WO2019130682A1 - Amortisseur et solénoïde - Google Patents

Amortisseur et solénoïde Download PDF

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Publication number
WO2019130682A1
WO2019130682A1 PCT/JP2018/034968 JP2018034968W WO2019130682A1 WO 2019130682 A1 WO2019130682 A1 WO 2019130682A1 JP 2018034968 W JP2018034968 W JP 2018034968W WO 2019130682 A1 WO2019130682 A1 WO 2019130682A1
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WO
WIPO (PCT)
Prior art keywords
core
mover
solenoid
shock absorber
valve
Prior art date
Application number
PCT/JP2018/034968
Other languages
English (en)
Japanese (ja)
Inventor
山岡　史之
Original Assignee
日立オートモティブシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2019562751A priority Critical patent/JP6877587B2/ja
Publication of WO2019130682A1 publication Critical patent/WO2019130682A1/fr

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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
    • 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
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/121—Guiding or setting position of armatures, e.g. retaining armatures in their end position
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures

Definitions

  • the present invention relates to a shock absorber that generates a damping force by controlling the flow of working fluid with respect to the stroke of a piston rod.
  • Patent Document 1 discloses a piston built-in type damping force adjustable hydraulic shock absorber having a solenoid of a core structure in which an axially arranged magnetic portion and a nonmagnetic portion are joined and integrated. .
  • the outer diameter of the mover is the same over the entire length, and the clearance (radial gap) between the magnetic portion and the mover and the clearance between the nonmagnetic portion and the mover are the same.
  • An object of the present invention is to provide a shock absorber with improved damping force controllability.
  • a shock absorber is A cylinder in which the working fluid is sealed; A piston slidably fitted in the cylinder; A piston rod having one end connected to the piston and the other end extending to the outside of the cylinder; A damping force generating mechanism capable of adjusting damping force characteristics by controlling a control current flowing to the solenoid;
  • the solenoid is a coil that generates a magnetic force by being energized.
  • a core provided on the inner circumferential side of the coil and having a magnetic portion and a nonmagnetic portion, wherein the magnetic portion and the nonmagnetic portion are arranged along the axial direction of the core;
  • a mover capable of moving the inner circumferential side of the core in the axial direction of the core; In the axial movement range of the mover relative to the core, the mover has a portion where the distance between the mover and the core in the radial direction is large and a small portion, and the small portion corresponds to the nonmagnetic portion of the core opposite.
  • the damping force controllability of the shock absorber can be improved.
  • the shock absorber 1 is a so-called piston built-in damping force in which a damping force generation mechanism 31 having a solenoid 91 is incorporated in a piston case 21 (piston) in the cylinder 2. It is an adjustable shock absorber 1 (hereinafter referred to as "the shock absorber 1").
  • the shock absorber 1 has a double cylinder structure in which the outer cylinder 3 is provided on the outside of the cylinder 2, and the reservoir 4 is formed between the cylinder 2 and the outer cylinder 3.
  • a piston valve 5 (piston) is slidably fitted in the cylinder 2.
  • a piston band 5A is provided on the outer peripheral side of the piston valve 5, and the inside of the cylinder 2 is divided into two chambers of an upper cylinder chamber 2A and a lower cylinder chamber 2B.
  • the piston valve 5 has an extension side passage 19 whose upper end opens to the cylinder upper chamber 2A, and a compression side passage 20 whose lower end opens to the cylinder lower chamber 2B.
  • a base valve 7 is provided which divides the cylinder lower chamber 2 ⁇ / b> B and the reservoir 4.
  • the base valve 7 is provided with passages 8 and 9 for communicating the cylinder lower chamber 2B with the reservoir 4.
  • the passage 8 is provided with a check valve 10 that allows only the flow of oil (working fluid) from the reservoir 4 side to the cylinder lower chamber 2B side.
  • the passage 9 is provided with a disk valve 11 that opens when the pressure of the fluid on the cylinder lower chamber 2B side reaches the set pressure and releases the pressure (fluid) on the cylinder lower chamber 2B side to the reservoir 4 side.
  • the bottom cap 12 is joined to the lower end of the outer cylinder 3, and the mounting member 13 is joined to the bottom cap 12.
  • the piston valve 5 is connected to the piston rod 6 via a piston case 21.
  • the piston case 21 has a substantially cylindrical case body 22 connected to the lower end (one end) of the piston rod 6, a case bottom 23 closing the lower end of the case body 22, and an axial direction from the lower end of the case bottom 23 (downward And a stem 24 on which the piston valve 5 is mounted.
  • the case bottom 23 and the shaft 24 are one component, and the case body 22 and the case bottom 23 are integrated by the screw 18.
