WO2013035290A1 - 減衰力可変ダンパ - Google Patents
減衰力可変ダンパ Download PDFInfo
- Publication number
- WO2013035290A1 WO2013035290A1 PCT/JP2012/005522 JP2012005522W WO2013035290A1 WO 2013035290 A1 WO2013035290 A1 WO 2013035290A1 JP 2012005522 W JP2012005522 W JP 2012005522W WO 2013035290 A1 WO2013035290 A1 WO 2013035290A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve plate
- damper
- piston
- damping force
- oil passage
- 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
- 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
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3485—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of supporting elements intended to guide or limit the movement of the annular discs
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
- B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
- B60G21/051—Trailing arm twist beam axles
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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
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination
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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
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3488—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features intended to affect valve bias or pre-stress
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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
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/464—Control of valve bias or pre-stress, e.g. electromagnetically
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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
- F16F9/50—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
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
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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
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
Definitions
- the present invention relates to a solenoid-type variable damping force damper used for a suspension of an automobile, and more particularly to a technology that realizes suppression of power consumption by preventing an excessive opening of a valve plate during high-speed operation.
- a damper for an automobile suspension includes a cylindrical cylinder filled with hydraulic oil, a piston that slides in the axial direction within the cylinder, and a piston rod that is attached to the tip of the piston.
- a multi-cylinder type or a single-cylinder type cylinder that moves hydraulic oil between a plurality of oil chambers is generally used.
- a communication oil passage and a flexible valve plate are provided on the piston, and flow resistance is given to the hydraulic oil that moves between oil chambers via the communication oil passage by the valve plate. It is common to obtain a damping force. However, since such a damper has a constant damping characteristic, it is not possible to obtain riding comfort and running stability suitable for the road surface condition and the running condition. Therefore, on the upper and lower surfaces of the piston body, a contraction side and an extension side valve plate made of a magnetic material are installed, and an annular electromagnetic coil that generates a magnetic field between the outer yoke and the inner yoke constituting the piston body is interposed.
- a damping force variable damper has been proposed that changes the strength of the magnetic field by increasing or decreasing the amount of current supplied to the electromagnetic coil, thereby changing the valve opening characteristics (ie, damping force) of the valve plate steplessly. (See Patent Documents 1 and 2).
- the damping force variable dampers of Patent Documents 1 and 2 are caused by attracting the valve plate with magnetic force at the end face of the piston body, and as described below, the power consumption during the high-speed operation of the damper becomes very large. was there. That is, in the damper having the above-described structure, when a large amount of hydraulic oil passes through the communication oil passage during high-speed telescopic operation, the hydraulic pressure on the communication oil passage side (inner side) rises due to a rapid inflow of the hydraulic oil, while the piston moves away. The oil pressure on the oil chamber side (outer side) is lowered by moving to, and the valve plate opens excessively.
- the present invention has been made in view of such a background, and provides a solenoid-type variable damping force damper that realizes suppression of power consumption and the like by preventing excessive opening of a valve plate during high-speed operation. Objective.
- a cylindrical cylinder (12) filled with hydraulic oil and reciprocating in the cylinder and one oil chamber (14 or 15) in the cylinder are reciprocated.
- the other oil chamber (15 or 14) and a piston rod (13) holding the piston at the tip, and the piston is fixed to the piston rod.
- a ferromagnetic inner yoke (34) having an outer peripheral surface coaxial with the cylinder, and an inner periphery that is coaxial with the outer peripheral surface of the inner yoke and faces the outer peripheral surface with a predetermined gap.
- a ferromagnetic outer yoke (31) having a surface, an electromagnetic coil (43) fitted in the gap, and an axial direction on the other oil chamber side while communicating with the one oil chamber
- the first communication oil passage (36, 37) having an opening on the end face and the opening of the first communication oil passage are closed elastically, and are ferromagnetically attracted in the closing direction by the magnetic force of the electromagnetic coil.
