WO2016084621A1 - 減衰バルブ及び緩衝器 - Google Patents
減衰バルブ及び緩衝器 Download PDFInfo
- Publication number
- WO2016084621A1 WO2016084621A1 PCT/JP2015/081900 JP2015081900W WO2016084621A1 WO 2016084621 A1 WO2016084621 A1 WO 2016084621A1 JP 2015081900 W JP2015081900 W JP 2015081900W WO 2016084621 A1 WO2016084621 A1 WO 2016084621A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- valve
- extension
- chamber
- passage
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- 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
- F16F9/446—Adjustment of valve bias or pre-stress
-
- 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
- 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
- F16F9/516—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 resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
-
- 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
Definitions
- This invention relates to a damping valve and a shock absorber.
- Some shock absorbers used in vehicle suspensions include a damping valve that can vary the damping force.
- a shock absorber a cylinder, a piston that divides the cylinder into an extension side chamber and a pressure side chamber, a piston rod that is connected to the piston at one end and is movably inserted into the cylinder, a damping valve, And a damping valve is a disk that opens and closes a passage that communicates between an extension side chamber and a pressure side chamber provided in the piston, and an annular valve seat that surrounds an outlet end of the passage provided in the piston.
- the shock absorber configured as described above, it is possible to control the damping force at the time of expansion and contraction by controlling the pressure in the back pressure chamber by the electromagnetic pressure control valve.
- the liquid passes through the fixed orifice provided in the disc valve and moves back and forth between the extension side chamber and the pressure side chamber. For this reason, when the piston moves at a low speed, the shock absorber exerts a damping force mainly by the fixed orifice.
- the damping force is exerted by the fixed orifice until the disk valve is opened from the valve seat. Therefore, in order to reduce the damping force, the fixed orifice It is necessary to increase the opening area. When the opening area of the fixed orifice is increased, the damping force can be reduced. However, since the maximum value of the damping force is determined by the fixed orifice, the damping force adjustment range is significantly limited.
- the adjustment range of the damping force can be increased. However, even if the damping force is soft, the damping force cannot be sufficiently reduced and the riding comfort in the vehicle is deteriorated.
- An object of the present invention is to provide a damping valve and a shock absorber capable of reducing the damping force when the damping force characteristic is made soft and expanding the damping force adjustment range.
- a valve disc having a passage and a valve seat surrounding an outlet end of the passage, and an annular leaf stacked on the valve disc and seated on and off the valve seat to open and close the passage
- a valve and an urging mechanism for applying a variable urging force to the leaf valve toward the valve disk side, and the leaf valve can be entirely retracted in the axial direction with respect to the valve disk,
- a damping valve is provided in which a gap is formed between the leaf valve and the valve seat.
- FIG. 1 is a sectional view of a shock absorber to which a damping valve according to an embodiment of the present invention is applied.
- FIG. 2 is a partially enlarged sectional view of a shock absorber to which the damping valve according to the embodiment of the present invention is applied.
- FIG. 3 is an enlarged cross-sectional view of the damping valve according to the embodiment of the present invention.
- FIG. 4 is a diagram illustrating the damping force characteristics of the shock absorber to which the damping valve according to the embodiment of the present invention is applied.
- the damping valve according to the embodiment of the present invention is applied to both the extension side damping valve and the compression side damping valve of the shock absorber D as shown in FIG.
- the damping valve is a valve disk having an extension side passage 3 and a pressure side passage 4 as passages, and an annular extension side valve seat 2d and a pressure side valve seat 2c surrounding the outlet ends of the extension side passage 3 and the pressure side passage 4, respectively.
- the piston 2, the annular extension leaf valve Ve stacked on the piston 2 and separated from the extension side valve seat 2 d to open and close the extension side passage 3, and the piston 2 stacked on the compression side valve seat 2 c.
- an annular pressure side leaf valve Vp that opens and closes the pressure side passage 4 and a variable urging force are applied to the extension side leaf valve Ve toward the piston 2 side, and a variable urging force is applied to the pressure side leaf valve Vp toward the piston 2 side.
- the damping valve may be applied only to the expansion side damping valve of the shock absorber D or only to the compression side damping valve.
- the shock absorber D includes a cylinder 1 filled with a fluid such as hydraulic oil, the above-described damping valve accommodated in the cylinder 1, a piston 2 slidably inserted into the cylinder 1, and a piston within the cylinder 1. And an extension side chamber R1 and a pressure side chamber R2 partitioned by 2 and a piston rod 7 that is movably inserted into the cylinder 1 and connected to the piston 2.
- the shock absorber D resists the flow of the liquid passing through the expansion side passage 3 by the expansion side leaf valve Ve when the piston 2 moves in the axial direction which is the vertical direction in FIG.
- a damping force is exerted on the flow of the liquid passing through the pressure side passage 4 by applying resistance by the pressure side leaf valve Vp.
- a free piston that slides in the cylinder 1 is provided below the cylinder 1 in FIG.
- a gas chamber is defined in the cylinder 1 by a free piston.
- the other end of the piston rod 7, one end of which is connected to the piston 2 passes through the inner periphery of an annular rod guide (not shown) provided at the upper end of the cylinder 1 and protrudes out of the cylinder 1.
- a seal (not shown) is provided between the piston rod 7 and the cylinder 1, and the cylinder 1 is liquid-tight by the seal.
- the shock absorber D is a so-called single rod type, the volume of the piston rod 7 that enters and exits the cylinder 1 as the shock absorber D expands and contracts is such that the volume of the gas in the gas chamber expands or contracts, and the free piston is the cylinder 1. This is compensated by moving up and down.
- the shock absorber D is a single cylinder type, but instead of a configuration in which a free piston and a gas chamber are provided, a reservoir may be provided on the outer periphery or outside of the cylinder 1 and volume compensation of the piston rod 7 may be performed by the reservoir. .
- the urging mechanism of the damping valve includes an extension side spool Se that urges the extension side leaf valve Ve, an extension side back pressure chamber Ce that presses the extension side spool Se with internal pressure, and a pressure side that urges the compression side leaf valve Vp.
- the spool Sp communicates with the compression-side back pressure chamber Cp via the compression-side back pressure chamber Cp that presses the compression-side spool Sp with internal pressure, and the expansion-side pilot orifice Pe as an expansion-side resistance element that provides resistance to the flow of liquid passing therethrough.
- the communication passage 24 communicated with the expansion-side back pressure chamber Ce via a compression-side pilot orifice Pp as a compression-side resistance element that gives resistance to the flow of the liquid that passes through the expansion-side chamber R1 toward the compression-side back pressure chamber Cp.
- the expansion side pressure introduction passage Ie that allows only the flow of liquid, the compression side pressure introduction passage Ip that allows only the flow of liquid from the compression side chamber R2 to the extension side back pressure chamber Ce, and the communication passage 24 are connected.
- Adjustment passage Pc a pressure side discharge passage Ep that allows the downstream of the adjustment passage Pc to communicate with the expansion side chamber R1 and allows only a liquid flow from the adjustment passage Pc to the expansion side chamber R1, and a pressure side chamber R2 that is downstream of the adjustment passage Pc.
- the piston rod 7 includes a piston holding member 8 that holds the piston 2 and an electromagnetic valve housing that is connected to the piston holding member 8 at one end to form a hollow housing portion L that houses the electromagnetic pressure control valve 6 together with the piston holding member 8.
- the cylinder 9 includes a rod member 10 having one end connected to the solenoid valve housing cylinder 9 and the other end protruding outward from the upper end of the cylinder 1.
- the piston holding member 8 is provided on the holding shaft 8a on which the annular piston 2 is mounted on the outer periphery, the flange 8b provided on the upper end outer periphery in FIG. 1 of the holding shaft 8a, and the upper end outer periphery in FIG. 1 of the flange 8b. And a cylindrical socket 8c.
- the piston holding member 8 has an annular hole 8d that opens at the tip of the holding shaft 8a and extends in the axial direction and communicates with the inside of the socket 8c, and a flange 8b that surrounds the holding shaft 8a at the lower end in FIG.
- a cylindrical passage is formed in which an annular groove 23a provided on the outer periphery forms a communication passage 24 that allows the expansion side pilot orifice Pe and the pressure side pilot orifice Pp to communicate with each other in the vertical hole 8d.
- the separator 23 is inserted.
- An annular valve seat 23b surrounding the opening at the lower end is provided at the lower end of the separator 23 in FIG.
- the vertical hole 8d allows the pressure side chamber R2 and the socket 8c to communicate with each other through a passage inside the separator 23.
- the extension side pilot orifice Pe and the pressure side pilot orifice Pp are configured not to communicate with the pressure side chamber R2 and the socket 8c in the vertical hole 8d by the separator 23.
- the horizontal hole 8g communicates with the communication path 24, and the horizontal hole 8g is not communicated with the pressure side chamber R2 and the socket 8c in the vertical hole 8d by the separator 23.
- the expansion resistance element and the compression resistance element may have any configuration as long as resistance can be given to the flow of liquid passing therethrough, and is not limited to an orifice, and may be a restriction such as a choke passage. It may be a valve that provides resistance, such as a leaf valve or a poppet valve.
- An annular recess 8k is provided on the outer periphery of the upper end of the socket 8c in FIG.
- the socket 8c is provided with a through hole 8m that leads from the recess 8k into the socket 8c.
- An annular plate 22a is disposed in the recess 8k, and the annular plate 22a is urged by a spring member 22b from above in FIG. 1 to close the through hole 8m.
- the solenoid valve housing cylinder 9 has a tubular housing cylinder portion 9a and a tubular connection having an outer diameter smaller than that of the housing cylinder portion 9a and extending upward from the top of the housing cylinder portion 9a in FIG. Part 9b, and a through hole 9c that opens to the side of the housing cylinder part 9a and communicates with the inside.
- the solenoid valve housing cylinder 9 and the piston holding member 8 are integrated by screwing the socket 8c of the piston holding member 8 into the inner periphery of the housing cylinder portion 9a of the solenoid valve housing cylinder 9.
- the electromagnetic valve accommodating cylinder 9 and the piston holding member 8 form an accommodating portion L in which the electromagnetic pressure control valve 6 is accommodated.
- an adjustment passage Pc described later is provided in the housing portion L.
- the accommodating portion L communicates with the communication path 24 through the port 8f, the annular groove 8e, and the lateral hole 8g.
- the port 8f, the annular groove 8e, and the lateral hole 8g form a part of the adjustment passage Pc.
- path which connects the accommodating part L and the communicating path 24 it is not limited to the port 8f, the annular groove 8e, and the horizontal hole 8g, For example, it is a path
- the port 8f, the annular groove 8e, and the lateral hole 8g are employed as a passage that connects the housing portion L and the communication passage 24, the processing of the passage is facilitated.
- the through hole 9c is opposed to the recess 8k. Together with the through hole 8m, the through hole 9c serves as a passage that allows the accommodating portion L to communicate with the extension side chamber R1.
- a check valve 22 that allows only the flow of liquid from the inside of the accommodating portion L toward the extension side chamber R1 is formed.
- the pressure side discharge passage Ep is formed by the through hole 9c, the recess 8k, the through hole 8m, and the check valve 22.
- a check valve 25 that is attached to and detached from an annular valve seat 23b provided at the lower end of the separator 23 in FIG.
- the check valve 25 prevents the flow of liquid from the pressure side chamber R2 side toward the storage portion L, and allows only the liquid flow from the storage portion L toward the pressure side chamber R2.
- the extension side discharge passage Ee is formed in the vertical hole 8d.
- the rod member 10 has a screw portion to which the connecting portion 9b of the solenoid valve housing cylinder 9 is screwed at the lower end in FIG.
