WO2014142191A1 - 減衰弁 - Google Patents
減衰弁 Download PDFInfo
- Publication number
- WO2014142191A1 WO2014142191A1 PCT/JP2014/056547 JP2014056547W WO2014142191A1 WO 2014142191 A1 WO2014142191 A1 WO 2014142191A1 JP 2014056547 W JP2014056547 W JP 2014056547W WO 2014142191 A1 WO2014142191 A1 WO 2014142191A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- pilot
- valve body
- valve seat
- damping
- Prior art date
Links
- 238000013016 damping Methods 0.000 title claims abstract description 142
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 19
- 230000002093 peripheral effect Effects 0.000 claims description 14
- 238000004891 communication Methods 0.000 claims description 8
- 239000012530 fluid Substances 0.000 claims description 5
- 239000006096 absorbing agent Substances 0.000 description 36
- 230000035939 shock Effects 0.000 description 36
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 31
- 239000010720 hydraulic oil Substances 0.000 description 23
- 125000006850 spacer group Chemical group 0.000 description 17
- 230000008602 contraction Effects 0.000 description 5
- 230000000149 penetrating effect Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000004804 winding Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000004043 responsiveness Effects 0.000 description 2
- 230000000452 restraining effect Effects 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 229920003002 synthetic resin Polymers 0.000 description 2
- 239000000057 synthetic resin Substances 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 238000002788 crimping Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 239000000945 filler Substances 0.000 description 1
- 238000007667 floating Methods 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 239000012762 magnetic filler Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/464—Control of valve bias or pre-stress, e.g. electromagnetically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/465—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 using servo control, the servo pressure being created by the flow of damping fluid, e.g. controlling pressure in a chamber downstream of a pilot passage
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/36—Valve members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
- F16K1/34—Cutting-off parts, e.g. valve members, seats
- F16K1/42—Valve seats
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K25/00—Details relating to contact between valve members and seats
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/02—Construction of housing; Use of materials therefor of lift valves
- F16K27/029—Electromagnetically actuated valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7879—Resilient material valve
- Y10T137/7888—With valve member flexing about securement
- Y10T137/789—Central mount
Definitions
- the present invention relates to a damping valve.
- damping valves are used as variable damping valves that vary the damping force of a shock absorber interposed between the vehicle body and the axle of the vehicle.
- a damping valve includes, for example, an annular valve seat provided in the middle of the flow path from the cylinder of the shock absorber to the reservoir, a valve body that opens and closes the annular valve seat and opens and closes the flow path, and branches from the flow path Pilot passage, an orifice provided in the middle of the pilot passage, a cylindrical spool that contacts the opposite side of the valve seat of the valve body, and a spool that is slidably mounted on the outer periphery.
- a valve housing that forms a back pressure chamber on the back side, a pilot valve provided downstream of the pilot passage, and a solenoid that adjusts the valve opening pressure of the pilot valve, are provided downstream of the pilot passage orifice.
- the secondary pressure is introduced into the back pressure chamber to press the valve body.
- the pilot valve is provided downstream of the back pressure chamber. Therefore, when the valve opening pressure of the pilot valve is adjusted by the thrust of the solenoid, the secondary pressure guided to the back pressure chamber is changed to open the pilot valve. It is controlled by the valve pressure.
- the secondary pressure acts on the back surface of the valve body, and the valve body is pressed against the valve seat side.
- Pressure on the upstream side of the flow path acts on the front face of the valve body so that the valve body bends and separates from the valve seat, so that the valve body is separated from the valve seat by the pressure on the upstream side of the flow path.
- valve opening pressure of the valve element can be adjusted.
- valve opening pressure of the pilot valve By adjusting the valve opening pressure of the pilot valve with the solenoid, the hydraulic oil passing through the flow path can be adjusted.
- the resistance given by the damping valve to the flow can be made variable. Therefore, a desired damping force can be generated in the shock absorber (see, for example, JP2009-222136A).
- the damping force is adjusted by adjusting the valve opening pressure of the pilot valve.
- the pilot valve is simply a poppet valve that opens and closes a port.
- inertia acts on the valve body.
- the distance that the valve element is separated from the valve seat is dynamically determined by the thrust of the solenoid, the urging force of the coil spring that urges the valve element, and the force that presses the valve element by the pressure upstream of the pilot valve. It overshoots more than the statically balanced position. Thereafter, the position of the valve body converges to the balanced position while being displaced across the statically balanced position.
- the flow passage area may be increased with respect to the pilot valve opening.
- the pilot valve is a poppet valve
- an attempt to increase the flow path area area increases the diameter of the annular valve seat on which the poppet valve is seated.
- the solenoid since the pressure receiving area where the pressure acts in the direction in which the poppet valve is separated from the annular valve seat becomes large, the solenoid must output a large thrust, resulting in a problem that the damping valve becomes large.
- An object of the present invention is to provide a damping valve that can exhibit a stable damping force without causing an increase in size.
- the valve is a damping valve having a port, a valve body that opens and closes the port, and the valve body is biased toward the valve seat member by internal pressure.
- a back pressure chamber a pilot passage leading to the back pressure chamber by reducing the pressure upstream of the port, and a pilot valve provided in the middle of the pilot passage to control the pressure in the back pressure chamber.
- the pilot valve has a cylindrical valve housing cylinder that communicates inside and outside and is provided with a through hole that communicates with the port, and an annular pilot valve seat that is provided at an end of the valve housing cylinder.
- a pilot valve seat member a large-diameter portion, a small-diameter portion that is slidably inserted into the valve housing cylinder, and a recess that is provided between the large-diameter portion and the small-diameter portion and faces the through hole
- a pilot valve body having the pilot valve seat Wherein an end portion of the large diameter portion by releasing seat damping valve for opening and closing the pilot passage is provided.
- FIG. 1 is a cross-sectional view of a damping valve according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view of a shock absorber to which a damping valve according to an embodiment of the present invention is applied.
- FIG. 3 is a diagram illustrating a damping characteristic of the shock absorber to which the damping valve according to the embodiment of the present invention is applied.
- FIG. 4 is an enlarged cross-sectional view of the pilot valve of the damping valve according to the embodiment of the present invention.
- FIG. 5 is a diagram showing a time transition of the displacement amount of the valve body after the pilot valve is opened.
- FIG. 6 is a diagram illustrating a damping characteristic of a shock absorber to which a damping valve according to a modification is applied.
- FIG. 1 is a cross-sectional view of a damping valve according to an embodiment of the present invention.
- FIG. 2 is a cross-sectional view of a shock absorber to which a damping valve according
- FIG. 7 is a diagram illustrating a damping characteristic of a shock absorber to which a damping valve according to another modification is applied.
- FIG. 8 is a partially enlarged cross-sectional view of a damping valve according to another embodiment of the present invention.