  • the upper end side (other end side) of the piston rod 6 passes through the cylinder upper chamber 2A, and is further inserted through the rod guide 14 and the oil seal 15 mounted on the upper end portions of the cylinder 2 and the outer cylinder 3 Extended to the outside of the Further, the upper end portion of the outer cylinder 3 is covered by the cap 16, and the spring receiving member 17 is attached to the outer periphery of the outer cylinder 3.
  • the shock absorber 1 is a damping force generating mechanism 31 that generates a damping force by controlling the flow of oil between the cylinder upper chamber 2 A and the cylinder lower chamber 2 B generated by the movement of the piston rod 6. Equipped with The damping force generation mechanism 31 has a main valve 32 provided at the lower end of the piston valve 5.
  • the main valve 32 includes a damping valve 33 that generates a damping force by restricting the flow of oil from the cylinder upper chamber 2A to the cylinder lower chamber 2B when the piston valve 5 moves to the extension side, and the damping valve 33
  • the back pressure chamber 34 has an inner pressure acting in the valve closing direction, and the back pressure chamber introduction passage 35 introduces oil from the cylinder upper chamber 2A to the back pressure chamber 34.
  • the damping valve 33 is constituted by a disc valve, and the shaft portion 24 of the piston case 21 is inserted into the shaft hole.
  • the inner peripheral edge portion of the damping valve 33 is sandwiched by the inner peripheral edge portion of the piston valve 5 and the shaft portion 36A of the pilot case 36.
  • An annular packing 37 (seat portion) is provided on the lower surface of the damping valve 33.
  • the packing 37 is slidably in contact with the inner peripheral surface of the annular wall 38 of the pilot case 36.
  • an annular back pressure chamber 34 is formed between the damping valve 33 and the pilot case 36.
  • the damping valve 33 is seated on the lower end of the piston valve 5 such that the damping valve 33 covers the lower end opening of the extension side passage 19 of the piston valve 5.
  • the upper cylinder chamber 2A and the lower cylinder chamber are formed by the passage 27 (notch) formed at the upper end of the piston valve 5 and extending in the radial direction, the extension passage 19, and the passage formed by opening the damping valve 33.
  • a first passage communicating with 2B is configured.
  • the pilot case 36 has a plurality of passages 41 penetrating the pilot case 36 in the vertical direction.
  • a disc valve 39 is provided at the lower end of the pilot case 36.
  • the disc valve 39 has an annular hole whose outer peripheral edge is formed at the lower end of the pilot case 36 so that the shaft portion 24 of the piston case 21 is inserted into the shaft hole and covers the lower end opening of the passage 41 of the pilot case 36.
  • the seat portion 40 is seated.
  • the pressure in the back pressure chamber 34 reaches the set load of the disc valve 39, the disc valve 39 is opened. Thereby, the pressure (oil liquid) of the back pressure chamber 34 can be released to the cylinder lower chamber 2B.
  • the inner peripheral edge portion of the disc valve 39 is held between the shaft portion 36A of the pilot case 36 and the washer 42.
  • a disc valve 43 is provided at the upper end of the piston valve 5.
  • the shaft portion 24 of the piston case 21 is inserted into the shaft hole, and the inner peripheral edge portion is sandwiched between the inner peripheral edge portion of the piston valve 5 and the inner peripheral edge portion of the valve member 25.
  • the disc valve 43 is seated on an annular seat portion 45 having an outer peripheral edge portion formed on the upper end of the piston case 5 so as to cover the annular recess 44 formed on the upper end of the piston valve 5.
  • the shaft member 24 of the piston case 21 is inserted into the shaft hole of the valve member 25 so as to cover the annular recess formed in the lower end surface of the case bottom 23 of the piston case 21. It abuts on the end face.
  • an annular passage 50 is formed between the case bottom 23 of the piston case 21 and the valve member 25.
  • the upper end of the compression side passage 20 is opened in the annular recess 44 of the piston valve 5.
  • a disc valve 47 is provided at the lower end of the valve member 25.
  • the shaft portion 24 of the piston case 21 is inserted into the shaft hole, and the inner peripheral edge portion is sandwiched between the disk 48 and the inner peripheral edge portion of the valve member 25.
  • the disc valve 47 is seated on an annular seat 49A formed on the outer peripheral edge of the lower end of the valve member 25 and an annular seat 49B formed on the inner side of the seat 49A.
  • An annular passage 50 between the valve member 25 and the case bottom 23 of the piston case 21 is formed on the passage 25A passing through the valve member 25 in the axial direction (vertical direction) and the outer peripheral surface of the shaft 24 of the piston case 21
  • the back pressure chamber 34 is in communication with the axially extending passage 28 and the passage 46 formed in the shaft portion 36A of the pilot case 36.