- the piston rod 7 is formed by integrating the rod member 10, the electromagnetic valve housing cylinder 9 and the piston holding member 8.
- a harness H for supplying power to a solenoid described later is inserted into the rod member 10 and the connecting portion 9b of the electromagnetic valve housing cylinder 9.
- the upper end of the harness H extends outward from the upper end of the rod member 10 and is connected to the power source and the control device.
- a pressure side annular spacer 60 as an annular spacer above the piston 2 in FIG.
- a collar 61 as a shaft member configured by stacking a plurality of annular plates having a circular outer shape, an annular pressure side leaf valve Vp slidably mounted on the outer periphery of the collar 61, and a slide on the outer periphery of the collar 61.
- a pressure-side annular plate 62 as an annular plate that is mounted movably, a pressure-side stopper 63, and a pressure-side chamber 11 that houses a pressure-side spool Sp and forms a pressure-side back pressure chamber Cp are assembled.
- An annular extension leaf valve Ve that is slidably attached, an extension side annular plate 66 as an annular plate that is slidably attached to the outer periphery of the collar 65, an extension side stopper 67, and an extension side spool Se.
- the extension side chamber 12 which is accommodated and forms the extension side back pressure chamber Ce is assembled.
- Piston 2 is formed by superimposing discs 2a and 2b which are divided into two parts.
- An extension side passage 3 and a pressure side passage 4 are formed inside the piston 2 to communicate the extension side chamber R1 and the pressure side chamber R2.
- the piston 2 by forming the piston 2 with the discs 2a and 2b divided into the upper and lower sides, the expansion side passage 3 and the pressure side passage 4 having complicated shapes can be formed without drilling. Can be manufactured inexpensively and easily.
- annular window 2e communicating with the pressure side passage 4, an annular pressure side valve seat 2c provided on the outer peripheral side of the annular window 2e and surrounding the pressure side passage 4, and an annular window 2e provided on the inner periphery of 2e.
- annular window 2g communicating with the extension passage 3
- annular extension valve seat 2d provided on the outer peripheral side of the annular window 2g and surrounding the extension passage 3
- annular window provided on the inner peripheral sheet portion 2h provided on the inner periphery of 2g.
- the extension-side leaf valve Ve is formed in an annular shape to allow insertion of the holding shaft 8 a of the piston holding member 8.
- the extension side leaf valve Ve is composed of a single annular plate.
- the extension-side leaf valve Ve may be configured by a plurality of laminated annular plates.
- the extension-side leaf valve Ve configured in this way is stacked below the piston 2 in FIG. 3 via the extension-side annular spacer 64 stacked on the inner peripheral seat portion 2h of the piston 2.
- the extension side leaf valve Ve has a notch Oe on the outer periphery that functions as an orifice when seated on the extension side valve seat 2d.
- the extension side leaf valve Ve is slidably mounted on the outer periphery of the collar 65.
- an expansion side annular plate 66 laminated on the expansion side leaf valve Ve is slidably mounted on the outer periphery of the collar 65.
- An annular auxiliary valve 71 having an outer diameter smaller than that of the expansion side annular plate 66 is laminated on the side of the expansion side annular plate 66 opposite to the expansion side leaf valve Ve.
- the auxiliary valve 71 is also slidably mounted on the outer periphery of the collar 65.
- the axial length when the extension-side leaf valve Ve, the extension-side annular plate 66 and the auxiliary valve 71 are stacked is set shorter than the axial length of the collar 65. Below the collar 65 in FIG.
- an extension side stopper 67 which is annular and has an outer diameter set larger than the inner diameters of the auxiliary valve 71 and the extension side annular plate 66. Below the extension side stopper 67, an extension side chamber 12 described later is disposed.
- the extension side leaf valve Ve, the extension side annular plate 66, and the auxiliary valve 71 are guided by a collar 65 as a shaft member, and are axially arranged between the extension side annular spacer 64 and the extension side stopper 67 in FIG. It can move in the direction.
- the extension side leaf valve Ve is pressed by the pressure from the extension side passage 3 side, so that the outer circumference is bent together with the extension side annular plate 66 and retreats from the piston 2 together with the extension side annular plate 66 and the auxiliary valve 71. Is possible.
- the retraction amounts of the extension side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 from the piston 2 are set by the axial length of the collar 65. Since the collar 65 is composed of a plurality of annular plates, the axial length of the collar 65 can be adjusted by changing the number of annular plates to be stacked.
- the collar 65 is not limited to a plurality of annular plates, and may be a single annular plate.
- the extension-side leaf valve Ve is stacked below the piston 2 in FIG. 3 via the extension-side annular spacer 64 that is stacked on the inner peripheral seat portion 2h of the piston 2.
- a gap is formed between the extension side leaf valve Ve and the extension side valve seat 2d.
- the vertical length of this gap in FIG. 3 can be adjusted by exchanging the expansion-side annular spacer 64 with a different thickness, or changing the number of layers of the expansion-side annular spacer 64.
- the gap between the extension side leaf valve Ve and the extension side valve seat 2d is set so that the height of the inner peripheral seat portion 2h is higher than the height of the extension side valve seat 2d, so that the extension side annular spacer 64 is provided.
- the size of the gap can be easily adjusted by providing the extended-side annular spacer 64.
- the extension side leaf valve Ve bends when an urging force is applied by the urging mechanism from the side opposite to the piston 2 on the back side, and seats on the extension side valve seat 2d when the urging force increases, and the extension side passage 3 is closed. In this state, the extension side passage 3 and the pressure side chamber R2 communicate with each other only through the notch Oe.
- the expansion side annular plate 66 is set to have higher bending rigidity than the expansion side leaf valve Ve. Therefore, the axial length (thickness) of the expansion side annular plate 66 is longer than the axial length (thickness) of the expansion side leaf valve Ve. Not only the rigidity is increased by the length in the axial direction, but the expansion-side annular plate 66 may be formed of a material having higher rigidity than the expansion-side leaf valve Ve.
- the inner diameter of the expansion side annular plate 66 is set to be smaller than the outer diameter of the inner peripheral sheet portion 2h provided in the piston 2.
- the outer diameter of the expansion side annular plate 66 is set to be larger than the inner diameter of the expansion side valve seat 2d.
- the auxiliary valve 71 has an outer diameter smaller than that of the extension side leaf valve Ve and the extension side annular plate 66. For this reason, when the extension side leaf valve Ve and the extension side annular plate 66 are bent by the pressure of the extension side passage 3, the outer peripheral side is more easily bent than the auxiliary valve 71.
- the damping characteristic of the extension side damping force can be tuned by changing the outer diameter of the auxiliary valve 71. If the auxiliary valve 71 is unnecessary due to the damping characteristic generated in the shock absorber D, it may be eliminated. If necessary, a plurality of auxiliary valves 71 may be stacked.
- the extension side chamber 12 includes a cylindrical mounting portion 12a fitted to the outer periphery of the holding shaft 8a of the piston holding member 8, a flange portion 12b provided on the outer periphery of the lower end in FIG. 3 of the mounting portion 12a, and a flange portion.
- a sliding contact cylinder 12c extending from the outer periphery of 12b toward the piston 2 side, an annular groove 12d provided on the inner periphery of the mounting portion 12a, and a notch 12e communicating from the outer periphery of the mounting portion 12a to the annular groove 12d.
- the annular groove 12d faces the compression side pilot orifice Pp provided on the holding shaft 8a.
- An extension side stopper 67 is interposed between the mounting portion 12 a of the extension side chamber 12 and the collar 65.
- the lower limit of movement of the extension side annular plate 66 may be regulated by eliminating the extension side stopper 67 and causing the mounting portion 12a to function as a stopper.
- the expansion side spool Se is accommodated in the sliding tube 12c.
- the extension-side spool Se is in sliding contact with the inner periphery of the sliding contact cylinder 12c, and can move in the axial direction within the sliding contact cylinder 12c.
- the extension-side spool Se includes an annular spool body 13 and an annular protrusion 14 that rises from the inner periphery of the upper end of the spool body 13 in FIG.
- the inner diameter of the annular protrusion 14 is set to be smaller than the outer diameter of the extended-side annular plate 66, and the annular protrusion 14 can abut on the lower surface in FIG.
- the expansion side back pressure chamber Ce is formed on the lower side in FIG. 3, which is the back side of the expansion side leaf valve Ve.
- the inner diameter of the spool body 13 may be set to a diameter that is in sliding contact with the outer periphery of the mounting portion 12 a, and the extension-side back pressure chamber Ce may be partitioned by the extension-side spool Se and the extension-side chamber 12.
- the annular groove 12d faces the compression side pilot orifice Pp provided in the holding shaft 8a, so that the extension side back pressure chamber Ce includes the notch 12e and the annular groove. It communicates with the pressure side pilot orifice Pp through 12d.
- the expansion side chamber 12 is provided with a pressure side pressure introduction passage Ip that opens to the outer periphery of the flange portion 12b.
- the pressure side pressure introduction passage Ip is a communication passage that connects the pressure side chamber R2 and the extension side back pressure chamber Ce.
- An annular plate 15 is stacked above the flange portion 12b of the extension side chamber 12 in FIG. The annular plate 15 is pressed against the flange portion 12b by the annular plate 15 and the spring member 16 interposed between the spool body 13 and the annular plate 15, and closes the pressure side pressure introduction passage Ip.
- the pressure side pressure introduction passage Ip is designed not to give resistance to the flow of the passing liquid.
- the annular plate 15 When the shock absorber D is contracted, the annular plate 15 is pressed by the pressure of the pressure side chamber R2 which is higher than the extension side back pressure chamber Ce and is separated from the flange portion 12b to open the pressure side pressure introduction passage Ip. When the shock absorber D is extended, the pressure side pressure introduction passage Ip is closed by being pressed against the flange portion 12b by the pressure in the extension side back pressure chamber Ce that is higher than the pressure side chamber R2. As described above, the annular plate 15 functions as a valve body of the pressure-side check valve Tp that allows only the liquid flow from the pressure-side chamber R2. By providing the pressure-side check valve Tp, the pressure-side pressure introduction passage Ip becomes a one-way passage that allows only the flow of liquid from the pressure-side chamber R2 to the extension-side back pressure chamber Ce.
- the spring member 16 that presses the annular plate 15 against the flange portion 12 b constitutes a compression side check valve Tp together with the annular plate 15. Further, the spring member 16 also plays a role of urging the expansion side spool Se toward the expansion side leaf valve Ve. Even if the bending of the expansion side leaf valve Ve is eliminated after the expansion side leaf valve Ve is bent and the expansion side spool Se is pushed downward in FIG. Is urged toward the expansion side leaf valve Ve by the spring member 16, and thus quickly returns to the original position (position shown in FIG. 3) following the expansion side leaf valve Ve.
- the extension side spool Se can be urged by a spring member different from the spring member 16, but the number of parts can be reduced and the structure can be reduced by sharing the spring member 16 with the compression side check valve Tp. It can be simplified.
- the outer diameter of the extension side spool Se is set to be larger than the inner diameter of the annular protrusion 14 that contacts the extension side annular plate 66. Therefore, the extension side spool Se is always driven by the pressure in the extension side back pressure chamber Ce. It is urged toward the extension side leaf valve Ve.
- the pressure side leaf valve Vp stacked above the piston 2 is annular in order to allow the holding shaft 8 a of the piston holding member 8 to be inserted, as with the extension side leaf valve Ve.
- the compression side leaf valve Vp is configured by a single annular plate.
- the compression side leaf valve Vp may be configured by a plurality of stacked annular plates.