- FIG. 9 is a partially enlarged cross-sectional view of a damping valve according to still another embodiment of the present invention.
- the damping valve V includes a valve seat member 1 having a port 1 a, a valve body 3 that opens and closes the port 1 a, and a tubular shape that abuts the valve body 3 on the opposite side of the valve seat member 1.
- a valve housing 20 as a spool holding member on which the spool 30 is mounted on the outer periphery so as to be movable in the axial direction, and the spool 30 and the valve housing 20 divide the valve body 3 by the internal pressure.
- the back pressure chamber P is configured to urge the spool 30 so as to be pressed toward the first side, and the ring 29 is attached to the outer periphery of the valve housing 20 and slidably contacts the inner periphery of the spool 30.
- the damping valve V is applied to the shock absorber S.
- the shock absorber S generates a damping force mainly by giving resistance to the fluid passing through the port 1a during expansion and contraction.
- the shock absorber S to which the damping valve V is applied is, for example, as shown in FIG. 2, a cylinder 10, a piston 11 that is slidably inserted into the cylinder 10, and a cylinder 10 that is slidably inserted into the cylinder 10.
- a discharge passage 15 is formed between the rod 12 connected to the piston 11, the rod side chamber 13 and the piston side chamber 14 defined by the piston 11 inserted into the cylinder 10, and the cylinder 10 covering the outer periphery of the cylinder 10.
- An intermediate cylinder 16 and an outer cylinder 18 that covers the outer periphery of the intermediate cylinder 16 and forms a reservoir 17 between the intermediate cylinder 16 and the intermediate cylinder 16 are configured.
- the rod side chamber 13, the piston side chamber 14, and the reservoir 17 are filled with working oil as a working fluid.
- the reservoir 17 is filled with gas in addition to hydraulic oil.
- any fluid that can exhibit a damping force can be used other than the working oil.
- the shock absorber S includes a suction passage 19 that allows only the flow of hydraulic oil from the reservoir 17 toward the piston side chamber 14, and a piston that is provided in the piston 12 and allows only the flow of hydraulic oil toward the rod side chamber 13 from the piston side chamber 14. And a passage 20.
- the discharge passage 15 communicates the rod side chamber 13 and the reservoir 17, and the damping valve V is provided in the middle of the discharge passage 15.
- the shock absorber S when the compression operation is performed, the piston 11 moves downward in FIG. 2 to compress the piston side chamber 14, and the hydraulic oil in the piston side chamber 14 moves to the rod side chamber 13 via the piston passage 20. .
- the hydraulic oil corresponding to the rod penetration volume becomes excessive in the cylinder 10, and the excess hydraulic oil is pushed out of the cylinder 10 and is stored in the reservoir 17 via the discharge passage 15. Is discharged.
- the shock absorber S increases the pressure in the cylinder 10 by exerting resistance to the flow of hydraulic oil that passes through the discharge passage 15 and moves to the reservoir 17 by the damping valve V, and exerts a compression side damping force.
- the shock absorber S When the shock absorber S is extended, the piston 11 moves upward in FIG. 2 to compress the rod side chamber 13, and the hydraulic oil in the rod side chamber 14 moves to the reservoir 17 through the discharge passage 15. At this time, the piston 11 moves upward to increase the volume of the piston side chamber 14, and hydraulic oil commensurate with this expansion is supplied from the reservoir 17 through the suction passage 19.
- the shock absorber S increases the pressure in the rod side chamber 13 by exerting resistance to the flow of the hydraulic oil that passes through the discharge passage 15 and moves to the reservoir 17 by the damping valve V, and exerts the extension side damping force.
- the shock absorber S discharges the hydraulic oil from the cylinder 10 through the discharge passage 15 to the reservoir 17 in both cases of the extension operation and the compression operation.
- This is a uniflow shock absorber that circulates through the side chamber 13 and the reservoir 17 one-way in order. That is, the shock absorber S generates the damping force on both sides of the pressure expansion by the single damping valve V.
- the shock absorber S sets the cross-sectional area of the rod 12 to a half of the cross-sectional area of the piston 11 so that the amount of hydraulic oil discharged from the cylinder 10 can be increased on both sides of the pressure expansion with the same amplitude. Can be set equal. Therefore, by setting the resistance that the damping valve V gives to the flow to be the same, the damping force on the expansion side and the compression side can be set to be the same.
- the damping valve V is mounted so as to be able to float on the outer periphery of a valve seat member 1 fitted to a sleeve 16 a provided in the opening of the intermediate cylinder 16 and an assembly shaft 1 c provided in the valve seat member 1.
- a restricting passage 2b that communicates the port 1a and the inter-valve chamber C with each other.
- the damping valve V further includes a hollow valve housing 20 connected to the assembly shaft 1c of the valve seat member 1, a cylindrical pilot valve seat member 21 accommodated in the valve housing 20, and a pilot valve seat member 21.
- a pilot valve body 22 that is slidably inserted therein and a solenoid Sol that applies thrust to the pilot valve body 22 are provided.
- a pilot passage 23 is formed in the valve seat member 1 and the valve housing 20 to reduce the pressure on the upstream side of the port 1a to the back pressure chamber P.
- the valve seat member 1 is assembled with a large-diameter base portion 1d fitted into the sleeve 16a, an assembly shaft 1c protruding from the base portion 1d toward the pilot valve seat member 21, and a base portion 1d.
- a hollow portion 1e formed so as to penetrate the shaft 1c in the axial direction to form a part of the pilot passage 23, an orifice 1f provided in the middle of the hollow portion 1e, a plurality of ports 1a penetrating the base portion 1d, and a base portion 1d of the pilot valve seat member 21 and an annular first valve seat 1b formed on the outer peripheral side of the outlet of the port 1a.
- the port 1a penetrates the base 1d of the valve seat member 1 as described above.
- An opening on the inner peripheral side of the base portion 1 d in the port 1 a is communicated with the rod side chamber 13 via a discharge passage 15 formed by the intermediate cylinder 16, and an opening on the sub-valve element 2 side in the port 1 a is connected to the reservoir 17. It is communicated.
- the shock absorber S discharges hydraulic oil from the rod side chamber 13 to the reservoir 17 through the discharge passage 15 and the port 1a during expansion and contraction, and the upstream side of the port 1a becomes the rod side chamber 13.
- the hollow part 1e is also connected in the rod side chamber 13 via the discharge passage 15 similarly to the port 1a.
- the valve seat member 1 has a small-diameter portion 1g formed with a small diameter on the discharge passage 15 side in the base portion 1d fitted in a sleeve 16a, and a seal ring 24 is mounted on the outer periphery of the small-diameter portion 1g.
- a sub-valve body 2 that is attached to and detached from the first valve seat 1b and opens and closes the port 1a is stacked on the opposite end of the base 1d of the valve seat member 1 from the small diameter portion 1g.