  • Each component of the shaft portion 24 inserted into the shaft hole is fixed to the case bottom portion 23 of the piston case 21 by an axial force generated by tightening of the nut 26 mounted on the lower end portion of the shaft portion 24.
  • the case bottom 23 of the piston case 21 is provided with a plurality of (only one is shown in FIG. 2) passages 51 penetrating the case bottom 23 in the axial direction (vertical direction).
  • the lower end of the passage 51 opens into the annular passage 50 and the upper end opens into the chamber 52 formed inside the annular side wall of the case bottom 23.
  • a valve seat 55 is formed on the bottom surface (bottom surface of the chamber 52) of the piston case 21, and an annular seat portion 54 formed on the lower end of the first valve body 53 is seated on the valve seat 55. Then, the seat portion 54 of the first valve body 53 is seated on the valve seat 55, whereby the first valve chamber 56 is formed between the first valve body 53 and the case bottom portion 23.
  • the first valve chamber 56 is in communication with the cylinder lower chamber 2B via a passage 57 (shaft hole) formed in the shaft portion 24.
  • the cylinder upper chamber is formed by the passage 57, the first valve chamber 56, the flow passage formed by opening the first valve body 53, the chamber 52, the passage 51, and the flow passage formed by opening the disk valve 47.
  • a second passage connecting the cylinder 2A and the cylinder lower chamber 2B is configured. In other words, the second passage is communicated / blocked by the disc valve 47 being opened / closed.
  • the piston valve 5 (piston rod 6) is moved to the contraction side, the pressure of the first valve chamber 56 reaches the set load, and the first valve body 53 is opened, so that the cylinder The chamber 2A and the cylinder lower chamber 2B are communicated with each other.
  • the chamber 52 is in communication with the back pressure chamber 34 via the passage 51, the annular passage 50, and the passage 28 formed in the shaft portion 24.
  • the first valve body 53 is a nonmagnetic material, and is formed in a stepped cylindrical shape having a large diameter portion 58 and a small diameter portion 59.
  • the small diameter portion 59 of the first valve body 53 is slidably fitted in the lower portion of the inner circumferential surface 114 of the magnetic portion 96 of the core 93 described later.
  • a seal member 60 (see FIG. 3) seals the space between the small diameter portion 59 of the first valve body 53 and the inner circumferential surface 114 of the magnetic portion 96 of the core 93.
  • the first valve body 53 is formed with a bore 63 whose upper end is open. In the bore 63, a needle type second valve body 65 is accommodated.
  • the second valve body 65 is seated on a valve seat 64 formed at an opening peripheral portion of the second valve chamber 69 which opens at the bottom surface of the bore 63.
  • the set load of the first valve body 53 and the second valve body 65 is varied by adjusting the control current to the solenoid 91.
  • the sub valve 68 is configured by an actuator that varies the set load of the first valve body 53 and the second valve body 65 by the thrust of the first valve body 53, the second valve body 65, and the solenoid 91.
  • the passage 70 and a passage 71 for communicating the second valve chamber 69 with the cylinder lower chamber 2B when the second valve 65 is opened are formed.
  • the second valve body 65 has a flange portion 72 formed on the outer peripheral edge on the upper end side. The outer peripheral surface of the flange portion 72 is slidably fitted to the inner peripheral surface of the bore 63.
  • a compression coil spring 73 for biasing the second valve body 65 upward with respect to the first valve body 53 is interposed.
  • the second valve body 65 is formed with a recess 74 opened at the center of the upper end of the second valve body 65.
  • an inner conical surface 76 is formed which receives the lower end of the hemispherical lower end of the actuating pin 75.
  • the operating pin 75 has a shaft 77 whose lower end is received by the inner conical surface 76 of the second valve body 65, a base 79 whose lower half is formed hemispherical, and a convex 78 formed at the center of the upper end of the base 79. And.
  • the actuating pin 75 is received by an inner conical surface 81 formed on the mover 80 of the solenoid 91 described later and the hemispherical surface of the base 79 described later.
  • the inner conical surface 81 is connected to the lower end of the large diameter hole 82 opened to the upper end of the mover 80 and the upper end of the small diameter hole 83 opened to the lower end of the mover 80.
  • the shaft 77 of the actuating pin 75 is inserted into the small diameter hole 83 of the mover 80.
  • the actuating surface of the lower hemispherical surface of the base 79 is the inner conical surface 81 of the mover 80 by the biasing force of the compression coil spring 85 interposed between the outer peripheral edge of the base 79 and the spring bearing member 84. To be seated.
  • Spring receiving member 84 has a stepped shaft shape, and is formed between large diameter shaft portion 141, small diameter shaft portion 142, and between large diameter shaft portion 141 and small diameter shaft portion 142 to receive the upper end of compression coil spring 85. It has a flange portion 143.