- the pressure-side leaf valve Vp configured in this way is stacked above the piston 2 in FIG. 3 via a pressure-side annular spacer 60 that is stacked on the inner peripheral seat portion 2 f of the piston 2.
- the pressure side leaf valve Vp has a notch Op on its outer periphery that functions as an orifice when seated on the pressure side valve seat 2c.
- the compression side leaf valve Vp is slidably mounted on the outer periphery of the collar 61.
- a pressure side annular plate 62 stacked on the pressure side leaf valve Vp is slidably mounted on the outer periphery of the collar 61.
- an annular auxiliary valve 81 having an outer diameter smaller than that of the pressure side annular plate 62 is laminated.
- the auxiliary valve 81 is also slidably mounted on the outer periphery of the collar 61.
- the axial length when the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 are stacked is set to be shorter than the axial length of the collar 61.
- a pressure side stopper 63 that is annular and has an outer diameter set larger than the inner diameter of the auxiliary valve 81 and the pressure side annular plate 62 is provided above the pressure side stopper 63. Above the pressure side stopper 63, a pressure side chamber 11 described later is disposed.
- the pressure-side leaf valve Vp, the pressure-side annular plate 62, and the auxiliary valve 81 are guided by a collar 61 as a shaft member, and move between the pressure-side annular spacer 60 and the pressure-side stopper 63 in the vertical direction in FIG. be able to.
- the pressure-side leaf valve Vp is pressed by pressure from the pressure-side passage 4 side, so that the outer periphery can be bent together with the pressure-side annular plate 62 and can be retracted from the piston 2 together with the pressure-side annular plate 62 and the auxiliary valve 81. .
- the retraction amounts of the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 from the piston 2 are set by the axial length of the collar 61. Since the collar 61 is composed of a plurality of annular plates, the axial length of the collar 61 can be adjusted by changing the number of annular plates to be stacked.
- the collar 61 is not limited to a plurality of annular plates, and may be a single annular plate.
- the pressure side leaf valve Vp is stacked above the piston 2 in FIG. 3 via the pressure side annular spacer 60 stacked on the inner peripheral seat portion 2f of the piston 2.
- a gap is formed between the pressure side leaf valve Vp and the pressure side valve seat 2c.
- the vertical length of this gap in FIG. 3 can be adjusted by exchanging the pressure side annular spacer 60 with a different thickness or changing the number of stacked pressure side annular spacers 60.
- the clearance between the pressure side leaf valve Vp and the pressure side valve seat 2c eliminates the pressure side annular spacer 60 by making the height of the inner peripheral seat portion 2f higher than the height of the pressure side valve seat 2c.
- the compression-side leaf valve Vp can also be formed by directly laminating the inner peripheral seat portion 2f. However, the size of the gap can be easily adjusted by providing the pressure side annular spacer 60.
- the pressure side leaf valve Vp bends when an urging force is applied by the urging mechanism from the opposite side of the piston 2 on the back side, and seats on the pressure side valve seat 2c when the urging force increases, thereby closing the pressure side passage 4. To do. In this state, the pressure side passage 4 and the extension side chamber R1 communicate with each other only through the notch Op.
- the pressure side annular plate 62 is set to have higher bending rigidity than the pressure side leaf valve Vp. Therefore, the axial length (thickness) of the compression side annular plate 62 is longer than the axial length (thickness) of the compression side leaf valve Vp.
- the pressure side annular plate 62 may be formed of a material having higher rigidity than the pressure side leaf valve Vp as well as increasing the rigidity by the axial length.
- the inner diameter of the compression side annular plate 62 is set to be smaller than the outer diameter of the inner peripheral sheet portion 2 f provided in the piston 2.
- the outer diameter of the pressure side annular plate 62 is set larger than the inner diameter of the pressure side valve seat 2c.
- the pressure side annular plate 62 has the inner peripheral seat portion 2f, the pressure side valve seat 2c, Supported by For this reason, the pressure in the pressure-side back pressure chamber Cp and the urging force by the pressure-side spool Sp are received by the pressure-side annular plate 62, and no overload acts on the pressure-side leaf valve Vp, and the pressure-side leaf valve Vp is further deformed. It is suppressed.
- the auxiliary valve 81 has an outer diameter smaller than that of the pressure side leaf valve Vp and the pressure side annular plate 62. For this reason, when the pressure side leaf valve Vp and the pressure side annular plate 62 are bent by the pressure of the pressure side passage 4, the outer peripheral side is more easily bent than the auxiliary valve 81.
- the damping characteristic of the compression side damping force can be tuned. If the auxiliary valve 81 is unnecessary due to the damping characteristic generated in the shock absorber D, it may be eliminated. If necessary, a plurality of auxiliary valves 81 may be stacked.
- the compression side chamber 11 includes a cylindrical mounting portion 11a fitted to the outer periphery of the holding shaft 8a of the piston holding member 8, a flange portion 11b provided on the outer periphery of the upper end in FIG. 3 of the mounting portion 11a, and a flange portion 11b.
- a sliding contact cylinder 11c extending from the outer periphery of the mounting portion 11a toward the piston 2, an annular groove 11d provided on the inner periphery of the mounting portion 11a, and a notch 11e communicating from the outer periphery of the mounting portion 11a to the annular groove 11d.
- the annular groove 11d faces the expansion side pilot orifice Pe provided on the holding shaft 8a.
- a pressure side stopper 63 is interposed between the mounting portion 11 a of the pressure side chamber 11 and the collar 61.
- the upper limit of the movement of the pressure side annular plate 62 may be regulated by eliminating the pressure side stopper 63 and causing the mounting portion 11a to function as a stopper.
- the pressure side spool Sp is accommodated in the sliding tube 11c.
- the outer periphery of the compression side spool Sp is in sliding contact with the inner periphery of the sliding contact cylinder 11c, and can move in the axial direction within the sliding contact cylinder 11c.
- the pressure-side spool Sp includes an annular spool body 17 and an annular protrusion 18 that rises from the outer periphery of the lower end of the spool body 17 in FIG.
- the inner diameter of the annular protrusion 18 is set to be smaller than the outer diameter of the pressure side annular plate 62, and the annular protrusion 18 can abut on the upper surface in FIG.
- a pressure side back pressure chamber Cp is formed on the upper side in FIG. 3, which is the back side of the pressure side leaf valve Vp.
- the inner diameter of the spool body 17 may be set to a diameter that is in sliding contact with the outer periphery of the mounting portion 11 a, and the compression-side back pressure chamber Cp may be partitioned by the compression-side spool Sp and the compression-side chamber 11.
- the annular groove 11d is opposed to the expansion side pilot orifice Pe provided on the holding shaft 8a, so that the pressure side back pressure chamber Cp is provided with the notch 11e and the annular groove 11d. And communicates with the extension pilot orifice Pe.
- the compression-side back pressure chamber Cp communicates with the expansion-side back pressure chamber Ce through the communication passage 24 formed in the vertical hole 8d of the holding shaft 8a and the compression-side pilot orifice Pp by communicating with the expansion-side pilot orifice Pe.
- the compression side chamber 11 is provided with an extension side pressure introduction passage Ie that opens to the outer periphery of the flange portion 11b.
- the extension side pressure introduction passage Ie is a passage that allows the extension side chamber R1 and the compression side back pressure chamber Cp to communicate with each other.
- An annular plate 19 is laminated below the flange portion 11b of the compression side chamber 11 in FIG. The annular plate 19 is pressed against the flange portion 11b by the annular plate 19 and the spring member 20 interposed between the spool body 17 and the annular plate 19, and closes the extension-side pressure introduction passage Ie.
- the expansion side pressure introduction passage Ie is designed so as not to provide resistance to the flow of the passing liquid.
- the annular plate 19 When the shock absorber D is extended, the annular plate 19 is pressed by the pressure of the expansion side chamber R1 which is higher than the compression side back pressure chamber Cp and is separated from the flange portion 11b to open the expansion side pressure introduction passage Ie.
- the shock absorber D When the shock absorber D is contracted, it is pressed against the flange portion 11b by the pressure in the compression side back pressure chamber Cp that is higher than the expansion side chamber R1, and closes the expansion side pressure introduction passage Ie.
- the annular plate 19 functions as a valve body of the extension-side check valve Te that allows only the liquid flow from the extension-side chamber R1.
- the extension side pressure introduction passage Ie becomes a one-way passage that allows only the flow of liquid from the extension side chamber R1 toward the compression side back pressure chamber Cp.
- the communication passage 24 communicates with the inside of the accommodating portion L through the annular groove 8e, the port 8f, and the lateral hole 8g provided in the piston holding member 8. Therefore, the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp are not only communicated with each other through the extension side pilot orifice Pe, the compression side pilot orifice Pp and the communication passage 24, but also through the extension side pressure introduction passage Ie. It communicates with R1, communicates with the pressure side chamber R2 through the pressure side pressure introduction passage Ip, and further communicates with the accommodating portion L through the port 8f and the lateral hole 8g.
- the spring member 20 that presses the annular plate 19 against the flange portion 11 b constitutes an extension check valve Te together with the annular plate 19.
- the spring member 20 also plays a role of urging the pressure side spool Sp toward the pressure side leaf valve Vp. Even if the bending of the pressure side leaf valve Vp is eliminated after the pressure side leaf valve Vp is bent and the pressure side spool Sp is pushed upward in FIG. Since it is urged toward the pressure side leaf valve Vp by 20, it quickly returns to the original position (position shown in FIG. 3) following the pressure side leaf valve Vp.
- the pressure side spool Sp can be urged by a spring member different from the spring member 20, but the number of parts can be reduced and the structure can be reduced by sharing the spring member 20 with the extension side check valve Te. It can be simplified. Since the outer diameter of the pressure side spool Sp is set to be larger than the inner diameter of the annular protrusion 18 that contacts the pressure side annular plate 62, the pressure side spool Sp is always pressed by the pressure of the pressure side back pressure chamber Cp. It is energized towards. For this reason, if it is a spring member aiming at energizing only pressure side spool Sp, it is not necessary to install.
- the extension side spool Se receives the pressure of the extension side back pressure chamber Ce and biases the extension side leaf valve Ve toward the piston 2 via the extension side annular plate 66.
- the pressure receiving area of the expansion side spool Se that receives the pressure of the expansion side back pressure chamber Ce is a difference between the area of a circle whose diameter is the outer diameter of the expansion side spool Se and the area of the circle whose diameter is the inner diameter of the annular protrusion 14. .
- the pressure side spool Sp receives the pressure of the pressure side back pressure chamber Cp and urges the pressure side leaf valve Vp toward the piston 2 via the pressure side annular plate 62.
- the pressure receiving area of the pressure side spool Sp that receives the pressure of the pressure side back pressure chamber Cp is a difference between the area of a circle whose diameter is the outer diameter of the pressure side spool Sp and the area of the circle whose diameter is the inner diameter of the annular protrusion 18.
- the pressure receiving area of the expansion side spool Se is set larger than the pressure receiving area of the compression side spool Sp.
- the annular protrusion 14 of the expansion side spool Se is in contact with the back surface of the expansion side annular plate 66, and the inner peripheral side of the expansion side annular plate 66 is attached to the outer periphery of the collar 65.
- the pressure receiving area where the pressure of the extension side back pressure chamber Ce acts directly on the extension side annular plate 66 is a circle whose diameter is the outer diameter of the collar 65 from the area of the circle whose diameter is the inner diameter of the annular protrusion 14. It is an area excluding the area.
- the annular protrusion 18 of the compression side spool Sp is in contact with the back surface of the compression side annular plate 62, and the inner peripheral side of the compression side annular plate 62 is attached to the outer periphery of the collar 61.