- a pressure accumulating housing (46, 47) which is fixed to the valve plate (41, 42) and an axial end surface on the other oil chamber side and forms a pressure accumulating chamber (71, 72) on the opposite side of the valve plate from the opening.
- a second communication oil passage (61, 62) for communicating the pressure accumulation chamber and the other oil chamber.
- valve plate covers substantially the entire axial end surface on the other oil chamber side.
- valve plate is formed with a flow rate adjusting hole that forms a part of the second communication oil passage.
- a valve plate similar to the valve plate is provided on the one oil chamber side, and further, the first oil chamber side valve plate corresponds to the first oil chamber side valve plate.
- a predetermined gap is formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the piston, and the second communication oil passage opens into the gap.
- the pressure accumulating housing is fastened to the inner yoke by fastening parts (13, 49), and at least a part of the second communication oil passage is formed in the shaft center of the fastening part. It was done.
- the hydraulic oil pushes open the valve plate and flows into the pressure accumulating chamber from the first communication oil passage. And the hydraulic pressure in the pressure accumulating chamber are balanced, so that excessive opening of the valve plate is suppressed.
- the second communication oil passage opens into the gap, the second communication oil passage is formed without a valve plate. Therefore, the present invention can be easily applied to a single cylinder damper.
- the second communication oil passage is provided with a pressure accumulating housing that is fastened by an inner yoke fastening part to form a pressure accumulating chamber, and at least a part of the second oil passage is formed in the shaft center of the fastening part.
- the present invention can be easily applied to a single cylinder damper.
- the rear suspension 1 of the present embodiment is a so-called H-type torsion beam suspension, and the torsion beam 4 that connects the left and right trailing arms 2 and 3 and the intermediate portion between the trailing arms 2 and 3.
- the left and right rear wheels 7 and 8 are suspended from a pair of left and right coil springs 5 and a pair of left and right dampers 6 as suspension springs.
- the damper 6 is a solenoid type damping force variable damper, and the damping force is variably controlled by an ECU 9 installed in a trunk room or the like.
- the damper 6 of the present embodiment is a monotube type (de carvone type), and has a cylindrical cylinder 12 filled with hydraulic oil, and an axial slide with respect to the cylinder 12.
- a piston rod 13 that moves, and a piston 16 that is attached to the tip (lower end) of the piston rod 13 and divides the inside of the cylinder 12 into an upper liquid chamber (one liquid chamber) 14 and a lower liquid chamber (the other liquid chamber) 15.
- a free piston 18 that defines a high-pressure gas chamber 17 at the bottom of the cylinder 12, a cover 19 that prevents dust from adhering to the piston rod 13 and the like, and a bump stop 20 that performs buffering during full bouncing. It is said.
- the cylinder 12 is connected to the upper surface of the trailing arm 2 which is a wheel side member via a bolt 21 inserted into the eyepiece 12a at the lower end.
- the piston rod 13 is connected to a damper base (wheel house upper part) 24 which is a vehicle body side member through an upper and lower pair of bushes 22 and a nut 23.
- the piston 16 includes a piston body 30, an expansion side valve plate 41, a contraction side valve plate 42, an electromagnetic coil 43, a pair of upper and lower connecting members 44 and 45, an expansion side pressure accumulating housing 46, and a contraction.
- a side pressure accumulating housing 47, a piston ring 48, and a stepped hexagon socket head bolt (hereinafter simply referred to as a bolt) 49 are included.
- the piston main body 30 is an integrally molded product manufactured by a powder metallurgy method, a die casting method, or the like using a ferromagnetic material such as a philite system, and a cylinder whose outer peripheral surface faces the inner peripheral surface of the cylinder 12 with a slight gap.
- an annular connecting portion 33 that connects the two.
- the inner yoke 32 is formed with female threaded holes 34 and 35 into which the male threaded portion 13a of the piston rod 13 and the bolt 49 are screwed into the upper and lower shaft centers, respectively, and both of them extend in the axial direction through the first communication on the extension side.
- An oil passage 36 and a contraction-side first communication oil passage 37 are formed.