- the sub-valve body 2 is annular and has an annular second valve seat 2a provided so as to protrude on the opposite side of the valve seat member 1, and an opening from the inner peripheral side of the second valve seat 2a. And a restriction passage 2b communicating with the surface on the one side.
- the outlet end of the port 1a is closed by the sub valve body 2.
- the restriction passage 2b provides resistance to the flow of hydraulic oil passing therethrough.
- the hydraulic oil that has passed through the port 1a passes through the restriction passage 2b and passes through the sub valve body 2.
- the sub valve body 2 is slidably mounted on the outer periphery of an annular spacer 25 mounted on the outer periphery of the assembly shaft 1c of the valve seat member 1.
- the spacer 25 is thicker in the axial direction than the axial thickness of the inner periphery of the sub-valve element 2, and the sub-valve element 2 can move in the axial direction on the outer periphery of the spacer 25.
- the sub valve body 2 is assembled to the valve seat member 1 so as to be floatable.
- the sub-valve body 2 is separated from the first valve seat 1b by moving away from the valve seat member 1, and opens the port 1a when the sub-valve body 2 is separated from the first valve seat 1b.
- the valve body 3 is laminated on the back side of the sub-valve body 2.
- the valve body 3 is an annular laminated leaf valve.
- the inner periphery of the valve body 3 is assembled to the assembly shaft 1c, and is sandwiched between the spacer 25 and the valve housing 20 screwed to the assembly shaft 1c. Therefore, the valve body 3 is allowed to bend on the outer peripheral side and can be seated on and off the second valve seat 2a of the sub-valve body 2.
- an inter-valve chamber C is formed between the valve body 3 and the sub-valve body 2. Is done.
- the inter-valve chamber C is communicated with the port 1a through the restriction passage 2b.
- the port 1 a is opened and communicates with the reservoir 17. That is, the valve body 3 can open and close the port 1a.
- the sub-valve body 2 slides on the outer periphery of the spacer 25 and separates from the first valve seat 1a.
- the hydraulic oil that has passed through the port 1a is discharged to the reservoir 17 through an annular gap formed between the sub valve body 2 and the first valve seat 1a.
- the valve element 3 is a laminated leaf valve configured by laminating a plurality of annular plates, but the number of annular plates is arbitrary.
- a notch orifice 3 a is provided on the outer periphery of the annular plate seated on the second valve seat 2 a in the valve body 3.
- the orifice may be provided by forming a notch or the like in the second valve seat 2a of the sub valve body 2 instead of the valve body 3, or the first valve seat 1b of the valve seat member 1 or the first valve seat 2 of the sub valve body 2. You may provide in the contact
- the restriction passage 2b since the restriction passage 2b only needs to communicate the front side and the back side of the sub-valve element 2, the restriction passage 2b may be provided in another place without being provided in the sub-valve element 2. When the sub valve body 2 is provided, processing becomes easy.
- a spacer 26, an annular leaf spring 27, and a spacer 28 are sequentially stacked and assembled to the assembly shaft 1c.
- the valve housing 20 is screwed to the tip of the assembly shaft 1c.
- the sub-valve body 2 mounted on the outer periphery of the spacer 25 is movable in the axial direction.
- the leaf spring 27 has an inner peripheral side fixed to the assembly shaft 1c and an outer peripheral side being a free end.
- the valve housing 20 has a cylindrical shape, a small diameter cylindrical portion 20a having a small outer diameter, a large diameter cylindrical portion 20b having a large outer diameter, and an annular shape provided on the outer periphery of the large diameter cylindrical portion 20b.
- a pressure introducing vertical hole 20e that leads to.
- the valve housing 20 is connected to the valve seat member 1 by screwing a screw hole portion 20f provided inside the small diameter cylindrical portion 20a to the assembly shaft 1c of the valve seat member 1.
- An annular protrusion 20g is provided on the inner peripheral side and a plurality of tool holes 20h opened on the end surface are provided at the end of the large diameter cylinder portion 20b opposite to the small diameter cylinder portion 20a.
- the valve housing 20 can be easily screwed onto the assembly shaft 1c by inserting and rotating a tool into the tool hole 20h.
- a ring 29 made of synthetic resin is attached to the annular groove 20c of the valve housing 20.
- a cylindrical spool 30 is slidably mounted on the outer periphery of the ring 29. That is, the spool 30 is movable in the axial direction with respect to the valve housing 20.
- a flange 30a protruding inward is provided at the end of the spool 30 on the valve body 3 side.
- the flange 30a includes an annular protrusion 30b that protrudes toward the valve body 3 side.
- the outer periphery of the leaf spring 27 is in contact with the end of the flange 30a opposite to the annular protrusion 30b.
- the spool 30 is urged toward the valve body 3 by the leaf spring 27, and the annular protrusion 30 b is in contact with the surface of the valve body 3 opposite to the sub-valve body 2.
- the spool 30 cooperates with the valve housing 20 to define a back pressure chamber P between the spool housing 20 and the spool housing 20.
- the back pressure chamber P is closed at the end on the valve body 3 side by a leaf spring 27 and communicated with the inside of the valve housing 20 via a pressure introducing vertical hole 20e and a pressure introducing horizontal hole 20d.
- the inside of the valve housing 20 communicates with the hollow portion 1e of the valve seat member 1 and communicates with the rod side chamber 13 upstream of the port 1a via the orifice 1f.
- the hydraulic oil discharged from the rod side chamber 13 is guided to the back pressure chamber P through the orifice 1f, and the pressure upstream of the port 1a is reduced by the orifice 1f and introduced into the back pressure chamber P.
- an urging force that presses the valve element 3 toward the sub-valve element 2 by the internal pressure of the back pressure chamber P acts on the back surface of the valve element 3. . That is, when the shock absorber S is expanded and contracted, the pressure in the rod side chamber 13 acts on the sub-valve 2 from the front side via the port 1a, and the internal pressure of the back pressure chamber P from the back side. The urging force by the leaf spring 27 acts through the valve body 3.
- the valve body 3 acts so that a force obtained by multiplying the inner diameter cross-sectional area of the spool 30 on the valve housing 20 side with respect to the flange 30a by the pressure of the back pressure chamber P is pressed against the sub-valve body 2, and the second valve seat 2a.
- the force obtained by multiplying the inner diameter cross-sectional area by the pressure in the inter-valve chamber C acts in the direction of separating from the sub-valve element 2.
- the ratio of the inner diameter sectional area of the spool 30 on the valve housing 20 side with respect to the flange 30a and the inner diameter sectional area of the second valve seat 2a is the ratio of the valve opening pressure of the valve body 3 to the pressure in the back pressure chamber P.
- the pressure ratio is determined.
- a hole may be provided in the leaf spring 27 and the pressure in the back pressure chamber P may be directly applied to the valve body 3.