- the pressure receiving area where the pressure of the pressure side back pressure chamber Cp directly acts on the pressure side annular plate 62 is the area of the circle whose diameter is the outer diameter of the collar 61 from the area of the circle whose diameter is the inner diameter of the annular protrusion 18. The area is excluded.
- the pressure side leaf valve Vp is urged toward the piston 2 by the pressure side load.
- the pressure side annular plate 62 may be eliminated, and the annular protrusion 18 may be brought into direct contact with the back surface of the pressure side leaf valve Vp.
- the pressure side leaf valve Vp since the pressure side leaf valve Vp is mounted on the outer periphery of the collar 61, the pressure side load acts on the pressure side leaf valve Vp as in the case where the pressure side annular plate 62 is provided.
- the extension side load which is the load that the extension side leaf valve Ve receives from the extension side back pressure chamber Ce
- Vp is set to be larger than the compression side load that is the load received from the compression side back pressure chamber Cp.
- the pressure-side load receives the pressure in the pressure-side back pressure chamber Cp. It depends only on the pressure receiving area.
- the extension side leaf valve Ve receives the extension side load received from the extension side back pressure chamber Ce, and the compression side leaf valve Vp uses the compression side back pressure chamber.
- the pressure receiving area of the expansion side spool Se is set to the compression side spool Sp. It may be larger than the pressure receiving area.
- the expansion-side annular plate 66 and the compression-side annular plate 62 are abolished, and the pressure in the expansion-side back pressure chamber Ce is directly applied to the expansion-side leaf valve Ve, so The leaf valve Vp may be directly acted on.
- the extension side spool Se contacts the extension side leaf valve Ve
- the compression side back pressure chamber Cp is closed by the compression side spool Sp
- the pressure side spool Sp contacts the pressure side leaf valve Vp.
- the pressure receiving area where the pressure of the extension side back pressure chamber Ce substantially acts can be set larger than the pressure receiving area of only the extension side leaf valve Ve. it can.
- the pressure receiving area difference between the compression side spool Sp and the expansion side spool Se can be set large, it is possible to give a large difference between the expansion side load and the compression side load.
- the range in which can be set can be expanded.
- the extension side leaf valve Ve When the shock absorber D is extended, the extension side leaf valve Ve receives the pressure from the extension side chamber R1 through the extension side passage 3 and receives the extension side load from the back side. When the extension side load exceeds the force pushed down by the pressure of the extension side chamber R1, the extension side leaf valve Ve bends until it contacts the extension side valve seat 2d and closes the extension side passage 3. At a certain piston speed when the shock absorber D is extended, the extension side load when the extension side leaf valve Ve closes the extension side passage 3 is the pressure receiving area, the extension of the pressure of the extension side back pressure chamber Ce. It can be set by the flexural rigidity of the side leaf valve Ve and the extension side annular plate 66.
- the compression side leaf valve Vp is a compression side back pressure at a certain piston speed when the shock absorber D is contracted and the compression side leaf valve Vp closes the compression side passage 4.
- the pressure can be set by the pressure receiving area where the pressure of the chamber Cp acts, the bending rigidity of the pressure side leaf valve Vp and the pressure side annular plate 62, and the like.
- the electromagnetic pressure control valve 6 is provided in an adjustment passage Pc that connects the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp upstream and the extension-side discharge passage Ee and pressure-side discharge passage Ep downstream.
- the electromagnetic pressure control valve 6 can control the pressure in the upstream extension side back pressure chamber Ce and pressure side back pressure chamber Cp.
- the extension side load is larger than the compression side load. For this reason, even when a large extension side load is required, it is not necessary to increase the pressure in the extension side back pressure chamber Ce so much. Therefore, even when it is desired to increase the damping force on the extension side, the maximum pressure that should be controlled by the electromagnetic pressure control valve 6 can be kept low.
- the extension side back pressure chamber Ce is on the back side of the extension side leaf valve Ve and is an annular protrusion. It acts on the inner side of the part where 14 abuts, and energizes the extension side leaf valve Ve.
- the extension side load is set in consideration of the urging load caused by the pressure of the extension side back pressure chamber Ce acting directly on the extension side leaf valve Ve.
- the pressure side load is set in consideration of the urging load caused by the pressure of the pressure side back pressure chamber Cp acting directly on the pressure side leaf valve Vp.
- the electromagnetic pressure control valve 6 is set to close the adjustment passage Pc when not energized and perform pressure control when energized.
- the adjustment passage Pc is provided with a fail valve FV that bypasses the electromagnetic pressure control valve 6 and can communicate with the upstream and the downstream.
- the electromagnetic pressure control valve 6 includes a valve seat member 30 having a valve housing cylinder 30a and a control valve valve seat 30d, and an electromagnetic valve body 31 that is attached to and detached from the control valve valve seat 30d. And a solenoid Sol that applies thrust to the solenoid valve body 31 to drive the valve body 31 in the axial direction.
- valve seat member 30 is inserted into the socket 8c of the piston holding member 8 and is inserted into the inner periphery of an annular valve housing 32 stacked above the flange 8b in FIG. It is accommodated in the accommodating part L, being positioned in the direction.
- the valve housing 32 is an annular member, and includes an annular window 32a formed at the upper end in FIG. 2, a port 32b that opens to the annular window 32a and communicates with the lower end in FIG. A notch groove 32c that opens to the inner periphery of the upper end in 2 and communicates with the port 32b, a groove 32d that is formed on the outer peripheral surface along the axial direction, an annular fail valve seat 32e that surrounds the outer periphery of the annular window 32a, Is provided.
- the port 32b faces the open end of the port 8f, and the port 32b and the cutout groove 32c communicate with the port 8f.
- the groove 32d faces the groove 8j provided in the flange 8b, and the groove 32d communicates with the groove 8j.
- the port 32b and the cutout groove 32c communicate with the communication path 24 through the port 8f, the annular groove 8e, and the lateral hole 8g.
- the port 32b and the notch groove 32c communicate with the expansion side back pressure chamber Ce and the pressure side back pressure chamber Cp through the communication passage 24, the expansion side pilot orifice Pe and the pressure side pilot orifice Pp.
- the groove 32d communicates with the pressure side chamber R2 in the separator 23 through the groove 8j and through the extension side discharge passage Ee in which the check valve 25 is provided, and through the through hole 9c, the recess 8k, the through hole 8m, and the check valve 22. It communicates with the extension side chamber R1 through the configured pressure side discharge passage Ep.
- valve accommodating cylinder 30a of the cylindrical valve seat member 30 is accommodated.
- the valve seat member 30 has a bottomed cylindrical shape, and a valve accommodating cylinder 30a provided with a flange 30b on the outer periphery of the upper end in FIG. 2; a through hole 30c that opens to the side of the valve accommodating cylinder 30a and communicates with the inside;
- An annular control valve seat 30d that protrudes in the axial direction is provided at the upper end in FIG. 2 of the valve housing cylinder 30a.
- a fail valve body 33 which is an annular leaf valve is provided on the outer periphery of the valve housing cylinder 30a of the valve seat member 30, a fail valve body 33 which is an annular leaf valve is provided.
- the fail valve body 33 is fixed by being sandwiched between the flange 30b of the valve seat member 30 and the inner periphery of the upper end of the valve housing 32 in FIG. .
- the outer peripheral side of the fail valve body 33 is seated in a state where initial deflection is given to an annular fail valve valve seat 32e provided in the valve housing. For this reason, the annular window 32 a is closed by the fail valve body 33.
- the fail valve body 33 bends when the pressure acting in the annular window 32a reaches the valve opening pressure through the port 32b, opens the annular window 32a, and communicates the port 32b with the expansion side discharge passage Ee and the pressure side discharge passage Ep.
- the fail valve FV includes a fail valve body 33 and a fail valve valve seat 32e.
- valve seat member 30 when the valve seat member 30 is assembled to the valve housing 32, the notch groove 32c formed in the valve housing 32 and the through hole 30c formed in the valve accommodating cylinder 30a face each other. For this reason, the expansion side back pressure chamber Ce and the pressure side back pressure chamber Cp communicate with the inside of the valve accommodating cylinder 30a through the port 32b.
- valve fixing member 35 which is annular and contacts the upper end of the flange 30b in FIG.
- solenoid Sol accommodated in the electromagnetic valve accommodating cylinder 9 is disposed above the valve fixing member 35 in FIG.
- the valve housing 32, the fail valve valve body 33, the valve seat member 30, the valve fixing member 35, and the solenoid Sol are connected to the solenoid valve housing cylinder 9 and the piston holding when the piston holding member 8 is screwed to the solenoid valve housing cylinder 9. It is clamped between the members 8 and fixed.
- the valve fixing member 35 includes a space on the inner peripheral side of the valve fixing member 35 and a space on the outer peripheral side of the valve seat member 30. Is provided with a notch groove 35a.
- the passage that connects the space on the inner peripheral side of the valve fixing member 35 and the space on the outer peripheral side of the valve seat member 30 is not limited to the notch groove 35a, and may be a through hole such as a port.
- the solenoid Sol is a top-cylindrical molded stator 36 in which a winding 37 and a harness H that energizes the winding 37 are integrated with a mold resin, and a top-cylindrical cylindrical stator that is fitted to the inner periphery of the mold stator 36.
- the first fixed iron core 38, the annular second fixed iron core 39 disposed in contact with the lower end in FIG. 1 of the molded stator 36, and the first fixed iron core 38 and the second fixed iron core 39 are interposed.
- a filler ring 40 that is mounted to form a magnetic gap, a cylindrical movable core 41 that is axially movable on the inner peripheral side of the first fixed core 38 and the second fixed core 39, and the movable core 41 And a shaft 42 fixed to the inner periphery of the shaft.
- a solenoid valve body 31 is slidably inserted into the valve seat member 30.
- the solenoid valve body 31 is opposite to the small-diameter portion 31a slidably inserted into the valve housing cylinder 30a of the valve seat member 30 and the valve seat member 30 side which is the upper side of the small-diameter portion 31a in FIG.
- a seating portion 31g facing the control valve valve seat 30d is provided at the lower end in FIG. 2 of the large-diameter portion 31b of the solenoid valve body 31.
- the seat portion 31g is seated on and off the control valve valve seat 30d. That is, when the seating portion 31g of the solenoid valve body 31 is seated on the control valve seat 30d of the valve seat member 30, the solenoid pressure control valve 6 is closed.
- a coil spring 34 is interposed between the flange 30b of the valve seat member 30 and the spring receiving portion 31d to urge the electromagnetic valve valve body 31 in a direction away from the valve seat member 30.
- the solenoid Sol exhibits a thrust that opposes the biasing force of the coil spring 34. Therefore, the electromagnetic valve body 31 is always urged in the direction away from the valve seat member 30 by the coil spring 34, and if the thrust against the coil spring 34 is not applied from the solenoid Sol, It is held at a separated position.
- the means for urging the electromagnetic valve body 31 in the direction away from the valve seat member 30 is not limited to the coil spring 34, and may be an elastic body capable of exerting a sufficient urging force.
- the small diameter portion 31a faces the through hole 30c, and thus the through hole 30c is closed.
- the solenoid valve body 31 is moved a predetermined amount from the position farthest away from the valve seat member 30 to the valve seat member 30 by energizing the solenoid Sol, the recess 31c always faces the through hole 30c. 30c is opened.
- the through hole 30c is provided in the recess 31c of the solenoid valve body 31 and the valve fixing member 35.
- the extended side discharge passage Ee and the pressure side discharge passage Ep communicate with each other through the cutout groove 35a.