- the outer yoke 31 and the inner yoke 32 have communication holes 38 a and 38 b that allow communication between the upper part of the extension-side first communication oil path 36 and the outer peripheral side of the outer yoke 31, the lower part of the contraction-side first communication oil path 37, and the outer yoke 31.
- Communicating holes 39a and 39b communicating with the outer peripheral side are respectively formed.
- the piston ring 48 has an annular shape having an abutment (not shown) like the piston for the internal combustion engine, and is externally fitted in a holding groove 40 formed in the lower portion of the outer yoke 31.
- the extension side valve plate 41 is a disc-like one formed by punching a plate material made of a ferromagnetic material having elasticity, a circular valve body 53 in which a bolt hole 51 and a flow rate adjusting hole 52 are formed, and a valve body 53. , And is fastened to the lower surface of the piston main body 30 by a bolt 49 via an extension-side accumulator housing 46.
- the contraction side valve plate 42 is a disc-like one formed by punching a plate material made of a ferromagnetic material having elasticity, and has a circular shape with a bolt hole 55 and a flow rate adjustment hole 56 formed therein.
- valve body 57 has a valve body 57 and a base portion 58 that supports the valve body 57, and is fastened to the upper surface of the piston main body 30 by a piston rod 13 (male thread portion 13 a) via a compression side pressure accumulating housing 47.
- both valve plates 41 and 42 are set so that each thickness is significantly larger than the thickness of the connection part 33.
- the electromagnetic coil 43 is fitted in the gap between the outer yoke 31 and the inner yoke 32, and lead wires 43 a and 43 b are connected to a power supply line 60 wired on the axis of the piston rod 13.
- the power supply line 60 supplies power to the electromagnetic coil 43 from a damper control ECU installed in a passenger compartment of the automobile.
- the connecting members 44 and 45 are annular members made of a non-magnetic material (austenitic stainless steel or aluminum alloy).
- the connecting members 44 and 45 are inserted into the gap between the outer yoke 31 and the inner yoke 32 and are press-fitted, welded, bonded, or the like.
- the yokes 31 and 32 are fixed.
- the connecting member 45 is provided with a communication hole 45 a that forms the first radial oil passage 61 together with the communication holes 39 a and 39 b of the outer yoke 31 and the inner yoke 32.
- the connection member 44 is provided with a communication hole 44 a that forms the second radial oil passage 62 together with the communication holes 38 a and 38 b of the outer yoke 31 and the inner yoke 32.
- the expansion-side pressure accumulating housing 46 is a bottomed annular member made of a non-magnetic material similar to both the connecting members 44 and 45, and a bolt hole 70 into which a bolt 49 is fitted is formed at the center thereof.
- An expansion side pressure accumulating chamber 71 that accommodates the expansion side valve plate 41 is defined between the main body 30 and the main body 30.
- the compression-side pressure accumulation housing 47 is the same product as the expansion-side pressure accumulation housing 46, and defines a compression-side pressure accumulation chamber 72 that accommodates the compression-side valve plate 42 between the piston body 30.
- the ECU detects the vehicle body acceleration obtained from the longitudinal G sensor, the lateral G sensor, and the vertical G sensor, the vehicle body speed input from the vehicle speed sensor, and the rotational speed of each wheel obtained from the wheel speed sensor. Based on the above, a target damping force of the damper 6 is set and a drive current (excitation current) is supplied to the electromagnetic coil 43. Then, the magnetic flux formed by the electromagnetic coil 43 reaches both ends of the outer yoke 31 and the inner yoke 32, and the expansion side valve plate 41 and the contraction side valve plate 42 are magnetically attracted.