  • the large diameter portion 84A of the spring receiving member 84 is inserted inside the upper end portion of the compression coil spring 85, and the small diameter shaft portion 142 is fitted to the ring 30 mounted in the recess 108 of the magnetic portion 95 of the core 93.
  • the second valve body 65 is biased downward with respect to the mover 80 by the spring force of the compression coil spring 86 mounted on the shaft portion 77 of the actuating pin 75.
  • the compression coil spring 86 is interposed between the bottom surface of the recess 74 of the second valve body 65 and the mover 80.
  • the space 88 between the second valve body 65 and the mover 80 inside the core 93 (magnetic portion 96) is formed by the passage 89 formed in the flange portion 72 of the second valve body 65. It is communicated with the bore 63 of the one valve body 53.
  • the coil cap 105 is fitted to the upper end portion of the inner peripheral surface 22A of the case main body 22 of the piston case 21.
  • the upper end of the coil cap 105 is provided with a terminal 133 held in an axial hole 131 A of the shaft portion 131 of the case main body 22 of the piston case 21.
  • the terminal 133 is connected to the coil 92 and the connector 135.
  • Connected to the terminal 133 is a connector 135 attached to one end (lower end) of the harness member 134 inserted into the shaft hole 6A of the piston rod 6.
  • the terminal 133 and the connector 135 are positioned in the rotational direction by the adapter 132.
  • the lower end of the piston rod 6 and the shaft portion 131 of the case body 22 of the piston case 21 are connected by a screw portion 136.
  • the large diameter hole portion 82 inside the mover 80 is the shaft hole 144 of the spring receiving member 84, the space 145 inside the shaft hole of the ring member 30, the passage 146 axially penetrating the magnetic portion 95, and the coil cap Via the passages 147 and 148 formed in 105, the annular passage 149 formed between the coil cap 105 and the cover 150 of the case body 22, and the passage 151 formed in the cover 150 of the case body 22. It communicates with the cylinder upper chamber 2A. As a result, an air vent passage is formed for discharging the air in the piston case 21 remaining at the time of assembly.
  • the solenoid 91 in the first embodiment includes a coil 92 generating a magnetic force when energized, a core 93 provided on the inner peripheral side of the coil 92, and a mover 80 capable of moving the inner peripheral side of the core 93 in the axial direction (vertical direction) Prepare.
  • the magnetic portion 95, the nonmagnetic portion 97, and the magnetic portion 96 are disposed in order from the top along the axial direction ("vertical direction" in FIG. 3).
  • the core 93 is configured by coupling the magnetic portions 95 and 96 disposed one above the other through the nonmagnetic portion 97.
  • the nonmagnetic portion 97 of the core 93 is formed in a substantially cylindrical shape, and the large inner diameter portion 100 is formed on the upper side (upper end) of the inner circumferential surface 98 via the step 98A.
  • the small outer diameter portion 101 is formed through the step portion 99A.
  • the magnetic part 95 of the core 93 is formed in a substantially cylindrical shape.
  • the upper portion of the inner circumferential surface 92A of the coil 92 is fitted to the outer circumferential surface 103 of the magnetic portion 95.
  • a small diameter shaft portion 104 is formed at the upper end of the magnetic portion 95, and the small diameter shaft portion 104 is fitted in a recess 106 that opens at the lower end surface of the coil cap 105.
  • the magnetic portion 95 is formed with an inner conical surface 107 opened at the lower end surface.
  • the tip (upper end) of the inner conical surface 107 is formed with a recess 108 in which the ring member 30 is fitted.
  • a small outer diameter portion 109 is formed on the lower end portion of the outer peripheral surface 103 of the magnetic portion 95 via the step portion 103A.
  • the peripheral edge of the opening of the inner conical surface 107 of the magnetic portion 95 is the annular lower end surface 110 of the magnetic portion 95.
  • a seal member 111 seals between the small diameter shaft portion 104 of the magnetic portion 95 and the concave portion 106 of the coil cap 105.
  • the magnetic part 96 of the core 93 is formed in a substantially cylindrical shape.
  • the lower portion of the inner circumferential surface 92A of the coil 92 is fitted to the outer circumferential surface 113 of the magnetic portion 96.
  • a large inner diameter portion 115 is formed on the upper end portion of the inner circumferential surface 114 of the magnetic portion 96 via the step portion 114A.
  • a flange portion 117 to be fitted to the inner peripheral surface 22A of the case main body 22 of the piston case 21 is formed.
  • the flange portion 117 of the magnetic portion 96 abuts on the upper end of an annular wall portion 116 formed on the case bottom 23 of the piston case 21.
  • the core 93 is axially positioned with respect to the piston case 21.