- the electromagnetic pressure control valve 6 enters a valve open state in which the seating portion 31g and the control valve valve seat 30d are separated.
- the pressure on the upstream side of the electromagnetic pressure control valve 6 can be controlled by adjusting the thrust of the solenoid Sol. Since the upstream side of the electromagnetic pressure control valve 6 communicates with the expansion side back pressure chamber Ce and the pressure side back pressure chamber Cp via the adjustment passage Pc, the electromagnetic pressure control valve 6 causes the expansion side back pressure chamber Ce and the pressure side back pressure chamber Cp to communicate with each other. The pressure in the pressure chamber Cp can be controlled.
- the downstream of the electromagnetic pressure control valve 6 communicates with the expansion side discharge passage Ee and the pressure side discharge passage Ep, and the liquid that has passed through the electromagnetic pressure control valve 6 has a low pressure when the hydraulic pressure buffer D is operating to extend.
- the pressure side chamber R2 is discharged to the low pressure side extension side chamber R1.
- the adjustment passage Pc is formed by the annular groove 8e, the port 8f, the lateral hole 8g, the port 32b, the notch groove 32c, a part of the accommodating portion L, and the groove 32d.
- the electromagnetic pressure control valve 6 has a blocking position in which the through hole 30c of the valve seat member 30 is closed by the small diameter portion 31a of the electromagnetic valve valve body 31 during a failure in which the solenoid Sol cannot be energized.
- the electromagnetic pressure control valve 6 functions not only as a pressure control valve but also as an on-off valve.
- the fail valve FV is configured to open and close an annular window 32a leading to the port 32b.
- the valve opening pressure of the fail valve FV is set to a pressure exceeding the upper limit pressure that can be controlled by the electromagnetic pressure control valve 6. For this reason, when the pressure on the upstream side of the electromagnetic pressure control valve 6 exceeds the upper limit pressure, the fail valve FV opens, and the port 32b bypasses the electromagnetic pressure control valve 6 and extends to the expansion side discharge passage Ee and the pressure side. It communicates with the discharge passage Ep.
- the pressures in the extension side back pressure chamber Ce and the pressure side back pressure chamber Cp are controlled to the valve opening pressure of the fail valve FV. Therefore, at the time of a failure in which the electromagnetic pressure control valve 6 is in the cutoff position, the pressures in the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp are controlled by the fail valve FV.
- a space K is formed on the tip side of the through hole 30c in the valve accommodating cylinder 30a.
- the space K communicates with the outside of the electromagnetic valve valve body 31 through a communication path 31e and an orifice 31f provided in the electromagnetic valve valve body 31.
- the damping force characteristic of the damping force of the shock absorber D is made soft, that is, when the urging force for urging the extension side leaf valve Ve and the pressure side leaf valve Vp by the urging mechanism is made small and the damping coefficient is made low.
- the solenoid Sol is energized so that the resistance that the electromagnetic pressure control valve 6 gives to the liquid passing through the adjustment passage Pc becomes small.
- the urging force provided by the urging mechanism is reduced so that the extension side leaf valve Ve and the pressure side leaf valve Vp do not seat on the corresponding extension side valve seat 2d and pressure side valve seat 2c, respectively.
- extension side leaf valve Ve can slide on the outer periphery of the collar 65. For this reason, the expansion side leaf valve Ve moves backward from the piston 2 together with the expansion side annular plate 66 and the auxiliary valve 71 due to the pressure in the expansion side chamber R ⁇ b> 1 rising as the shock absorber D extends. As a result, the gap between the extension side leaf valve Ve and the extension side valve seat 2d becomes large.
- the size of the gap between the extension side leaf valve Ve and the extension side valve seat 2d is determined by the force that the pressure in the extension side chamber R1 received from the extension side passage 3 side attempts to retract the extension side leaf valve Ve from the piston 2. It is determined by the balance with the extension side load by the urging mechanism.
- the extension side leaf valve Ve In order to reduce the damping force when the damping force characteristic is soft, it is necessary to reduce the rigidity of the extension side leaf valve Ve as much as possible.
- the extension side leaf valve Ve must have a rigidity enough to withstand a large extension side load by the urging mechanism, and there is a limit to reducing the rigidity.
- the extension side leaf valve Ve In the present shock absorber D, a gap is formed between the extension side leaf valve Ve and the extension side valve seat 2d, and the extension side leaf valve Ve may further be retracted from the piston 2. it can. For this reason, it is possible to secure a large flow path area between the extension side leaf valve Ve and the extension side valve seat 2d while ensuring the rigidity required for the extension side leaf valve Ve.
- the shock absorber D has a line against the damping force generated by the conventional shock absorber indicated by the line A as shown in FIG.
- the damping force characteristic is soft, a very small slope of the damping coefficient can be realized, and the damping force can be greatly reduced.
- the extension speed of the shock absorber D is further increased and the pressure in the expansion side chamber R1 is increased, the retraction amount of the expansion side leaf valve Ve from the piston 2 is further increased.
- the auxiliary valve 71 comes into contact with the expansion side stopper 67, further retreat of the expansion side leaf valve Ve is restricted.
- the expansion-side leaf valve Ve is restricted from moving in the axial direction on the inner peripheral side by contacting the expansion-side stopper 67. For this reason, the outer peripheral side of the extension side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 is bent with the outer peripheral end of the extension side stopper 67 as a fulcrum, and the extension side passage 3 is further opened.
- the amount of bending at this time is determined according to the force by which the pressure in the extending side chamber R1 received from the extending side passage 3 side tends to bend the extending side leaf valve Ve, the extending side annular plate 66 and the auxiliary valve 71, and the amount of bending. It is determined by the balance between the force of the side leaf valve Ve, the extension side annular plate 66 and the auxiliary valve 71 returning to the extension side valve seat 2d by the spring reaction force generated by itself and the extension side load by the urging mechanism.
- the liquid in the extension side chamber R1 pushes open the extension side check valve Te, passes through the extension side pressure introduction passage Ie, and flows into the adjustment passage Pc.
- the liquid that has passed through the adjustment passage Pc pushes the check valve 25 open and is discharged to the low pressure side pressure side chamber R2 through the expansion side discharge passage Ee.
- the extension pilot orifice Pe provides resistance when the liquid passes and causes a pressure loss, and the pressure is lower than that of the extension side chamber R1 downstream of the adjustment passage Pc when the liquid is flowing. For this reason, the check valve 22 provided in the pressure side discharge passage Ep is not opened and remains closed.
- extension side pressure introduction passage Ie not only leads to the compression side back pressure chamber Cp but also leads to the extension side back pressure chamber Ce through the communication passage 24. For this reason, when the shock absorber D is extended, the pressure in the extension-side back pressure chamber Ce becomes higher than the pressure-side chamber R2, and the pressure-side pressure introduction passage Ip is closed by the pressure-side check valve Tp.
- the pressure in the pressure side back pressure chamber Cp is higher than that in the pressure side chamber R2 on the low pressure side, but there is no inconvenience because it only energizes the pressure side leaf valve Vp that closes the pressure side passage 4 where no liquid flows. .
- the pressure in the extension side back pressure chamber Ce is controlled by adjusting the pressure on the upstream side of the adjustment passage Pc by energizing the solenoid Sol of the electromagnetic pressure control valve 6 provided in the adjustment passage Pc.
- the extension side load can be controlled to a desired magnitude by adjusting the energization amount to the solenoid Sol.
- the opening degree of the extension side leaf valve Ve can be controlled by the electromagnetic pressure control valve 6, and the extension side damping force when the shock absorber D is extended can be controlled.
- the pressure side leaf valve Vp can slide on the outer periphery of the collar 61. For this reason, the pressure side leaf valve Vp moves backward from the piston 2 together with the pressure side annular plate 62 and the auxiliary valve 81 due to the pressure in the pressure side chamber R ⁇ b> 2 rising as the shock absorber D contracts. As a result, the gap between the pressure side leaf valve Vp and the pressure side valve seat 2c becomes large.
- the size of the gap between the pressure-side leaf valve Vp and the pressure-side valve seat 2c depends on the force of the pressure-side chamber R2 received from the pressure-side passage 4 side and the force that causes the pressure-side leaf valve Vp to retreat from the piston 2. It is determined by the balance with the compression side load.
- the compression side leaf valve Vp in order to reduce the damping force when the damping force characteristic is soft, it is necessary to reduce the rigidity of the compression side leaf valve Vp as much as possible.
- the compression side leaf valve Vp like the extension side leaf valve Ve, the compression side leaf valve Vp must have a rigidity sufficient to withstand a large pressure side load by the urging mechanism, and there is a limit to reducing the rigidity.
- this shock absorber D a gap is formed between the pressure side leaf valve Vp and the pressure side valve seat 2c, and the entire pressure side leaf valve Vp can be retracted from the piston 2. For this reason, it is possible to ensure a large flow path area between the pressure side leaf valve Vp and the pressure side valve seat 2c while ensuring the rigidity required for the pressure side leaf valve Vp.
- the shock absorber D has a line D against the damping force generated by the conventional shock absorber indicated by the line C as shown in FIG.
- the damping force characteristic is made soft, an extremely small inclination of the damping coefficient can be realized, and the damping force can be greatly reduced.
- the contraction speed of the shock absorber D is further increased and the pressure in the pressure side chamber R2 is increased, the retreat amount of the pressure side leaf valve Vp from the piston 2 is further increased.
- the auxiliary valve 81 comes into contact with the pressure side stopper 63, further retreat of the pressure side leaf valve Vp is restricted.
- the pressure side leaf valve Vp is restricted from moving in the axial direction on the inner peripheral side by contacting the pressure side stopper 63. Therefore, the outer peripheral side of the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81 is bent with the outer peripheral end of the pressure side stopper 63 as a fulcrum, and the pressure side passage 4 is further opened.
- the amount of bending at this time is determined according to the pressure of the pressure side chamber R2 received from the pressure side passage 4 side and the pressure of the pressure side leaf valve Vp, the pressure side annular plate 62 and the auxiliary valve 81, and the pressure side leaf valve Vp according to the amount of bending.
- the pressure-side annular plate 62 and the auxiliary valve 81 are determined by the balance between the force to return to the pressure-side valve seat 2c side by the spring reaction force generated by itself and the pressure-side load by the urging mechanism.
- the liquid in the pressure side chamber R2 pushes and opens the pressure side check valve Tp, passes through the pressure side pressure introduction passage Ip, and flows into the adjustment passage Pc.
- the liquid that has passed through the adjustment passage Pc pushes the check valve 22 open and is discharged to the low-pressure side extension side chamber R1 through the pressure side discharge passage Ep.
- the pressure-side pilot orifice Pp provides resistance when the liquid passes and causes a pressure loss. Therefore, the pressure-side pilot orifice Pp has a lower pressure than the pressure-side chamber R2 downstream of the adjustment passage Pc when the liquid is flowing. For this reason, the check valve 25 provided in the extension side discharge passage Ee does not open and remains closed.
- the pressure side pressure introduction passage Ip not only leads to the extension side back pressure chamber Ce but also leads to the pressure side back pressure chamber Cp through the communication passage 24. For this reason, when the shock absorber D is contracted, the pressure in the compression-side back pressure chamber Cp becomes higher than that of the expansion-side chamber R1, and the expansion-side pressure introduction passage Ie is closed by the expansion-side check valve Te.
- the pressure in the extension side back pressure chamber Ce is higher than that in the extension side chamber R1 on the low pressure side, but it only energizes the extension side leaf valve Ve that closes the extension side passage 3 where no liquid flows. There is no inconvenience.