- the valve element 53 of the extension side valve plate 41 is opened by being pressed by the hydraulic oil flowing in from the extension side first communication oil passage 36. At this time, the hydraulic oil is passed through the flow rate adjusting hole 52. In combination with the circulation, the oil pressure on the upper surface side (the surface on the electromagnetic coil 43 side) and the oil pressure on the lower surface side of the valve body 53 are substantially equal in the expansion-side pressure accumulating chamber 71. Therefore, even when the damper 6 operates at a high speed toward the expansion side and the inflow speed of the hydraulic oil from the expansion side first communication oil passage 36 increases, the valve element 53 of the expansion side valve plate 41 is excessively opened. Is less likely to occur. This eliminates the need for the ECU to supply a very large current to the electromagnetic coil 43, and allows the target current to be set substantially the same regardless of the operating speed of the damper 6, thereby improving the controllability of the damping force. .
- the valve element 57 of the contraction-side valve plate 42 is opened by being pressed by the hydraulic oil flowing in from the first extension fluid passage 36. At this time, the hydraulic oil is passed through the flow rate adjusting hole 56. In combination with the circulation, the oil pressure on the lower surface side (surface on the electromagnetic coil 43 side) of the valve body 57 and the oil pressure on the upper surface side are substantially equal in the compression side pressure accumulating chamber 72. Therefore, even when the damper 6 operates at a high speed toward the contraction side and the inflow speed of the hydraulic oil from the contraction-side first communication oil passage 37 increases, the valve element 57 of the contraction-side valve plate 42 is excessively opened. Is less likely to occur.
- the ECU does not need to supply a large current to the electromagnetic coil 43, and the target current can be set to be substantially the same regardless of the operation speed of the damper 6 as in the case of the contraction side telescopic operation. Force controllability is also improved.
- the piston 16 according to the first modified example has substantially the same configuration as that of the above-described embodiment, but instead of providing the first radial oil passage, a bolt 49 is provided.
- An axial oil passage 81 is formed at the shaft center of the shaft, and a communication oil passage 82 is formed on the inner yoke 32 side to connect the contraction-side first communication oil passage 37 and the axial oil passage 81.
- the operation of the first modification is also the same as that of the embodiment except that the flow path of the hydraulic oil between the contraction-side first communication oil passage 37 and the piston-side oil chamber 15 is different.
- the piston 16 according to the second modified example has substantially the same configuration as that of the above-described embodiment, but instead of providing the second radial oil passage, the contraction side is provided.
- the valve plate 42 is provided with a communication hole 85 that communicates with the extension-side first communication oil passage 36
- the contraction-side pressure accumulation housing 47 is provided with a communication hole 86 that communicates the rod-side oil chamber 14 with the extension-side pressure accumulation chamber 71.
- the operation of the second modified example is also the same as that of the embodiment except that the flow path of the hydraulic oil between the expansion side first communication oil path 36 and the contraction side first communication oil path 37 and the rod side oil chamber 14 is different. .
- no connecting member is installed on the upper portion of the piston body 30.
- the piston 16 according to the third modified example has substantially the same configuration as that of the first modified example described above, but has a long axial length as the expansion side pressure accumulating housing 46.
- a holding groove 91 in which the piston ring 48 is fitted is formed on the outer periphery of the extension-side pressure accumulating housing 46.
- the present invention is applied to a single cylinder type variable damping force damper used for a torsion beam type rear suspension.
- the present invention can also be applied to a damping force variable damper for a front suspension, a double cylinder type damping force variable damper, and the like.