- the pressure in the inter-valve chamber C is increased by the pressure in the rod side chamber 13, and the force to deflect the outer periphery of the valve body 3 toward the spool 30 side is the internal pressure of the back pressure chamber P and the urging force by the leaf spring 27.
- the valve body 3 bends and separates from the second valve seat 2a, a gap is formed between the valve body 3 and the sub-valve body 2, and the port 1a is opened.
- the inner diameter of the second valve seat 2a is made larger than the inner diameter of the first valve seat 1b, the sub-valve element 2 receives the pressure on the port 1a side, and the sub-valve element 2 is the inter-valve chamber.
- a difference is given to the pressure receiving area that receives the pressure on the C side. Therefore, if the differential pressure generated by the restriction passage 2b does not reach the valve opening pressure for separating the sub valve body 2 from the first valve seat 1b, the sub valve body 2 remains seated on the first valve seat 1b.
- the sub valve body 2 is also in the first state.
- the port 1a is opened by separating from the valve seat 1b. That is, in this embodiment, the pressure increase ratio in the valve body 3 is set smaller than the pressure increase ratio in the sub valve body 2 that is the ratio of the valve opening pressure of the sub valve body 2 to the pressure in the inter-valve chamber C.
- the pressure in the rod side chamber 13 when the valve body 3 opens is lower than the pressure in the rod side chamber 13 when the sub valve body 2 opens. That is, the valve opening pressure of the valve body 3 is set to be lower than the valve opening pressure of the sub valve body 2.
- the pressure introducing lateral hole 20d communicates with the annular groove 20c in which the ring 29 is mounted, the ring 29 is pressed against the spool 30 by the pressure received from the pressure introducing lateral hole 20d. Therefore, when the pressure upstream of the port 1a is increased, the force pressing the ring 29 is increased.
- the ring 29 may be formed of, for example, a fluororesin or other synthetic resin, or a material that hardly wears the sliding surface of the spool 30 such as brass. Further, in order to facilitate the mounting of the ring 29 in the annular groove 20c, it is preferable to insert a bias cut (split) 29a in the ring 29. When the ring 29 is provided with the bias cut 29a, the ring 29 is easily expanded in diameter by the pressure from the inner peripheral side, and the movement of the spool 30 is easily suppressed.
- a cylindrical pilot valve seat member 21 is accommodated in the valve housing 20 on the surface side where the annular protrusion 20g is provided rather than the screw hole 20f.
- the pilot valve seat member 21 includes a bottomed cylindrical valve housing cylinder 21a, a flange portion 21b provided to project outward on the outer periphery of the opening side end of the valve housing cylinder 21a, and a valve housing cylinder 21a.
- a through hole 21c that opens from the side and communicates with the inside, an annular pilot valve seat 21d that protrudes in the axial direction at the opening side end of the valve housing cylinder 21a, and a flange that is provided on the outer periphery of the flange portion 21b And a valve holding portion 21e that is thicker than the portion 21b.
- a fail valve body 31 composed of an annular laminated leaf valve is mounted on the outer periphery of the annular protrusion 20g of the valve housing 20.
- the fail valve body 31 is sandwiched between the surface of the large-diameter cylindrical portion 20b of the valve housing 20 where the annular protrusion 20g is provided and the valve restraining portion 21e of the pilot valve seat member 21. Thereby, the inner periphery of the fail valve body 31 is fixed, and the outer periphery can be bent.
- the pilot valve body 22 is slidably inserted into the valve housing cylinder 21a of the pilot valve seat member 21.
- the pilot valve body 22 is provided on the pilot valve seat member 21 side and is slidably inserted into the valve accommodating cylinder 21a, and a large diameter portion provided on the opposite side of the pilot valve seat member 21.
- annular recess 22c provided between the small-diameter portion 22a and the large-diameter portion 22b
- a flange-shaped spring receiving portion 22d provided on the outer periphery at the opposite end to the pilot valve seat member 21, and a pilot A communication passage 22e penetrating from one end of the valve body 22 to the other end, an orifice 22f provided in the middle of the communication passage 22e, and an outer periphery on the opposite end to the pilot valve seat member 21 of the spring receiving portion 22d.
- annular protrusion 22g is an annular protrusion 22g.
- the recess 22c of the pilot valve body 22 always faces the through hole 21c when the pilot valve body 22 moves in the axial direction with respect to the pilot valve seat member 21. That is, the pilot valve body 22 does not block the through hole 21c within a range in which the movement of the pilot valve body 22 is allowed.
- the pilot valve body 22 has an outer diameter on the opposite side to the pilot valve seat member 21 with the recess 22c as a boundary, and the pilot valve seat member 21 side end of the large diameter portion 22b.
- an annular seat portion 22h facing the pilot valve seat 21d is provided.
- the pilot valve body 22 moves in the axial direction with respect to the pilot valve seat member 21, so that the seat portion 22h is separated from and seated on the pilot valve seat 21d. That is, the pilot valve body 22 and the pilot valve seat member 21 constitute a pilot valve Pi, and when the seating portion 22h is seated on the pilot valve seat 21d, the pilot valve Pi is closed.
- a perforated disk 32 that fits to the inner periphery of the annular protrusion 22g is laminated, and the communication path 22e is formed in the hole (
- the holed disk 32 communicates with the rear surface side opposite to the pilot valve body 22 via a not-shown).
- a coil spring 33 for biasing the pilot valve body 22 to the opposite side of the pilot valve seat member 21 is interposed between the spring receiving portion 22d and the flange portion 21b.
- the pilot valve body 22 is always urged to the opposite side of the pilot valve seat member 21 by the coil spring 33, and if a thrust against the coil spring 33 does not act from a solenoid Sol described later, the pilot valve Pi opens. It comes to be in a state.
- the coil spring 33 is used to urge the pilot valve body 22 in a direction away from the pilot valve seat member 21.
- an urging force can be exerted.
- An elastic body that can be used can be used.
- a space K is formed in the valve accommodating cylinder 21a and closer to the bottom side of the valve accommodating cylinder 21a than the through hole 21c. .
- the space K communicates with the outside of the pilot valve Pi through a communication passage 22e and an orifice 22f provided in the pilot valve body 22.
- a fail valve seat member 34 is provided on the outer periphery of the pilot valve body 22 so as to be stacked on the large-diameter cylindrical portion 20b side of the valve housing 20.
- the fail valve seat member 34 has an annular shape, and is provided on the outer periphery with a socket portion 34a that fits on the outer periphery of the large-diameter cylindrical portion 20b of the valve housing 20, and an annular window 34b provided on the valve housing 20 side end.
- a fail valve seat 34c provided on the outer periphery of the annular window 34b, an annular recess 34d provided on the inner peripheral side of the annular window 34b, and a plurality of passages formed from the inner periphery to the annular recess 34d and leading to the annular window 34b.