- the pressure in the pressure side back pressure chamber Cp is controlled by adjusting the pressure on the upstream side of the adjustment passage Pc by energizing the solenoid Sol of the electromagnetic pressure control valve 6 provided in the adjustment passage Pc. That is, the compression side load can be controlled to a desired magnitude by adjusting the energization amount to the solenoid Sol.
- the electromagnetic pressure control valve 6 can control the opening degree of the pressure side leaf valve Vp, and the pressure side damping force when the shock absorber D is contracted can be controlled.
- the damping force characteristic of the damping force of the shock absorber D is made hard, that is, when the urging force for energizing the extension side leaf valve Ve and the pressure side leaf valve Vp by the urging mechanism is increased and the damping coefficient is increased.
- the solenoid Sol is energized so that the resistance that the electromagnetic pressure control valve 6 gives to the liquid passing through the adjustment passage Pc is increased.
- the urging force provided by the urging mechanism is increased so that the extension side leaf valve Ve and the pressure side leaf valve Vp are seated on the corresponding extension side valve seat 2d and pressure side valve seat 2c, respectively.
- extension side leaf valve Ve is bent by the urging mechanism and is seated on the extension side valve seat 2d, and no gap is formed between them.
- pressure side leaf valve Vp is also bent by the urging mechanism so that the pressure side leaf valve Vp is seated on the pressure side valve seat 2c, and no gap is formed between them.
- the extension side leaf valve Ve When the shock absorber D is extended to move the piston 2 upward in FIG. 1 and the piston speed is low, the extension side leaf valve Ve is in the extension side even if it receives the pressure of the extension side chamber R1 from the extension side passage 3.
- the extension side chamber R1 and the pressure side chamber R2 do not separate from the valve seat 2d and communicate with each other only through the notch Oe provided in the extension side leaf valve Ve, except for the adjustment passage Pc.
- the shock absorber D provides resistance to the flow of the liquid passing through the expansion side passage 3 by the notch Oe functioning as an orifice, so that the buffer D is located between the expansion side leaf valve Ve and the expansion side valve seat 2d. Compared with the damping force generated in a state where a gap is formed in the gap, a large damping force can be exhibited.
- the liquid in the extension side chamber R1 pushes open the extension side check valve Te, passes through the extension side pressure introduction passage Ie, and flows into the adjustment passage Pc.
- the pressure on the upstream side of the adjustment passage Pc with the electromagnetic pressure control valve 6 provided in the adjustment passage Pc, the pressure in the extension-side back pressure chamber Ce is adjusted and the extension-side load is adjusted in the same manner as in the soft case. It can be controlled to a desired size.
- the opening degree of the extension side leaf valve Ve by the electromagnetic pressure control valve 6, it is possible to control the extension side damping force when the shock absorber D is extended in the hardware.
- the pressure side leaf valve Vp is pressure side even if it receives the pressure of the pressure side chamber R2 from the pressure side passage 4.
- the pressure side chamber R2 and the extension side chamber R1 do not separate from the valve seat 2c, and communicate with each other only through the notch Op provided in the pressure side leaf valve Vp except for the adjustment passage Pc.
- the shock absorber D provides resistance to the flow of the liquid passing through the pressure side passage 4 by the notch Op functioning as an orifice, so that there is a gap between the pressure side leaf valve Vp and the pressure side valve seat 2c. Compared with the damping force generated in the formed state, a large damping force can be exhibited.
- the liquid in the pressure side chamber R1 pushes open the pressure side check valve Tp, passes through the pressure side pressure introduction passage Ip, and flows to the adjustment passage Pc.
- the pressure on the upstream side of the adjustment passage Pc with the electromagnetic pressure control valve 6 provided in the adjustment passage Pc, the pressure in the compression-side back pressure chamber Cp is adjusted and the pressure-side load is set to a desired value as in the soft case.
- the size can be controlled.
- the gap is formed between the leaf valves Ve and Vp and the valve seats 2c and 2d, and the leaf valves Ve and Vp are entirely pistons. It is possible to retract from 2 in the axial direction. For this reason, while ensuring the rigidity of the leaf valves Ve and Vp, it is possible to increase the flow path area as compared with the conventional damping valve and buffer using the fixed orifice.
- the damping valve and the shock absorber D having the above-described configuration, it is possible to reduce the damping force when the damping force characteristic is soft, and when the damping force characteristic is hard, the leaf valve It is possible to increase the damping force by seating Ve and Vp on the valve seats 2c and 2d. Thus, in the damping valve and the shock absorber D, a variable width of the damping force can be secured.
- the damping valve and the shock absorber of the present embodiment it is possible to reduce the damping force when the damping force characteristic is soft, and to increase the damping force adjustment range.
- the pressure in the extension side back pressure chamber Ce is increased to increase the pressure between the extension side leaf valve Ve and the extension side valve seat 2d.
- the clearance is gradually reduced, and the expansion side leaf valve Ve is seated on the expansion side valve seat 2d.
- the pressure between the pressure side leaf valve Vp and the pressure side valve seat 2c is gradually reduced by increasing the pressure in the pressure side back pressure chamber Cp, and the pressure side leaf valve Vp is seated on the pressure side valve seat 2c.
- the pressure in the extension side back pressure chamber Ce is lowered to reduce the pressure between the extension side leaf valve Ve and the extension side valve seat 2d. Increase the gap gradually.
- the clearance between the pressure side leaf valve Vp and the pressure side valve seat 2c is gradually increased by lowering the pressure in the pressure side back pressure chamber Cp.
- an extension side annular plate 66 that is slidably mounted on the outer periphery of the collar 65 is laminated, and on the back side of the compression side leaf valve Vp, the outer periphery of the collar 61 is slidably mounted.
- the pressure side annular plates 62 are stacked. Since the urging force of the urging mechanism is received by the expansion side annular plate 66 and the pressure side annular plate 62, the rigidity of the expansion side annular plate 66 is made higher than that of the expansion side leaf valve Ve, and the pressure side annular plate 62 is more than the pressure side leaf valve Vp.
- the inner diameter of the extension-side annular plate 66 laminated on the back surface of the extension-side leaf valve Ve is smaller than the outer diameter of the inner peripheral seat portion 2h of the piston 2, and the extension-side annular plate 66 has an outer diameter of the extension-side valve. It is larger than the inner diameter of the seat 2d.
- the inner diameter of the pressure side annular plate 62 laminated on the back surface of the pressure side leaf valve Vp is smaller than the outer diameter of the inner peripheral seat portion 2f of the piston 2, and the outer diameter of the pressure side annular plate 62 is equal to that of the pressure side valve seat 2c. It is larger than the inner diameter.
- the pressure acting on the back side of the extension side leaf valve Ve and the pressure side leaf valve Vp is received by the extension side annular plate 66 and the pressure side annular plate 62. Therefore, by providing the expansion side annular plate 66 and the pressure side annular plate 62, it is possible to prevent an excessive bending force on the piston 2 side from acting on the expansion side leaf valve Ve and the pressure side leaf valve Vp.
- the collars 61 and 65 as the shaft members are laminated with an extension side stopper 67 and a pressure side stopper 63 for regulating the distance in which the leaf valves Ve and Vp and the annular plates 66 and 62 are retracted from the piston 2.
- the thickness and number of the extension side stopper 67 and the pressure side stopper 63 the axial positions of the extension side chamber 12 and the pressure side chamber 11 constituting the biasing mechanism can be adjusted.
- An extension side annular spacer 64 and a pressure side annular spacer 60 are provided between the inner peripheral seat portions 2f and 2h provided on the piston 2 as a valve disk and the extension side leaf valve Ve and the pressure side leaf valve Vp.
- the size of the gap formed between the extension side leaf valve Ve and the compression side leaf valve Vp and the piston 2 is adjusted by changing the thickness and number of the extension side annular spacer 64 and the pressure side annular spacer 60. be able to. As a result, the damping force characteristic of the shock absorber D when soft can be tuned.
- the energizing mechanism energizes the leaf valves Ve and Vp using the pressure of one or both of the extension side chamber R1 and the compression side chamber R2 in the shock absorber D. For this reason, the leaf valves Ve and Vp can be energized without preparing a generation source of the energizing force separately. Further, the urging force can be changed by adjusting the pressure.
- the pressure receiving area that receives the pressure of the expansion side chamber R1 is an area obtained by subtracting the cross sectional area of the rod member 10 from the cross sectional area of the piston 2. Needs to be much larger than the pressure in the compression side chamber R2 during the contraction operation.
- the expansion side load that urges the expansion side leaf valve Ve urges the compression side leaf valve Vp. It is comprised so that it may become larger than the compression side load to do.
- the extension side spool Se is used when the extension side spool Se is used.
- the pressure receiving area of the expansion side spool Se that receives the pressure of the pressure chamber Ce can be made larger than the back surface area of the expansion side leaf valve Ve.
- the extension side back pressure can be increased by increasing the pressure receiving area of the extension side spool Se. Even if the pressure in the chamber Ce is small, a large extension side load can be output. As a result, the control width of the extension side damping force can be ensured without using a large solenoid Sol.
- the pressure control of the extension side back pressure chamber Ce and the pressure control of the pressure side back pressure chamber Cp are performed by driving one electromagnetic valve valve body 31 and each driving independent valve body. It is not done. Further, by setting the extension side load larger than the compression side load, the control range of the extension side damping force can be secured even if the extension side back pressure chamber Ce and the compression side back pressure chamber Cp communicate with each other. In this way, the electromagnetic pressure control valve 6 only needs to be provided with one electromagnetic valve valve body 31, and the structure for controlling the pressure in each of the back pressure chambers Ce and Cp can be greatly simplified. The manufacturing cost of the shock absorber D can be reduced.
- the solenoid Sol in the electromagnetic pressure control valve 6 can be reduced in size, and the structure of the electromagnetic pressure control valve 6 is simplified. For this reason, even if the electromagnetic pressure control valve 6 is applied to the piston portion of the shock absorber D, an increase in the size of the shock absorber D is suppressed. Therefore, according to the present shock absorber D, the structure of the shock absorber D can be simplified and the size can be reduced, and the mounting property on the vehicle can be improved. Furthermore, since the solenoid Sol does not have to exert a large thrust for increasing the extension side damping force, the power consumption when increasing the damping force is reduced and the power can be saved.
- the pressure receiving area for receiving the pressure of the expansion side back pressure chamber Ce of the expansion side spool Se is larger than the pressure receiving area for receiving the pressure of the compression side back pressure chamber Cp of the compression side spool Sp, so that the expansion side load is compared with the compression side load. Can easily be enlarged.
- extension-side back pressure chamber Ce and the compression-side back pressure chamber Cp are communicated by the communication path 24 through the extension-side resistance element and the compression-side resistance element. Since the pressure side pressure introduction passage Ip introduces the liquid from the pressure side chamber R2 to the expansion side back pressure chamber Ce with almost no resistance, the pressure side into the expansion side back pressure chamber Ce when the shock absorber D switches from the expansion operation to the contraction operation. The pressure in the chamber R2 is quickly introduced. For this reason, the expansion side spool Se presses the expansion side leaf valve Ve according to the pressure in the expansion side back pressure chamber Ce and the urging force of the spring member 16, and promptly moves the expansion side leaf valve Ve to the expansion side valve seat 2d. And the extension side passage 3 is closed.
- the expansion side pressure introduction passage Ie also introduces liquid from the expansion side chamber R1 into the compression side back pressure chamber Cp with almost no resistance. Therefore, when the shock absorber D switches from the contraction operation to the expansion operation, the expansion side chamber enters the compression side back pressure chamber Cp. The pressure in R1 is quickly introduced. For this reason, the pressure side spool Sp presses the pressure side leaf valve Vp according to the pressure in the pressure side back pressure chamber Cp and the urging force of the spring member 20, and promptly seats the pressure side leaf valve Vp on the pressure side valve seat 2c. The passage 4 is closed.