  • a boss portion 118 to be fitted to the inner circumferential surface 116A of the annular wall portion 116 is formed.
  • the core 93 causes the small outer diameter portion 109 at the lower end of the magnetic portion 95 to be pressed into the large inner diameter portion 100 at the upper end of the nonmagnetic portion 97, and the stepped portion 103 A of the outer peripheral surface 103 of the magnetic portion 95 and the upper end of the nonmagnetic portion 97
  • the magnetic portion 95 and the nonmagnetic portion 97 are joined by brazing along the circumferential direction between them.
  • the core 93 press-fits the small outer diameter portion 101 at the lower end of the nonmagnetic portion 97 into the large inner diameter portion 115 at the upper end of the magnetic portion 96.
  • the magnetic portion 96 and the nonmagnetic portion 97 are joined by brazing along the circumferential direction with the upper end.
  • the inner diameter of the inner peripheral surface 114 of the magnetic portion 96 and the inner diameter of the inner peripheral surface 98 of the nonmagnetic portion 97 are the same. That is, the inner circumferential surface 114 of the magnetic portion 96 and the inner circumferential surface 98 of the nonmagnetic portion 97 are flush with each other, in other words, disposed on the same inner cylindrical surface.
  • the magnetic portion 95 and the nonmagnetic portion 97 are positioned relative to each other in the axial direction. Further, the lower end of the nonmagnetic portion 97 abuts against the step portion 114A of the inner circumferential surface 114 of the magnetic portion 96, whereby the magnetic portion 96 and the nonmagnetic portion 97 are positioned relative to each other in the axial direction.
  • a seal member 119 mounted in an annular groove formed on the outer peripheral surface of the flange portion 117.
  • an outer conical surface 120 which is expanded in diameter toward the flange portion 117 is formed.
  • the mover 80 is formed in a substantially cylindrical shape.
  • the upper end portion of the mover 80 is formed with a tapered portion 123 having an outer conical surface 124 whose diameter is reduced toward the upper end.
  • the outer conical surface 124 of the mover 80 is opposed to the inner conical surface 107 of the magnetic portion 95 with a certain axial gap.
  • the mover 80 has a large diameter portion 125 having an outer circumferential surface 126 which is a sliding surface with respect to the core 93, and a small diameter portion 128 continuous with the lower end of the large diameter portion 125 via the step portion 127.
  • An annular groove 130 is formed in the lower portion of the outer peripheral surface 129 of the small diameter portion 128, and the falling of the mover 80 is restricted in the annular groove 130, and the outer peripheral surface 129 and the magnetic portion 96 of the core 93 make contact.
  • a sliding ring 158 is disposed to prevent
  • the outer peripheral surface 126 of the large diameter portion 125 of the mover 80 is slidably fitted to the inner peripheral surface 98 of the nonmagnetic portion 97 of the core 93. That is, a fixed sliding clearance is formed between the outer peripheral surface 126 of the large diameter portion 125 of the mover 80 and the inner peripheral surface 98 of the nonmagnetic portion 97 of the core 93.
  • the small diameter portion 128 of the mover 80 is fitted to the inner circumferential surface 114 (shaft hole) of the magnetic portion 96 with a fixed fit (space fit).
  • a fixed clearance is formed between the outer peripheral surface 129 of the small diameter portion 128 of the mover 80 and the inner peripheral surface 114 of the magnetic portion 96 of the core 93.
  • the solenoid 91 has a portion where the distance between the mover 80 and the core 93 in the radial direction is large and a small portion in the axial movement range of the mover 80 with respect to the core 93.
  • a portion (large diameter portion 125) having a small radial distance faces the nonmagnetic portion 97 of the core 93.
  • transfer of magnetic flux between core 93 and mover 80 in solenoid 91 is performed from magnetic portion 96 to small diameter portion 128 of mover 80 and from taper portion 123 of mover 80 to magnetic portion 95. It takes place on the inner conical surface 107.
  • the transfer direction of the magnetic flux between the core 93 and the mover 80 is also reverse.
  • the shock absorber 1 is mounted between the sprung and unsprung portions of the suspension system of the vehicle.
  • the shock absorber 1 When vibration occurs in the vehicle, the shock absorber 1 generates a damping force to the stroke of the piston rod 6 by controlling the flow of oil (working fluid).
  • the damping force generation mechanism 31 varies the back pressure (pressure of the back pressure chamber 34) of the main valve 32 during the extension stroke of the piston rod 6 (hereinafter referred to as "the extension stroke") to reduce the damping valve.
  • the damping force is adjusted by changing the valve opening pressure of 33.
  • the thrust of the solenoid 91 is controlled to change the set load (opening pressure) of the first valve body 53, thereby reducing the damping force.