- an annular flange 34f provided to project inwardly on the inner periphery of the end opposite to the valve housing 20, a plurality of notches 34g provided on the end opposite to the valve housing 20, and a socket And a through hole 34h penetrating the portion 34a.
- the inner diameter of the fail valve seat member 34 other than the flange 34f is set to a diameter that does not hinder the movement of the pilot valve body 22.
- the valve restraining portion 21 e of the pilot valve seat member 21 is sandwiched between the fail valve body 31 and the valve valve member 20 together with the fail valve body 31.
- the member 21 and the fail valve body 31 are fixed.
- the valve accommodating cylinder 21 a of the pilot valve seat member 21 is accommodated in the valve housing 20.
- the pilot valve seat member 21 is positioned on the fail valve seat member 34 in the radial direction by fitting the outer periphery of the valve holding portion 21e into an annular recess 34d provided in the fail valve seat member 34.
- the fail valve body 31 is seated on a fail valve seat 34c provided on the fail valve seat member 34 and closes the annular window 34b.
- the fail valve seat 31 is separated from the fail valve seat 34c to open the annular window 34b, and the fail valve seat member is opened via the passage 34e and the through hole 34h.
- 34 communicates with the reservoir 17.
- the fail valve body 31 and the fail valve seat member 34 constitute a fail valve F.
- the passage 34 e and the through hole 34 h form a fail passage that branches off from the pilot passage 23 and communicates the pilot passage 23 with the reservoir 17. Since the passage 34e is formed by a groove provided on the valve housing 20 side of the fail valve seat member 34, it is very easy to process, but it can also be formed by a hole other than the groove.
- the damping valve V communicates the rod side chamber 13 and the reservoir 17 through the port 1a, and opens and closes the port 1a with the sub-valve body 2 and the valve body 3.
- the hollow portion 1e of the valve seat member 1 the inside of the valve housing 20, the through hole 21c of the pilot valve seat member 21, the inside of the pilot valve seat member 21, the recess 22c of the pilot valve body 22,
- a pilot passage 23 communicating the rod side chamber 13 and the reservoir 17 is formed in the fail valve seat member 34 and through a notch 34 g of the fail valve seat member 34.
- the pilot passage 23 communicates with the back pressure chamber P through a pressure introducing lateral hole 20d and a pressure introducing vertical hole 20e provided in the valve housing 20, and the pressure upstream of the port 1a is in the middle of the pilot passage 23.
- the pressure is reduced by the provided orifice 1 f and introduced into the back pressure chamber P.
- the pilot passage 23 is opened and closed by the pilot valve Pi, and the pressure in the back pressure chamber P can be controlled by adjusting the opening degree of the pilot valve Pi.
- the shock absorber S includes a solenoid Sol that applies thrust to the pilot valve body 22 in order to adjust the opening degree of the pilot valve Pi.
- the pilot valve body 22 when the pilot valve body 22 is urged by the coil spring 33 and the outer periphery of the annular protrusion 22g abuts on the flange 34e, the communication between the notch 34g and the fail valve seat member 34 is cut off. That is, the pilot valve body 22 is separated from the pilot valve seat 21d as much as possible, and the downstream side of the pilot passage 23 is blocked from the connection point of the fail passage. In this state, when the pressure in the pilot passage 23 increases and reaches the valve opening pressure of the fail valve body 31, the fail valve body 31 is separated from the fail valve seat 34c. Thus, the pilot passage 23 can be communicated with the reservoir 17 through the passage 34e, the annular window 34d, and the through hole 34h.
- a sleeve 18a is attached to the opening provided in the outer cylinder 18, and the solenoid Sol is accommodated in a bottomed cylindrical case 35 that is screwed to the outer periphery of the sleeve 18a.
- the solenoid Sol includes an annular solenoid bobbin 39 that is wound around the winding 38 and is fixed to the bottom of the case 35, and a first fixed iron core 40 that has a bottomed cylindrical shape and is fitted to the inner periphery of the solenoid bobbin 39. And a cylindrical second fixed iron core 41 fitted to the inner periphery of the solenoid bobbin 39, and the first fixed iron core 40 and the second fixed iron core 41 interposed between the first fixed iron core 40 and the second fixed iron core 41.
- the shaft 44 is fixed to the inner periphery of the movable iron core 43.
- the case 35 is configured to include a cylindrical portion 35a and a bottom portion 35b fixed by crimping the opening end of the cylindrical portion 35a, and when the opening end of the cylindrical portion 35a is crimped, the inner periphery of the cylindrical portion 35a is formed.
- the bobbin holder 36 is fixed together with the bottom 35b.
- the bobbin holder 36 holds a solenoid bobbin 39, and the solenoid bobbin 39 is attached to the case 35 via the bobbin holder 36.
- the movable iron core 43 has a cylindrical shape, and a shaft 44 extending in the axial direction from both ends is mounted on the inner periphery.
- An annular guide 46 is fitted on the inner periphery of the second fixed iron core 41, and an annular bush 47 is held on the inner periphery of the guide 46.
- the shaft 44 is held by an annular bush 45 provided at the bottom of the first fixed iron core 40 and a bush 47 so as to be movable in the axial direction.
- the bushes 45 and 47 allow the shaft 44 to move in the axial direction. Guided.
- the guide 46 fitted to the inner periphery of the second fixed iron core 41 contacts the fail valve seat member 34. Accordingly, the fail valve seat member 34, the pilot valve seat member 21, the valve housing 20, and the valve seat member 1 are fixed to the shock absorber S. Since the fail valve seat member 34 is provided with a notch 34g, the pilot passage 23 is not blocked even if the guide 46 contacts the fail valve seat member 34.
- the bush 44 side end of the shaft 44 is in contact with the perforated disk 32 fitted to the inner periphery of the annular protrusion 22g of the pilot valve body 22.
- the urging force of the coil spring 33 also acts on the shaft 44 via the pilot valve body 22.
- the coil spring 33 not only biases the pilot valve body 22 but also plays a role of biasing the shaft 44 as a part of the solenoid Sol.
- the second fixed iron core 41 includes a cylindrical sleeve 41b fitted to the inner periphery of the sleeve 18a, whereby each member constituting the solenoid Sol is positioned in the radial direction with respect to the sleeve 18a. .
- a notch (not shown) is provided on the outer periphery of the fail valve seat member 34.
- the sleeve 41b is set to have an axial length dimension so as not to interfere with the spool 30.
- the guide 46 is provided with a hole 46a penetrating in the axial direction so that no pressure difference is generated between the fail valve seat member 34 side and the movable iron core 43 side of the guide 46. Further, the movable iron core 43 is also provided with a hole 43a penetrating in the axial direction, and a pressure difference is generated between the guide 46 side and the bush 45 side of the movable iron core 43 to prevent smooth movement of the movable iron core 43. There is no consideration.