- extension side pressure introduction passage Ie and the pressure side pressure introduction passage Ip are not provided with an extension side resistance element and a pressure side resistance element such as an orifice. For this reason, even if the annular plate 19 of the extension side check valve Te and the annular plate 15 of the compression side check valve Tp do not adhere to the pressure side chamber 11 and the extension side chamber 12 due to aging, etc., respectively, There is no change in the flow rate guided through the expansion side pressure introduction passage Ie and the pressure side pressure introduction passage Ip. Therefore, the valve closing operation at the time of damping force control and expansion / contraction switching is not affected.
- a piston 2 having an extension side passage 3 and a pressure side passage 4 on the outer periphery side of the piston rod 7, an extension side leaf valve Ve and a pressure side leaf valve Vp stacked on the piston 2, and a cylindrical shape on the inner periphery.
- the pressure side chamber 11 in which the back pressure chamber Cp is formed is mounted, the extension side chamber 12 is provided with a pressure side pressure introduction passage Ip, and the pressure side chamber 11 is provided with an extension side pressure introduction passage Ie.
- the urging of the expansion side spool Se to the expansion side leaf valve Ve and the urging of the annular plate 15 of the pressure side check valve Tp that opens and closes the pressure side pressure introduction passage Ip are performed by one spring member 16.
- the urging of the compression side spool Sp to the compression side leaf valve Vp and the urging of the annular plate 19 of the extension side check valve Te that opens and closes the extension side pressure introduction passage Ie are performed by one spring member 20.
- the piston rod 7 of the shock absorber D has a holding shaft 8a provided on the distal end side, on which the piston 2, the extension side leaf valve Ve, the pressure side leaf valve Vp, the extension side chamber 12 and the pressure side chamber 11 are mounted on the outer periphery.
- a vertical hole 8d that opens at the tip of the holding shaft 8a, an extension pilot orifice Pe and a pressure pilot orifice Pp that are provided in the holding shaft 8a and communicate with a communication passage 24 provided in the vertical hole 8d, and an electromagnetic pressure control valve. 6
- an adjustment passage Pc that communicates the communication passage 24 with the accommodation portion L
- a pressure-side discharge passage Ep that communicates the accommodation portion L with the expansion side chamber R ⁇ b> 1.
- a communication passage 24 is formed which communicates the extension-side back pressure chamber Ce and the pressure-side back pressure chamber Cp in the vertical hole 8d with an annular groove 23a provided on the outer periphery.
- a separator 23 that forms the extended-side discharge passage Ee is inserted on the inner periphery. Due to such a configuration, the electromagnetic pressure control valve 6 can be accommodated in the piston rod 7 without difficulty, and the back pressure on the extension side is shifted to the outer periphery of the piston rod 7 by shifting from the electromagnetic pressure control valve 6 in the axial direction.
- the chamber Ce and the compression side back pressure chamber Cp can be provided.
- the electromagnetic pressure control valve 6 is set so as to perform pressure control when energized and close the adjustment passage Pc when de-energized.
- the adjustment passage Pc is provided with a fail valve FV that bypasses the electromagnetic pressure control valve 6, and the valve opening pressure of the fail valve FV is set larger than the maximum control pressure by the electromagnetic pressure control valve 6. . For this reason, at the time of failure, the extension side load and the compression side load become maximum, and the shock absorber D exhibits the greatest damping force and can stabilize the vehicle body posture even at the time of failure.
- the small diameter portion 31a of the electromagnetic valve valve body 31 is opposed to the through hole 30c to close the through hole 30c.
- the through hole 30c may not be completely closed, and the concave portion 31c may be slightly opposed to the through hole 30c so as to function as a throttle valve.
- the electromagnetic pressure control valve 6 includes a cylindrical valve housing cylinder 30a in which a through hole 30c that is a part of the adjustment passage Pc is formed, and an annular control valve valve seat 30d provided at an end of the valve housing cylinder 30a.
- a small-diameter portion 31a that is slidably inserted into the valve housing cylinder 30a, and a large end portion that is larger in outer diameter than the small-diameter portion 31a and that is attached to and detached from the control valve valve seat 30d.
- a solenoid valve body 31 having a diameter portion 31b and a recess 31c provided between the small diameter portion 31a and the large diameter portion 31b and capable of facing the through hole 30c, and the through hole 30c of the valve seat member 30.
- the adjustment passage Pc is shut off by making the small-diameter portion 31a of the electromagnetic valve valve body 31 face each other.
- the area receiving the pressure acting in the direction of pushing out the solenoid valve disc 31 from the valve seat member 30 is the area of the circle whose diameter is the outer diameter of the small diameter portion 31a from the area of the circle whose diameter is the inner diameter of the control valve valve seat 30d.
- the area minus. As described above, the area receiving the pressure acting in the direction of pushing out the electromagnetic valve body 31 can be reduced, and the flow area at the time of opening the valve can be increased. It can be stabilized.
- valve closed state is maintained regardless of the upstream pressure, so that only the fail valve FV is effective. be able to.
- the structure of the above-mentioned urging mechanism is an example, and is not limited to this.
- the damping valve according to the embodiment of the present invention is applied to both the expansion side damping valve and the compression side damping valve has been described.
- the stretching side damping valve and the compression side damping valve are described. And may be applied to only one of the above.
- the damping valve according to the embodiment of the present invention is not limited to the damping valve provided in the piston portion of the shock absorber, and may be applied to a damping valve provided in a base valve (not shown).
Abstract
Description
Claims (8)
- 通路と当該通路の出口端を囲む弁座とを有するバルブディスクと、
前記バルブディスクに積層されて前記弁座に離着座して前記通路を開閉する環状のリーフバルブと、
前記リーフバルブに前記バルブディスク側へ向けて可変附勢力を作用させる附勢機構と、を備え、
前記リーフバルブは、前記バルブディスクに対して軸方向に全体が後退可能であって、
前記リーフバルブが無負荷で前記バルブディスクに積層される状態では、前記リーフバルブと前記弁座との間に隙間が形成される減衰バルブ。 - 請求項1に記載の減衰バルブであって、
前記リーフバルブの前記バルブディスク側とは反対側に積層されるとともに前記リーフバルブとともに前記バルブディスクに対して軸方向に後退可能であって前記リーフバルブよりも剛性が高いプレートをさらに備える減衰バルブ。 - 請求項2に記載の減衰バルブであって、
前記リーフバルブおよび前記プレートは、環状であって、
外周に前記リーフバルブおよび前記プレートが軸方向に移動自在に装着される軸部材と、
前記軸部材に積層されて前記リーフバルブおよび前記プレートの前記バルブディスクからの後退量を規制するストッパと、をさらに備える減衰バルブ。 - 請求項1に記載の減衰バルブであって、
前記バルブディスクの前記通路より内側に設けられた内周シート部と前記リーフバルブとの間に介装される環状スペーサをさらに備え、
前記環状スペーサは、1枚または複数枚設けられる減衰バルブ。 - シリンダと、
前記シリンダ内に収容される請求項1に記載の減衰バルブと、
前記バルブディスクにより前記シリンダ内に区画された伸側室及び圧側室と、
前記シリンダ内に移動自在に挿入されるとともに前記バルブディスクに連結されるピストンロッドと、を備え、
前記通路は、前記伸側室と前記圧側室とを連通する緩衝器。 - 請求項5に記載の緩衝器であって、
前記附勢機構は、前記伸側室と前記圧側室の一方または両方の圧力を利用して前記リーフバルブを附勢する緩衝器。 - 請求項5に記載の緩衝器であって、
前記バルブディスクは、前記通路として前記伸側室と前記圧側室とを連通する伸側通路及び圧側通路と、前記弁座として伸側通路の出口端を囲む伸側弁座及び圧側通路の出口端を囲む圧側弁座と、を有し、
前記リーフバルブは、前記伸側通路を開閉する伸側リーフバルブと前記圧側通路を開閉する圧側リーフバルブとを有し、
前記附勢機構は、
前記伸側リーフバルブを附勢する伸側スプールと、
内部圧力で前記伸側スプールを押圧する伸側背圧室と、
前記圧側リーフバルブを附勢する圧側スプールと、
内部圧力で前記圧側スプールを押圧する圧側背圧室と、
通過する液体の流れに抵抗を与える伸側抵抗要素を介して前記伸側背圧室に連通されるともに通過する液体の流れに抵抗を与える圧側抵抗要素を介して前記圧側背圧室に連通される連通路と、
前記伸側室から前記圧側背圧室へ向かう液体の流れのみを許容する伸側圧力導入通路と、
前記圧側室から前記伸側背圧室へ向かう液体の流れのみを許容する圧側圧力導入通路と、
前記連通路に接続される調整通路と、
前記調整通路の下流を前記伸側室へ連通するとともに前記調整通路から前記伸側室へ向かう液体の流れのみを許容する圧側排出通路と、
前記調整通路の下流を前記圧側室へ連通するとともに前記調整通路から前記圧側室へ向かう液体の流れのみを許容する伸側排出通路と、
前記調整通路に設けられて調整通路の上流圧力を制御する電磁圧力制御弁と、を有し、
前記伸側背圧室内の圧力と前記圧側背圧室内の圧力とが等しい場合、前記伸側背圧室の圧力によって前記伸側リーフバルブを附勢する伸側荷重の方が前記圧側背圧室の圧力によって前記圧側リーフバルブを附勢する圧側荷重よりも大きい緩衝器。 - 請求項7に記載の緩衝器であって、
前記伸側背圧室の圧力を受ける前記伸側スプールの受圧面積は、前記圧側背圧室の圧力を受ける前記圧側スプールの受圧面積よりも大きい緩衝器。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020177013925A KR101914398B1 (ko) | 2014-11-25 | 2015-11-12 | 감쇠 밸브 및 완충기 |
US15/528,957 US10544852B2 (en) | 2014-11-25 | 2015-11-12 | Damping valve and damper |
CN201580064346.0A CN107002809B (zh) | 2014-11-25 | 2015-11-12 | 阻尼阀和缓冲器 |
EP15863448.5A EP3225875B1 (en) | 2014-11-25 | 2015-11-12 | Damping valve and shock absorber |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014-237849 | 2014-11-25 | ||
