業株式会社 | ダンパおよび操作ユニット |
JP2016023652A (ja) * | 2014-07-16 | 2016-02-08 | オイレス工業株式会社 | ダンパ |
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KR20240004571A (ko) | 2024-01-11 |
JP2022172724A (ja) | 2022-11-17 |
CN117242278A (zh) | 2023-12-15 |
EP4336303A1 (en) | 2024-03-13 |
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