- the solenoid Sol is formed such that the magnetic path passes through the first fixed iron core 40, the movable iron core 43, and the second fixed iron core 41, and is arranged closer to the first fixed iron core 40 when the winding 38 is excited.
- the made movable iron core 43 is sucked to the second fixed iron core 41 side.
- a thrust toward the pilot valve Pi side acts on the movable iron core 43.
- the shaft 44 that moves integrally with the movable iron core 43 is in contact with the pilot valve body 22 of the pilot valve Pi, so that the thrust of the solenoid Sol is transmitted to the pilot valve body 22. Yes. That is, when the solenoid Sol is excited, a thrust in a direction toward the valve seat member 1 can be applied to the pilot valve body 22 from the movable iron core 43 through the shaft 44.
- the pilot valve element 22 When the solenoid Sol is not energized, the pilot valve element 22 is pushed away from the pilot valve seat 21d by the coil spring 33, opens the pilot valve Pi to the maximum extent, and sits on the flange 34f of the fail valve seat member 34. Then, the pilot passage 23 is shut off. Thereby, the fail valve F is made effective.
- the thrust applied to the pilot valve body 22 can be adjusted by the energization amount to the winding 38 of the solenoid Sol, and thereby the valve opening pressure of the pilot valve Pi can be controlled.
- the resultant pressure of the force that separates the pilot valve body 22 from the pilot valve seat 21d and the urging force of the coil spring 33 when the pressure upstream of the pilot passage 23 acts on the pilot valve body 22 is the solenoid Sol.
- the valve is opened and the pilot passage 23 is opened.
- the pilot valve Pi is opened and the pilot passage 23 is opened.
- the magnitude of the valve opening pressure of the pilot valve Pi can be adjusted by adjusting the thrust of the solenoid Sol with the magnitude of the current supplied to the solenoid Sol.
- the internal pressure of the back pressure chamber P is controlled by the valve opening pressure of the pilot valve Pi. Therefore, the pressure which acts on the back surface of the valve body 3 can be adjusted by adjusting the valve opening pressure with the solenoid Sol. That is, the valve opening pressure at which the valve body 3 opens the port 1a can be controlled.
- the pressure in the inter-valve chamber C is increased by the pressure in the rod-side chamber 13, and the force to bend the outer periphery of the valve body 3 causes the internal pressure of the back pressure chamber P and the leaf spring 27 to When the urging force is overcome, the valve body 3 bends and separates from the second valve seat 2a. That is, a gap is formed between the valve body 3 and the sub-valve body 2, and the port 1a is opened.
- the pressure in the inter-valve chamber C that separates the valve body 3 from the second valve seat 2a can be adjusted. That is, the valve opening pressure of the valve body 3 can be controlled by the amount of current applied to the solenoid Sol.
- the damping characteristic of the damping valve V (a characteristic of the damping force with respect to the piston speed) is such that the hydraulic oil moves through the sliding gap and the orifice 3a of the damping valve V until the valve body 3 opens. Since it passes, it becomes a characteristic with a slight inclination (the line X portion in FIG. 3).
- the inclination becomes smaller, that is, the damping coefficient becomes smaller.
- the valve opening pressure of the valve body 3 is smaller than the valve opening pressure of the sub valve body 2. Become. Therefore, if the differential pressure generated by the restriction passage 2b does not reach the valve opening pressure for separating the sub valve body 2 from the first valve seat 1b, the sub valve body 2 remains seated on the first valve seat 1b.
- valve body 3 When the valve body 3 is in the valve open state, the piston speed of the shock absorber S is increased, and the differential pressure generated by the restriction passage 2b reaches the valve opening pressure for separating the sub valve body 2 from the first valve seat 1b. Then, the sub valve body 2 is also separated from the first valve seat 1b, and the port 1a is opened.
- the port 1a communicates directly with the reservoir 17 without passing through the restriction passage 2b, so that only the valve body 3 is in the open state.
- the channel area is larger than when the port 1a communicates with the reservoir 17 only through the restriction passage 2b. Therefore, as shown by the line Z in FIG. 3, the damping characteristic of the damping valve V is smaller in inclination than when only the valve body 3 is in the valve open state. That is, the attenuation coefficient is further reduced.
- the damping characteristic of the damping valve V is such that the line Y and the line Z are moved up and down within the range indicated by the broken line in FIG. Can be changed.
- the damping valve V can make the pressure increase ratio in the valve body 3 smaller than the pressure increase ratio in the sub valve body 2, whereby the valve opening pressure of the valve body 3 is higher than the valve opening pressure of the sub valve body 2. Get smaller. That is, the damping valve V relieves the port 1a in two stages. Therefore, in the damping valve V, the damping force at the low speed during the full soft time that minimizes the valve opening pressure of the pilot valve Pi can be reduced as compared with the conventional damping valve, and the damping force can be reduced.
- the variable range can be increased.
- the damping valve V of the present embodiment when the piston speed of the shock absorber S is in the low speed range, a soft damping force can be output and the damping force is not excessive.
- the upper limit of the hard damping force required when the piston speed is in the high speed range can be increased, and the damping force is not insufficient. Therefore, if the damping valve V is applied to the shock absorber S, the damping force variable range can be increased, and the riding comfort in the vehicle can be improved.
- the pilot valve Pi includes a pilot valve seat member 21 and a pilot valve body 22.
- the pilot valve seat member 21 includes a cylindrical valve accommodating cylinder 21a having a through hole 21c communicating between the inside and the outside, and an annular pilot valve seat 21d provided at an end of the valve accommodating cylinder 21a.
- the pilot valve body 22 is provided between the small diameter portion 22a, the large diameter portion 22b, and the small diameter portion 22a and the large diameter portion 22b, which are slidably inserted into the valve housing cylinder 21a, and is opposed to the through hole 21c.
- a recess 22c The pilot valve Pi is configured such that the end of the large-diameter portion 22b of the pilot valve body 21 is attached to and detached from the pilot valve seat 21d of the pilot valve seat member 21.
- the pilot valve Pi can reduce the pressure receiving area A in which the pressure acts in the direction in which the pilot valve body 22 comes out of the pilot valve seat member 21, and can increase the flow path area when the valve is opened. can do.
- the pilot valve body 22 is separated from the pilot valve seat 21d while the pressure receiving area receiving the pressure for separating the pilot valve body 22 from the pilot valve seat 21d is reduced.
- the channel area with respect to the quantity can be increased. Therefore, the convergence time of the pilot valve body 22 to the static balance position can be shortened as shown by the solid line in FIG. 5 without increasing the size of the actuator such as the solenoid Sol. There is no inconvenience. Furthermore, a steep damping force change of the damping valve V can be suppressed, and a stable damping force can be exhibited with high responsiveness.