JP2014237849A JP6378618B2 (ja) | 2014-11-25 | 2014-11-25 | 減衰バルブ及び緩衝器 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016084621A1 true WO2016084621A1 (ja) | 2016-06-02 |
Family
ID=56074190
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/081900 WO2016084621A1 (ja) | 2014-11-25 | 2015-11-12 | 減衰バルブ及び緩衝器 |
Country Status (6)
Country | Link |
---|---|
US (1) | US10544852B2 (ja) |
EP (1) | EP3225875B1 (ja) |
JP (1) | JP6378618B2 (ja) |
KR (1) | KR101914398B1 (ja) |
CN (1) | CN107002809B (ja) |
WO (1) | WO2016084621A1 (ja) |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100170760A1 (en) | 2009-01-07 | 2010-07-08 | John Marking | Remotely Operated Bypass for a Suspension Damper |
US9452654B2 (en) | 2009-01-07 | 2016-09-27 | Fox Factory, Inc. | Method and apparatus for an adjustable damper |
US10036443B2 (en) | 2009-03-19 | 2018-07-31 | Fox Factory, Inc. | Methods and apparatus for suspension adjustment |
US11299233B2 (en) | 2009-01-07 | 2022-04-12 | Fox Factory, Inc. | Method and apparatus for an adjustable damper |
US20190176557A1 (en) * | 2009-01-07 | 2019-06-13 | Fox Factory, Inc. | Active valve for an internal bypass |
US8838335B2 (en) | 2011-09-12 | 2014-09-16 | Fox Factory, Inc. | Methods and apparatus for suspension set up |
US10697514B2 (en) | 2010-01-20 | 2020-06-30 | Fox Factory, Inc. | Remotely operated bypass for a suspension damper |
EP2530355B1 (en) | 2011-05-31 | 2019-09-04 | Fox Factory, Inc. | Apparatus for position sensitive and/or adjustable suspension damping |
US10330171B2 (en) | 2012-05-10 | 2019-06-25 | Fox Factory, Inc. | Method and apparatus for an adjustable damper |
EP3225874B1 (en) | 2014-11-25 | 2023-08-23 | KYB Corporation | Attenuation valve and shock absorber |
JP6527760B2 (ja) * | 2015-06-17 | 2019-06-05 | 株式会社ショーワ | 減衰力可変式緩衝器 |
JP6093837B1 (ja) * | 2015-11-19 | 2017-03-08 | Kyb株式会社 | 磁気粘性流体緩衝器 |
BE1023716B1 (nl) * | 2016-01-03 | 2017-06-26 | Shi Yan | Frequentie afhankelijke schokdemper |
JP2017198276A (ja) * | 2016-04-27 | 2017-11-02 | Kyb株式会社 | 減衰力調整バルブ及び緩衝器 |
JP6706165B2 (ja) * | 2016-07-07 | 2020-06-03 | Kyb株式会社 | 減衰弁および緩衝器 |
US11261932B2 (en) | 2017-07-27 | 2022-03-01 | Hitachi Astemo, Ltd. | Shock absorber |
JP2019138401A (ja) * | 2018-02-13 | 2019-08-22 | Kyb株式会社 | 緩衝器 |
JP7125363B2 (ja) * | 2019-03-04 | 2022-08-24 | Kyb株式会社 | 緩衝器 |
WO2021195554A1 (en) * | 2020-03-27 | 2021-09-30 | DRiV Automotive Inc. | Damper assembly |
KR102385442B1 (ko) * | 2020-07-31 | 2022-04-12 | 에스앤티모티브 주식회사 | 주파수 감응형 쇽업소버 |
US11692605B2 (en) * | 2021-07-29 | 2023-07-04 | Rüdiger Kranz | Hydraulic shock absorber |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS491993U (ja) * | 1972-04-06 | 1974-01-09 | ||
JPS61158582U (ja) * | 1985-03-26 | 1986-10-01 | ||
JPH03163233A (ja) * | 1989-11-20 | 1991-07-15 | Kayaba Ind Co Ltd | 油圧緩衝器のバルブ装置 |
JP2013029133A (ja) * | 2011-07-27 | 2013-02-07 | Hitachi Automotive Systems Ltd | シリンダ装置 |
Family Cites Families (36)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3194262A (en) * | 1963-12-10 | 1965-07-13 | Chrysler Corp | Shock absorber base valve |
US4624347A (en) * | 1984-01-23 | 1986-11-25 | Ford Motor Company | Piston assembly for shock absorber |
JPH0251637A (ja) * | 1988-08-12 | 1990-02-21 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
US5193655A (en) * | 1989-09-20 | 1993-03-16 | Atsugia Unisia Corp. | Variable damping force shock absorber with feature of linear and wide range damping force variation depending upon piston stroke speed |
US5129488A (en) * | 1989-11-16 | 1992-07-14 | Atsugi Unisia Corporation | Vibration mode responsive variable damping force shock absorber with feature of automatic selection of damping mode depending upon vibration mode of vehicular body |
JP2601904Y2 (ja) * | 1992-04-27 | 1999-12-13 | カヤバ工業株式会社 | 油圧緩衝器のバルブ構造 |
US5441133A (en) * | 1992-05-14 | 1995-08-15 | Kayaba Kogyo Kabushiki Kaisha | Hydraulic damper having leaf valve stopper |
DE19518560C2 (de) * | 1994-05-20 | 1997-07-10 | Tokico Ltd | Hydraulischer Dämpfer mit einstellbarer Dämpfungskraft |
JPH10122290A (ja) * | 1996-10-18 | 1998-05-12 | Kayaba Ind Co Ltd | 減衰バルブ構造 |
JPH10213172A (ja) * | 1997-01-27 | 1998-08-11 | Toyota Motor Corp | 減衰力可変ショックアブゾーバ |
DE19755994C2 (de) * | 1997-12-17 | 2003-02-20 | Thyssen Krupp Bilstein Gmbh | Kolben für einen hydraulischen Schwingungsdämpfer |
JP3972276B2 (ja) * | 1998-12-28 | 2007-09-05 | 株式会社日立製作所 | 減衰力調整式油圧緩衝器 |
JP4449022B2 (ja) * | 1999-04-28 | 2010-04-14 | 日立オートモティブシステムズ株式会社 | 減衰力調整式油圧緩衝器及び減衰力調整機構 |
DE10020778B4 (de) * | 1999-04-28 | 2005-01-13 | Tokico Ltd., Kawasaki | Hydraulischer Stossdämpfer mit Dämpfungskraftregelung |
JP2001263405A (ja) * | 2000-03-15 | 2001-09-26 | Showa Corp | 油圧緩衝器 |
JP4587089B2 (ja) * | 2000-05-31 | 2010-11-24 | 日立オートモティブシステムズ株式会社 | 減衰力調整式油圧緩衝器 |
JP3978708B2 (ja) * | 2001-11-29 | 2007-09-19 | 株式会社日立製作所 | 減衰力調整式油圧緩衝器 |
JP3978707B2 (ja) * | 2001-11-29 | 2007-09-19 | 株式会社日立製作所 | 減衰力調整式油圧緩衝器 |
US6668986B2 (en) * | 2002-01-08 | 2003-12-30 | Delphi Technologies, Inc. | Active hydraulic fluid vehicular suspension damper |
JP2004150574A (ja) * | 2002-10-31 | 2004-05-27 | Kayaba Ind Co Ltd | 油圧緩衝器の減衰力発生バルブ |
US7104180B2 (en) * | 2003-11-04 | 2006-09-12 | Delphi Technologies, Inc. | Low noise linear actuator |
US7290643B2 (en) * | 2003-12-17 | 2007-11-06 | Nobuaki Fujita | Front fork in two-wheeled motor vehicle or the like |
JP4987283B2 (ja) * | 2005-11-09 | 2012-07-25 | カヤバ工業株式会社 | 緩衝器のバルブ構造および緩衝器 |
JP4967091B2 (ja) * | 2007-04-19 | 2012-07-04 | 日立オートモティブシステムズ株式会社 | 流体圧緩衝器 |
JP4761474B2 (ja) * | 2007-09-06 | 2011-08-31 | カヤバ工業株式会社 | 緩衝器のバルブ構造 |
US8297418B2 (en) * | 2008-06-05 | 2012-10-30 | Tenneco Automotive Operating Company Inc. | Nested check high speed valve |
US8794407B2 (en) * | 2009-11-18 | 2014-08-05 | Tenneco Automotive Operating Company Inc. | Velocity progressive valving |
US9022187B2 (en) * | 2010-07-28 | 2015-05-05 | Kayaba Industry Co., Ltd. | Damping valve for shock absorber |
JP5812650B2 (ja) * | 2011-03-31 | 2015-11-17 | 日立オートモティブシステムズ株式会社 | 減衰力調整式緩衝器 |
JP5713462B2 (ja) * | 2012-06-27 | 2015-05-07 | カヤバ工業株式会社 | 減衰バルブ |
US9067471B2 (en) * | 2013-03-15 | 2015-06-30 | Tenneco Automotive Operating Company Inc. | Piston assembly with open bleed |
WO2015000160A1 (en) * | 2013-07-04 | 2015-01-08 | Beijingwest Industries Co., Ltd. | Hydraulic suspension damper with a spring valve assembly |
JP6114667B2 (ja) * | 2013-09-17 | 2017-04-12 | Kyb株式会社 | 減衰弁 |
JP6108550B2 (ja) * | 2013-09-19 | 2017-04-05 | Kyb株式会社 | 緩衝装置 |
US9500251B2 (en) * | 2014-11-25 | 2016-11-22 | Tenneco Automotive Operating Company Inc. | Shock absorber having orifice check disc |
US9845839B2 (en) * | 2016-02-18 | 2017-12-19 | Tenneco Automotive Operating Company Inc. | Shock absorber having check disc for orifice passage |
-
2014
- 2014-11-25 JP JP2014237849A patent/JP6378618B2/ja active Active
-
2015
- 2015-11-12 CN CN201580064346.0A patent/CN107002809B/zh active Active
- 2015-11-12 WO PCT/JP2015/081900 patent/WO2016084621A1/ja active Application Filing
- 2015-11-12 KR KR1020177013925A patent/KR101914398B1/ko active IP Right Grant
- 2015-11-12 US US15/528,957 patent/US10544852B2/en active Active
- 2015-11-12 EP EP15863448.5A patent/EP3225875B1/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS491993U (ja) * | 1972-04-06 | 1974-01-09 | ||
JPS61158582U (ja) * | 1985-03-26 | 1986-10-01 | ||
JPH03163233A (ja) * | 1989-11-20 | 1991-07-15 | Kayaba Ind Co Ltd | 油圧緩衝器のバルブ装置 |
JP2013029133A (ja) * | 2011-07-27 | 2013-02-07 | Hitachi Automotive Systems Ltd | シリンダ装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3225875A4 * |
Also Published As
Publication number | Publication date |
---|---|
EP3225875A4 (en) | 2018-10-24 |
EP3225875A1 (en) | 2017-10-04 |
KR101914398B1 (ko) | 2018-11-01 |
US20170268595A1 (en) | 2017-09-21 |
JP6378618B2 (ja) | 2018-08-22 |
KR20170075764A (ko) | 2017-07-03 |
US10544852B2 (en) | 2020-01-28 |
JP2016098950A (ja) | 2016-05-30 |
CN107002809B (zh) | 2019-04-23 |
CN107002809A (zh) | 2017-08-01 |
EP3225875B1 (en) | 2022-10-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2016084621A1 (ja) | 減衰バルブ及び緩衝器 | |
JP6239921B2 (ja) | 液圧緩衝器 | |
JP5952760B2 (ja) | 減衰弁 | |
JP5952762B2 (ja) | 減衰弁 | |
US11614140B2 (en) | Damping valve and shock absorber | |
JP6101179B2 (ja) | 減衰弁 | |
CN108027077B (zh) | 阻尼阀和缓冲器 | |
JP6114667B2 (ja) | 減衰弁 | |
WO2017010526A1 (ja) | 減衰弁および減衰弁を備えた緩衝器 | |
JP6018517B2 (ja) | ソレノイドバルブ | |
JP6442247B2 (ja) | バルブ | |
WO2018155293A1 (ja) | 緩衝器 | |
JP6059548B2 (ja) | ソレノイドバルブ | |
JP6442248B2 (ja) | 減衰バルブ及び緩衝器 | |
JP6059549B2 (ja) | ソレノイドバルブ | |
JP6262977B2 (ja) | 液圧緩衝器 | |
JP6514492B2 (ja) | 減衰バルブ及び緩衝器 | |
JP7128759B2 (ja) | 圧力制御弁 | |
CN116194697A (zh) | 阻尼阀以及缓冲器 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15863448 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20177013925 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15528957 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
REEP | Request for entry into the european phase |
Ref document number: 2015863448 Country of ref document: EP |