- the single plate type thing was mentioned as an expansion side valve plate or a contraction side valve plate, you may employ
- the second communication oil passage is formed in the inner yoke or the outer yoke.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
Description
<サスペンション>
図1に示すように、本実施形態のリヤサスペンション1は、いわゆるH型トーションビーム式サスペンションであり、左右のトレーリングアーム2,3や、両トレーリングアーム2,3の中間部を連結するトーションビーム4、懸架ばねである左右一対のコイルスプリング5、左右一対のダンパ6等から構成されており、左右のリヤホイール7,8を懸架している。ダンパ6は、ソレノイド式の減衰力可変型ダンパであり、トランクルーム内等に設置されたECU9によってその減衰力が可変制御される。
図2に示すように、本実施形態のダンパ6は、モノチューブ式(ド・カルボン式)であり、作動油が充填された円筒状のシリンダ12と、このシリンダ12に対して軸方向に摺動するピストンロッド13と、ピストンロッド13の先端(下端)に装着されてシリンダ12内を上部液室(一方の液室)14と下部液室(他方の液室)15とに区画するピストン16と、シリンダ12の下部に高圧ガス室17を画成するフリーピストン18と、ピストンロッド13等への塵埃の付着を防ぐカバー19と、フルバウンド時における緩衝を行うバンプストップ20とを主要構成要素としている。
図3,図4に示すように、ピストン16は、ピストン本体30、伸び側バルブプレート41、縮み側バルブプレート42、電磁コイル43、上下一対の連結部材44,45,伸び側蓄圧ハウジング46,縮み側蓄圧ハウジング47、ピストンリング48、段付きの6角穴付きボルト(以下、単にボルトと記す)49から構成されている。
自動車が走行を開始すると、ECUは、前後Gセンサや横Gセンサ、上下Gセンサから得られた車体の加速度や、車速センサから入力した車体速度、車輪速センサから得られた各車輪の回転速度等に基づき、ダンパ6の目標減衰力を設定して電磁コイル43に駆動電流(励磁電流)を供給する。すると、電磁コイル43が形成した磁束がアウタヨーク31およびインナヨーク32の両端に達し、伸び側バルブプレート41と縮み側バルブプレート42とが磁力吸引される。
ダンパ6が伸び側にテレスコピック作動すると、図5に示すように、ロッド側油室14内の作動油は、第2径方向油路62と伸び側第1連通油路36とを通過し、伸び側バルブプレート41の弁体53を開弁させて伸び側蓄圧室71に流入する。伸び側蓄圧室71に流入した作動油は、伸び側バルブプレート41とピストン本体30との間隙を通過した後、縮み側第1連通油路37の下端部分と第1径方向油路61とを経由してピストン側油室15に流入する。すなわち、本実施形態においては、ダンパ6が伸び側にテレスコピック作動すると、縮み側第1連通油路37の下端部分と第1径方向油路61とが伸び側第2連通油路として機能する。
ダンパ6が縮み側にテレスコピック作動すると、図6に示すように、ピストン側油室15内の作動油は、第1径方向油路61と縮み側第1連通油路37とを通過し、縮み側バルブプレート42の弁体57を開弁させて縮み側蓄圧室72に流入する。縮み側蓄圧室72に流入した作動油は、縮み側バルブプレート42とピストン本体30との間隙を通過した後、伸び側第1連通油路36の上端部分と第2径方向油路62とを経由してロッド側油室14に流入する。すなわち、本実施形態においては、ダンパ6が縮み側にテレスコピック作動すると、伸び側第1連通油路36の上端部分と第2径方向油路62とが縮み側第2連通油路として機能する。
図7,図8に示すように、第1変形例に係るピストン16は、上述した実施形態と略同様の構成となっているが、第1径方向油路を設けることに代えて、ボルト49の軸心に軸方向油路81が形成されるとともに、インナヨーク32側に縮み側第1連通油路37と軸方向油路81とを連通させる連通油路82が形成されている。第1変形例の作用も、縮み側第1連通油路37とピストン側油室15との間における作動油の流通経路が異なる以外、実施形態と同様である。
図9,図10に示すように、第2変形例に係るピストン16は、上述した実施形態と略同様の構成となっているが、第2径方向油路を設けることに代えて、縮み側バルブプレート42に伸び側第1連通油路36に連絡する連通孔85が穿設され、縮み側蓄圧ハウジング47にロッド側油室14と伸び側蓄圧室71とを連通する連通孔86が穿設されている。第2変形例の作用も、伸び側第1連通油路36および縮み側第1連通油路37とロッド側油室14との間における作動油の流通経路が異なる以外、実施形態と同様である。なお、第2変形例の場合、実施形態とは異なり、ピストン本体30の上部に連結部材が設置されていない。