- the pressure in the back pressure chamber P acts on the annular groove 20c provided on the outer periphery of the valve housing 20, and presses the ring 29 attached to the annular groove 20c so as to expand the diameter. For this reason, as the amount of current supplied to the solenoid Sol increases and the opening pressure of the pilot valve Pi increases, the frictional force generated between the spool 30 and the ring 29 slidably contacting the inner periphery of the spool 30 increases.
- the damping force variable range at the time of hardware is expanded, and the damping force suitable for the damping target is buffered. S can be generated.
- the ring 29 since the ring 29 has the bias cut 29a, the movement of the spool 30 can be further suppressed. Therefore, the effect of increasing the attenuation coefficient when the back pressure chamber P is set to a high pressure becomes remarkable, and the increase degree of the attenuation coefficient can be increased.
- the attenuation coefficient does not change as shown in FIG.
- the ring 29 since the ring 29 is always pressed toward the spool 30 by the pressure in the back pressure chamber P, the ring 29 exerts a function of sealing between the spool 30 and the valve housing 20. According to this, the pressure in the back pressure chamber P can be adjusted as intended regardless of the clearance between the spool 30 and the valve housing 20, so that the damping force generated by the damping valve V is stable without variation. To do.
- the sub valve body 2 is stacked on the valve seat member 1 and the valve body 3 is stacked on the sub valve body 2 to open the port 1a in two stages.
- Body 2 may be abolished.
- the valve body 3 is directly laminated on the first valve seat 1b of the valve seat member 1, the spool 30 is brought into contact with the back side of the valve body 3, and the pressure in the back pressure chamber P is
- the damping valve V causes the shock absorber S to exhibit a damping characteristic as shown in FIG.
- the internal pressure of the back pressure chamber P is controlled by applying a thrust according to the supply current to the solenoid Sol to the pilot valve Pi, and the sub valve body 2 and the valve body 3 are opened. Since the valve pressure is adjusted, the internal pressure of the back pressure chamber P can be adjusted without depending on the flow rate of the hydraulic oil flowing through the pilot passage 23. Therefore, even when the piston speed of the shock absorber S is in the low speed range, the change in the damping force with respect to the current supplied to the solenoid Sol becomes nearly linear, and the controllability is improved. Moreover, since the internal pressure of the back pressure chamber P for energizing the valve body 3 is controlled by applying a thrust according to the current supplied to the solenoid Sol to the pilot valve Pi, the variation in damping force can be reduced. .
- the damping valve V is cut off from the current supply to the solenoid Sol, the pilot valve body 22 is pressed by the coil spring 33, and the opening end of the fail valve seat member 34 opposite to the valve housing 20 is closed. It is done.
- the shock absorber S can function as a passive shock absorber.
- the damping characteristic of the shock absorber S during the failure can be arbitrarily set in advance.
- the solenoid Sol is used to drive the pilot valve body 22, but an actuator other than the solenoid Sol can also be used.
- the pilot valve Pi is a passive pressure control valve without controlling the valve opening pressure of the pilot valve Pi with an actuator such as a solenoid Sol, that is, even if the pressure control of the back pressure chamber P is not performed, the pilot Since the flow path area amount with respect to the separation amount of the valve body 22 from the pilot valve seat 21d can be increased, the stroke length of the coil spring 33 energizing the pilot valve body 22 can be shortened, and the increase in size of the damping valve can be suppressed. Even in this case, since the amount of overshoot and the convergence time in the displacement of the pilot valve body 22 can be reduced, the effect that a stable damping force can be exhibited is not lost.
- the pilot valve Pi is a passive pressure control valve, that is, when the pressure control of the back pressure chamber P is not performed, the pressure increase ratio in the valve body 3 should be smaller than the pressure increase ratio in the sub valve body 2. Can do.
- the damping characteristic of the shock absorber S can be changed in two stages, a soft damping force can be output when the piston speed is in a low speed range, and there is no excessive damping force, and the piston speed is high. When it becomes a range, a hard damping force can be output, and a deficiency in damping force can be resolved.
- the port 1a can be opened largely, and the attenuation coefficient when the sub valve body 2 is opened can be reduced. it can. Therefore, damping force control by the solenoid Sol becomes very easy.
- valve body 3 is a leaf valve having an annular shape
- the inner periphery is fixed to the valve seat member 1 and the outer periphery is attached to and detached from the second valve seat 2a
- the sub valve body 2 opens the port 1a.
- the sub-valve element 2 is urged to help the sub-valve element 2 return to the position where it is seated on the first valve seat 1b.
- valve body 3 can also be attached to the valve seat member 1 in a floating manner as a disc shape like the sub-valve body 2 of the present embodiment.
- the valve body 3 opens and the sub valve body 2 opens.
- the damping characteristic of the damping valve V can be made a relief characteristic in two stages.
- the 1st valve seat 1b and the 2nd valve seat 2a are both cyclic
- the first valve seat 1b and the second valve seat 2a can be designed to have an increased pressure ratio by being annular, but are not limited to an annular shape and can be of any shape.
- the damping valve V includes a back pressure chamber P provided on the side opposite to the main valve seat of the valve body 3 and urges the valve body 3 with the pressure in the back pressure chamber P. Therefore, by managing the dimensions of the members forming the back pressure chamber P, the valve opening pressure of the valve body 3 can be prevented from varying from product to product, and a stable urging force can be applied to the valve body 3, A large urging force can be applied to the valve body 3.
- the damping valve V includes a pilot passage 23 for reducing the pressure on the upstream side of the port 1a and leading it to the back chamber P. Therefore, the damping valve V uses the pressure on the upstream side of the port 1a to The valve opening pressure with the valve body 3 can be set.
- the damping force can be made variable by adjusting the valve opening pressure between the sub-valve body 2 and the valve body 3.
- the pressure of the port 1a is reduced and introduced into the back pressure chamber P by the orifice 1f provided in the pilot passage 23.
- the pressure is reduced by another valve such as a choke. You may do it.
- the sub-valve element 2 is annular, is slidably mounted on the outer periphery of the spacer 25, and is attached to the valve seat member 1 so as to be able to float.
- sub valve body urging means 50 for urging the sub valve body 2 toward the valve seat member 1 may be provided as in the damping valve V2 shown in FIG.
- the sub valve body urging means 50 is a disc spring and is interposed between the spacer 25 and the valve body 3 so that the sub valve body 2 is provided on the valve seat member 1. It is energized in the direction to be seated on 1b.
- the other members constituting the damping valve V2 are the same members as the members of the damping valve V, and the description thereof is duplicated. Therefore, the same reference numerals are given in the drawings and the detailed description thereof is omitted.