  • the second valve body 65 When the oil (working fluid) on the cylinder upper chamber 2A side is pressurized by the movement of the piston valve 5 (piston) in the cylinder 2 during the extension stroke, the second valve body 65 is closed, ie, When the second valve body 65 is seated on the valve seat 64 of the first valve body 53, the upstream side of the back pressure chamber 34 is the passage 46, the passage 28, the inner peripheral passage 25 B of the valve member 25, and the disc valve 47 It communicates with the cylinder upper chamber 2A through the back pressure chamber introduction passage 35 formed in the above. Thus, the pressurized fluid in the cylinder upper chamber 2A side is introduced into the back pressure chamber 34 via the back pressure chamber introduction passage 35, the passage 28, and the passage 46.
  • the downstream side of the back pressure chamber 34 is in communication with the second valve chamber 69 via the passage 46, the passage 28, the annular passage 50, the passage 51, the chamber 52 and the passage 70.
  • the set load (opening pressure) of the damping valve 33 is adjusted by controlling the thrust (control current) of the solenoid 91 and varying the pressure of the back pressure chamber 34, that is, the back pressure of the main valve 32. Ru.
  • the pressure of the second valve chamber 69 reaches the set load of the second valve body 65 and the second valve body 65 is opened, the working fluid flows from the back pressure chamber introduction passage 35, and the back pressure is generated.
  • a pressure difference is generated in the chamber introduction passage 35, a pressure difference is generated between the back pressure chamber 34 and the cylinder upper chamber 2A.
  • this differential pressure becomes equal to or more than the set load of the main valve 32, the main valve 32 opens.
  • the thrust (control current) of the solenoid 91 is controlled to change the set load (opening pressure) of the first valve body 53, so that the thrust of the solenoid 91 is resisted.
  • the valve When the valve is opened, the oil on the cylinder lower chamber 2B side passes through the passage 57, the chamber 52, the passage 51, and the annular passage 50, and further opens the disc valve 47 in which the back pressure chamber introduction passage 35 is formed. The valve is circulated to the cylinder upper chamber 2A. At this time, damping force of the valve characteristic by the disc valve 47 can be obtained.
  • the first valve body 53 and the second valve body 65 move integrally.
  • the outer diameter of the mover is the same over the entire length, and the clearance (radial gap) between the magnetic portion and the mover and the nonmagnetic portion
  • the clearance with the mover is the same, all of the outer peripheral surface of the mover slides on the inner peripheral surface of the core in the axial movement range of the mover relative to the core.
  • the lateral force (radial attraction force) acting on the mover becomes uneven in the circumferential direction by the eccentricity of the mover relative to the core, the sliding resistance between the mover and the core increases, and the solenoid
  • the hysteresis of the thrust characteristic becomes large.
  • there is a difference in damping force characteristics between the increase direction and the decrease direction with respect to the control current to the coil and the damping force controllability is deteriorated.
  • the large diameter portion 125 of the mover 80 is opposed to the nonmagnetic portion 97 of the core 93, thereby reducing the clearance (distance between radial directions) between the mover 80 and the core 93.
  • the section B of FIG. 4 and making the small diameter portion 128 of the mover 80 face the magnetic section 96 of the core 93, a portion where the clearance between the mover 80 and the core 93 is large (section C of FIG. And the magnetic force of the small diameter portion 128 of the mover 80 and the core 93 so that the lateral force in the section C of FIG. 4 becomes small while securing the solenoid thrust (axial direction attraction force) applied to the mover 80).
  • the clearance with the part 96 was made appropriate.
  • the clearance between the large diameter portion 125 of the mover 80 and the nonmagnetic portion 97 of the core 93 is a minute clearance for sliding between the large diameter portion 125 and the nonmagnetic portion 97, and the small diameter portion of the mover 80
  • the clearance between 128 and the magnetic portion 96 of the core 93 is a clearance for keeping the small diameter portion 128 and the magnetic portion 96 in a non-contact state.
  • FIG. 5 what is shown in FIG. 5 is the clearance in the section C of FIG. 4, that is, the clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93 (here simply referred to as “clearance”) on the horizontal axis.
  • the vertical axis represents the force acting on the mover 80 (referred to as “generated force” in FIG. 4) in a state in which the current value supplied to the coil 92 is fixed.
  • the lateral force generated in section A of FIG. 4 is substantially constant in the section where the clearance exceeds 0 and is 0.35 mm.
  • the solenoid thrust (axial direction attraction force) tends to gradually decrease in a section where the clearance exceeds 0 and is up to 0.35 mm.
  • the lateral force generated in section C in FIG. 4 tends to decrease sharply in a section where the clearance exceeds 0 to 0.2 mm, and then gradually decreases.