図11に示すように、第3変形例に係るピストン16は、上述した第1変形例と略同様の構成となっているが、伸び側蓄圧ハウジング46として軸方向長さの長いものが採用されるとともに、伸び側蓄圧ハウジング46の外周にピストンリング48が外嵌する保持溝91が形成されている。第3変形例の作用は第1変形例と略同様であるが、例えば伸び側蓄圧ハウジング46とピストンリング48とをサブアセンブリとしておくことで、ピストン16の組立作業が容易となる。
12 シリンダ
13 ピストンロッド
14 ロッド側油室
15 ピストン側油室
16 ピストン
30 ピストン本体
31 アウタヨーク
32 第1空隙
33 第2空隙
34 インナヨーク
35 連結部
38 伸び側連通油路
39 縮み側連通油路
41 伸び側バルブプレート
42 縮み側バルブプレート
43 電磁コイル
61,62 連結部材
Claims (6)
- 作動油が封入された円筒状のシリンダと、前記シリンダ内を往復動するとともに当該シリンダ内を一方の油室と他方の油室とに区画する円柱状のピストンと、前記ピストンを先端に保持したピストンロッドとを備え、
前記ピストンは、
前記ピストンロッドに固定され、前記シリンダに対して同軸をなす外周面を備えた強磁性体性のインナヨークと、
前記インナヨークの外周面と同軸をなすとともに、当該外周面に対して所定の空隙をもって対峙する内周面を備えた強磁性体性のアウタヨークと、
前記空隙に嵌装された電磁コイルと、
前記一方の油室に連通するとともに、前記他方の油室側の軸方向端面に開口を有する第1連通油路と、
前記第1連通油路の前記開口を弾性をもって閉鎖するとともに、前記電磁コイルの磁力によって閉方向に吸引される強磁性体性のバルブプレートと、
前記他方の油室側の軸方向端面に固着され、前記バルブプレートの前記開口とは反対側に蓄圧室を形成する蓄圧ハウジングと、
前記蓄圧室と前記他方の油室とを連通させる第2連通油路と
を有することを特徴とする減衰力可変ダンパ。 - 前記バルブプレートが前記他方の油室側の軸方向端面の略全体を覆うことを特徴とする、請求項1に記載された減衰力可変ダンパ。
- 前記バルブプレートには、前記第2連通油路の一部を形成する流量調整孔が形成されたことを特徴とする、請求項2に記載された減衰力可変ダンパ。
- 前記一方の油室側にも前記バルブプレートと同様のバルブプレートが設けられ、更に、当該一方の油室側のバルブプレートに対応するように、第1,第2連通油路および蓄圧ハウジングが設けられたことを特徴とする請求項1~請求項3のいずれか一項に記載された減衰力可変ダンパ。
- 前記シリンダの内周面と前記ピストンの外周面との間に所定の空隙が形成され、
前記第2連通油路が当該空隙に開口することを特徴とする、請求項1~請求項4のいずれか一項に記載された減衰力可変ダンパ。 - 蓄圧ハウジングが前記インナヨークに締結部品によって締結され、
前記第2連通油路は、少なくともその一部が前記締結部品の軸心に穿設されたことを特徴とする、請求項1~請求項4のいずれか一項に記載された減衰力可変ダンパ。
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JP2013532430A JP5738418B2 (ja) | 2011-09-10 | 2012-08-31 | 減衰力可変ダンパ |
EP12829622.5A EP2754918B1 (en) | 2011-09-10 | 2012-08-31 | Damper with variable damping force |
CN201280043898.XA CN103890442B (zh) | 2011-09-10 | 2012-08-31 | 变阻尼力阻尼器 |
US14/343,204 US9103398B2 (en) | 2011-09-10 | 2012-08-31 | Variable damping force damper |
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JP2011-197754 | 2011-09-10 | ||
JP2011197754 | 2011-09-10 |
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US (1) | US9103398B2 (ja) |
EP (1) | EP2754918B1 (ja) |
JP (1) | JP5738418B2 (ja) |
CN (1) | CN103890442B (ja) |
WO (1) | WO2013035290A1 (ja) |
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JP2017003017A (ja) * | 2015-06-11 | 2017-01-05 | Kybモーターサイクルサスペンション株式会社 | 緩衝器 |
US10823251B2 (en) | 2015-12-21 | 2020-11-03 | Lord Corporation | Seat-damping devices, systems, and methods |
CN107917162B (zh) * | 2017-12-27 | 2023-08-08 | 苏州西捷克缓冲科技有限公司 | 具有自动补偿功能的可调整型油压缓冲器 |
Citations (4)