  • the lateral force generated in section C of FIG. 4 is the mover relative to the axis of the core 93 due to the clearance (sliding clearance) between the large diameter portion 125 of the mover 80 and the nonmagnetic portion 97 of the core 93.
  • This eccentricity causes the magnetic flux density of the solenoid 91 to deviate along the circumferential direction, and as a result, a radial attraction force acts on the mover 80.
  • the solenoid thrust ie, the movable
  • FIG. 6 shows the piston speed (0.1 m / s, 0.3 m / s, 0.6 m / s) in the conventional shock absorber in which all the outer peripheral surface of the mover slides on the inner peripheral surface of the core
  • FIG. 7 is a chart showing damping force characteristics of the shock absorber according to the first embodiment.
  • the hysteresis of the damping force generated by the damping force generating mechanism 31, that is, the damping force and the control current when the control current is changed in the increasing direction is reduced. It is possible to reduce the difference from the damping force when changing in the direction.
  • the current value supplied to the coil 92 can be made to correspond to the damping force generated by the damping force generating mechanism 31, and the controllability of the damping force can be improved.
  • the shock absorber (1) of the first embodiment includes a cylinder (2) in which a working fluid is enclosed, a piston (2) slidably fitted in the cylinder (2), and a piston (21) at one end
  • the piston rod (6) is connected to the other end and the other end is extended to the outside of the cylinder (2), and the damping force generating mechanism (31) whose damping force characteristic can be adjusted by controlling the control current flowing to the solenoid (91).
  • the solenoid (91) is provided with a coil (92) for generating a magnetic force by being energized, and an inner peripheral side of the coil (92), and an axially disposed magnetic portion (95, 96) and a core (93) having a nonmagnetic portion (97), and a mover (80) axially movable on the inner peripheral side of the core (93), the core of the mover (80) In the axial movement range relative to (93), the mover (80) and the core (93 And a radial distance is larger portion and a smaller portion of the small portion is opposed non-magnetic portion of the core (93) and (97).
  • the radial distance between the mover (80) and the core (93) in the portion where the radial distance between the mover (80) and the core (93) is large (first embodiment)
  • the reduction of the solenoid thrust and the deviation of the lateral force generated in the mover (80) can be minimized. It is possible to reduce the sliding resistance between the mover (80) and the core (93), which is generated when the mover (80) moves in the axial direction.
  • the hysteresis of the damping force generated by the damping force generation mechanism (31), that is, the difference between the damping force when the control current is changed in the increasing direction and the damping force when the control current is changed in the decreasing direction Can be reduced, and as a result, controllability of damping force can be improved.
  • the solenoid ( 91) and the control current to the coil (92) can be reduced, and consequently, the buffer (1) can be miniaturized and the power consumption can be reduced.
  • the mover (80) since the mover (80) has the large diameter portion (125) and the small diameter portion (128), the large diameter portion (125) and the nonmagnetic portion (97) of the core (93) are opposed to each other. The sliding resistance between the mover (80) and the core (93) can be reduced.
  • the damping force generation mechanism (31) including the solenoid (91) is incorporated in the cylinder (2), the first embodiment can be applied to a so-called piston built-in damping force adjustable hydraulic shock absorber .
  • the damping force generation mechanism (31) including the solenoid (91) Can be applied to a so-called control valve side-mounted damping force-adjusting hydraulic shock absorber in which the cylinder is mounted on the side wall of the cylinder (2).
  • the inner diameter of the core 93 in the axial movement range (section B and section C in FIG. 4) of the mover 80 is the same, and the mover 80 is provided with the large diameter portion 125 and the small diameter portion 128.
  • the portion (the clearance between the small diameter portion 128 of the mover 80 and the magnetic portion 96 of the core 93) and the small portion (the large diameter portion 125 of the mover 80 and the core) And a sliding clearance (93) with the nonmagnetic portion 97).
  • the outer diameter of the cylindrical portion 155 (sections B and C in FIG. 4) of the mover 80 is formed identical, and the core 93 is made large with the small inner diameter portion 156 (small diameter portion).
  • the inner diameter portion 157 (large diameter portion) the radial distance between the mover 80 and the core 93 is small (a clearance between the cylindrical portion 155 of the mover 80 and the magnetic portion 96 of the core 93).
  • a portion (sliding clearance between the cylindrical portion 155 of the mover 80 and the nonmagnetic portion 97 of the core 93) is provided.
  • a sliding clearance is formed between the inner circumferential surface 156A of the small inner diameter portion 156 of the nonmagnetic portion 97 of the core 93 and the outer circumferential surface 155A of the cylindrical portion 155 of the mover 80.
  • a sliding ring 158 made of nonmagnetic material is attached to the annular groove 130 formed in the outer peripheral surface 155A of the cylindrical portion 155 of the mover 80.
  • the same effects as those of the first embodiment described above can be obtained. Further, in the second embodiment, unlike the mover 80 in the first embodiment, there is no need to finish the outer peripheral surface 126 of the large diameter portion 125 and the outer peripheral surface 129 of the small diameter portion 128 in separate steps. can do.
  • the inner circumferential surface 156A of the small inner diameter portion 156 of the nonmagnetic portion 97 and the inner circumferential surface 114 of the magnetic portion 96 of the core 93 are finished in the state of individual components before the core 93 is integrated. The number of processing steps does not increase with respect to the first embodiment.
  • the radial gap between the mover and the core has a large portion and a small portion, and the small portion is the core
  • the configuration is shown facing the nonmagnetic portion of Desirably, in the entire axial direction movement range of the mover relative to the core, the small radial gap is opposed to the nonmagnetic portion of the core, but the radial gap is partially small in the axial movement range. It does not exclude what makes the part face the magnetic part of the core.
  • the present invention is not limited to the above-described embodiment, but includes various modifications.
  • the above-described embodiment is described in detail to explain the present invention in an easy-to-understand manner, and is not necessarily limited to one having all the described configurations.
  • part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Damping Devices (AREA)
  • Electromagnets (AREA)

Abstract

Selon la présente invention, une partie où un espace libre entre un élément mobile et un noyau est petit est formée, et une partie où l'espace libre entre l'élément mobile et le noyau est grand est formée, et un espace libre entre une partie de petit diamètre de l'élément mobile et une partie magnétique du noyau est optimisé de telle sorte qu'une force latérale générée dans l'élément mobile est réduite tandis qu'une poussée de solénoïde est maintenue, et il est ainsi possible de supprimer à un minimum une réduction de la poussée de solénoïde et de la polarisation de la force latérale générée dans l'élément mobile, et d'améliorer la commande de force d'amortissement d'un mécanisme de génération de force d'amortissement.
PCT/JP2018/034968 2017-12-26 2018-09-21 Amortisseur et solénoïde WO2019130682A1 (fr)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022070602A1 (fr) * 2020-09-30 2022-04-07 日立Astemo株式会社 Solénoïde, mécanisme de réglage de force d'amortissement, et amortisseur à force d'amortissement réglable
WO2022070879A1 (fr) * 2020-09-30 2022-04-07 日立Astemo株式会社 Solénoïde, mécanisme de réglage de force d'amortissement, et amortisseur de type à réglage de force d'amortissement
US20220252128A1 (en) * 2019-09-09 2022-08-11 Kyb Corporation Solenoid, solenoid valve, and shock absorber

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4109955B2 (ja) * 2002-10-04 2008-07-02 株式会社ケーヒン 電磁弁
JP4141375B2 (ja) * 2003-11-07 2008-08-27 三菱電機株式会社 ３方ブリード式比例電磁弁
JP2014073018A (ja) * 2012-09-28 2014-04-21 Hitachi Automotive Systems Ltd ソレノイド
JP2016070421A (ja) * 2014-09-30 2016-05-09 日立オートモティブシステムズ株式会社 緩衝器
WO2016104392A1 (fr) * 2014-12-26 2016-06-30 イーグル工業株式会社 Solénoïde

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4109955B2 (ja) * 2002-10-04 2008-07-02 株式会社ケーヒン 電磁弁
JP4141375B2 (ja) * 2003-11-07 2008-08-27 三菱電機株式会社 ３方ブリード式比例電磁弁
JP2014073018A (ja) * 2012-09-28 2014-04-21 Hitachi Automotive Systems Ltd ソレノイド
JP2016070421A (ja) * 2014-09-30 2016-05-09 日立オートモティブシステムズ株式会社 緩衝器
WO2016104392A1 (fr) * 2014-12-26 2016-06-30 イーグル工業株式会社 Solénoïde

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220252128A1 (en) * 2019-09-09 2022-08-11 Kyb Corporation Solenoid, solenoid valve, and shock absorber
WO2022070602A1 (fr) * 2020-09-30 2022-04-07 日立Astemo株式会社 Solénoïde, mécanisme de réglage de force d'amortissement, et amortisseur à force d'amortissement réglable
WO2022070879A1 (fr) * 2020-09-30 2022-04-07 日立Astemo株式会社 Solénoïde, mécanisme de réglage de force d'amortissement, et amortisseur de type à réglage de force d'amortissement
JP7446462B2 (ja) 2020-09-30 2024-03-08 日立Astemo株式会社 ソレノイド、減衰力調整機構および減衰力調整式緩衝器
JP7446464B2 (ja) 2020-09-30 2024-03-08 日立Astemo株式会社 ソレノイド、減衰力調整機構および減衰力調整式緩衝器

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