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JPS484466Y1 (ja) * | 1967-11-29 | 1973-02-03 | ||
JP2008275126A (ja) | 2007-05-07 | 2008-11-13 | Honda Motor Co Ltd | 車両の減衰力可変式ダンパ |
JP2008309193A (ja) * | 2007-06-12 | 2008-12-25 | Kayaba Ind Co Ltd | 緩衝器のバルブ構造 |
JP4599422B2 (ja) | 2008-03-10 | 2010-12-15 | 本田技研工業株式会社 | 車両の減衰力可変式ダンパ |
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NL87342C (ja) * | 1952-01-04 | |||
JPS57171133A (en) * | 1981-04-13 | 1982-10-21 | Kayaba Ind Co Ltd | Hydraulic buffer |
JPS589538U (ja) * | 1981-07-13 | 1983-01-21 | カヤバ工業株式会社 | 油圧緩衝器 |
JPS58106239A (ja) * | 1981-08-24 | 1983-06-24 | Kayaba Ind Co Ltd | 油圧緩衝器 |
JPS60122037U (ja) * | 1984-01-26 | 1985-08-17 | カヤバ工業株式会社 | 油圧緩衝器 |
US5878850A (en) * | 1996-12-16 | 1999-03-09 | General Motors Corporation | Bi-directional pressure control valved damper |
JP4525918B2 (ja) * | 2005-04-15 | 2010-08-18 | トヨタ自動車株式会社 | 減衰力発生システムおよびそれを含んで構成された車両用サスペンションシステム |
US8240439B2 (en) | 2007-05-07 | 2012-08-14 | Honda Motor Co., Ltd. | Vehicle damper of variable damping force |
CN201705852U (zh) * | 2010-04-08 | 2011-01-12 | 长春孔辉汽车科技有限公司 | 电控式可变阻尼减振器 |
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2012
- 2012-08-31 JP JP2013532430A patent/JP5738418B2/ja not_active Expired - Fee Related
- 2012-08-31 EP EP12829622.5A patent/EP2754918B1/en not_active Not-in-force
- 2012-08-31 WO PCT/JP2012/005522 patent/WO2013035290A1/ja active Application Filing
- 2012-08-31 US US14/343,204 patent/US9103398B2/en active Active
- 2012-08-31 CN CN201280043898.XA patent/CN103890442B/zh not_active Expired - Fee Related
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JPS484466Y1 (ja) * | 1967-11-29 | 1973-02-03 | ||
JP2008275126A (ja) | 2007-05-07 | 2008-11-13 | Honda Motor Co Ltd | 車両の減衰力可変式ダンパ |
JP2008309193A (ja) * | 2007-06-12 | 2008-12-25 | Kayaba Ind Co Ltd | 緩衝器のバルブ構造 |
JP4599422B2 (ja) | 2008-03-10 | 2010-12-15 | 本田技研工業株式会社 | 車両の減衰力可変式ダンパ |
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US20140216870A1 (en) | 2014-08-07 |
EP2754918A4 (en) | 2015-05-27 |
EP2754918A1 (en) | 2014-07-16 |
EP2754918B1 (en) | 2016-11-02 |
US9103398B2 (en) | 2015-08-11 |
CN103890442A (zh) | 2014-06-25 |
JP5738418B2 (ja) | 2015-06-24 |
CN103890442B (zh) | 2015-12-02 |
JPWO2013035290A1 (ja) | 2015-03-23 |
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