- the sub valve body 2 is urged by the sub valve body urging means 50, the sub valve body 2 is seated on the first valve seat 1b after the sub valve body 2 opens the port 1a. Can help return to position. Further, even when the valve body 3 and the sub-valve body 2 are separated from each other, the sub-valve body urging means 50 assists the returning operation of the sub-valve body 2, so that, for example, when the shock absorber S switches in the expansion / contraction direction The delay in closing the port 1a can be prevented, and the damping force generation response is further improved.
- the sub-valve urging means 50 only needs to exert an urging force so that the sub-valve 2 can be returned to the position where the sub-valve 2 is seated on the first valve seat 1b. It may be an elastic body.
- the sub-valve body biasing means can be incorporated in the valve body 51.
- the valve body 51 includes an annular outer ring portion 52 that is attached to and detached from the first valve seat 1b and includes a second valve seat 52a, and an annular inner ring portion 53 that functions as a sub-valve body biasing means.
- the other members constituting the damping valve V3 are the same members as the members of the damping valve V, and the description thereof is duplicated. Therefore, the same reference numerals are given in the drawings and the detailed description thereof is omitted.
- the sub-valve body 51 is mounted on the outer periphery of the assembly shaft 1c of the valve seat member 1 via an inner ring portion 53 formed of a thin plate on the inner peripheral side.
- an inner ring portion 53 formed of a thin plate on the inner peripheral side.
- the damping valve V3 spacers 54 and 55 are attached to the assembly shaft 1c instead of the spacer 25, and the inner periphery of the inner ring portion 53 is held by the spacers 54 and 55.
- the inner ring portion 53 is provided with a restriction passage 53a that functions as an orifice, and communicates the inter-valve chamber C with the port 1a.
- the outer ring portion 52 has an annular shape, and includes an annular second valve seat 52a provided on the outer periphery so as to protrude on the opposite side to the valve seat member 1, and an inner ring on the opposite side to the inner circumferential valve seat member 1.
- An annular recess 52b into which the outer periphery of the portion 53 is fitted is provided.
- the outer ring portion 52 is positioned in the radial direction by the inner ring portion 53 so that no deviation occurs.
- the inner ring portion 53 that functions as the sub valve body urging means is incorporated into the sub valve body 51 itself, the sub ring body 51 itself is urged by the inner ring portion 53, so that the outer ring portion 52 is After opening the port 1a, the outer ring portion 52 can be helped to return to the position where the outer ring portion 52 is seated on the first valve seat 1b.
- the inner ring portion 53 helps the returning operation of the outer ring portion 52, so that the port 1a is closed when the expansion / contraction direction of the shock absorber S is switched. Delay can be prevented, and damping force generation response is further improved.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
- Safety Valves (AREA)
- Fluid-Damping Devices (AREA)
- Fluid-Driven Valves (AREA)
- Details Of Valves (AREA)
Abstract
Description
Claims (12)
- 減衰弁であって、
ポートを備えた弁座部材と、
前記ポートを開閉する弁体と、
前記弁体を内部圧力で前記弁座部材側へ向けて附勢する背圧室と、
前記背圧室に前記ポートの上流側の圧力を減圧して導くパイロット通路と、
前記パイロット通路の途中に設けられて前記背圧室内の圧力を制御するパイロット弁と、
を備え、
前記パイロット弁は、
内外を連通するとともに前記ポートに通じる透孔が設けられた筒状の弁収容筒と、前記弁収容筒の端部に設けられた環状のパイロット弁座と、を有するパイロット弁座部材と、
大径部と、前記弁収容筒内に摺動自在に挿入される小径部と、前記大径部と前記小径部との間に設けられて前記透孔に対向する凹部と、を有するパイロット弁体と、
を備え、
前記パイロット弁座に前記大径部の端部を離着座させて、前記パイロット通路を開閉する減衰弁。 - 請求項1に記載の減衰弁であって、
前記弁収容筒は、有底筒状であって、前記パイロット弁体との間に空間を形成し、
前記パイロット弁体は、
一端から他端へと通じる連通路と、
前記連通路の途中に設けられたオリフィスと、
を備え、
前記連通路を介して前記空間を外部へ連通させた減衰弁。 - 請求項1に記載の減衰弁であって、
前記パイロット通路から分岐されるフェール通路と、
前記フェール通路の途中に設けられたフェール弁と、
をさらに備え、
前記パイロット弁は、前記パイロット弁体が前記パイロット弁座から最大限離間すると、前記パイロット通路における前記フェール通路との接続点よりも下流側を遮断する減衰弁。 - 請求項1に記載の減衰弁であって、
前記パイロット弁は、
前記パイロット弁体を前記パイロット弁座から離間する方向へ附勢するパイロット弁体附勢部材と、
前記パイロット弁体附勢部材に抗して前記パイロット弁体を前記パイロット弁座に着座させる方向に推力を作用させるソレノイドと、
をさらに備える減衰弁。 - 請求項1に記載の減衰弁であって、
前記弁座部材は、前記ポートを囲む第一弁座を有し、
前記第一弁座に離着座するとともに前記弁座部材とは反対側に第二弁座を有するサブ弁体をさらに備え、
前記弁体は、前記第二弁座に離着座し、前記サブ弁体とともに前記サブ弁体との間であって前記第二弁座の内周側に弁体間室を形成し、
前記ポートと前記弁体間室とを連通するとともに通過する流体の流れに抵抗を与える制限通路をさらに備え、
前記背圧室の内部圧力で前記弁体とともに前記サブ弁体を前記弁座部材側へ押圧する減衰弁。 - 請求項5に記載の減衰弁であって、
前記サブ弁体は、前記弁座部材に対して浮動可能に積層される減衰弁。 - 請求項5に記載の減衰弁であって、
前記サブ弁体を前記弁座部材側へ附勢するサブ弁体附勢手段をさらに備える減衰弁。 - 請求項5に記載の減衰弁であって、
前記第一弁座および前記第二弁座は、いずれも環状であって、前記第一弁座の内径よりも前記第二弁座の内径を大径に設定した減衰弁。 - 請求項5に記載の減衰弁であって、
前記制限通路は、前記サブ弁体に形成される減衰弁。 - 請求項1に記載の減衰弁であって、
前記弁体は、環状であって、内周が前記弁座部材に固定されて外周の撓みが許容されるリーフバルブである減衰弁。 - 請求項1に記載の減衰弁であって、
前記弁体の前記弁座部材とは反対側に当接する筒状のスプールと、
外周に前記スプールが軸方向に移動自在に装着されるスプール保持部材と、
前記スプール保持部材の外周に装着されて前記スプールの内周に摺接するリングと、
をさらに備え、
前記背圧室は、前記スプールと前記スプール保持部材とによって区画され、
前記リングの内周側に前記背圧室内の圧力を作用させた減衰弁。 - 請求項11に記載の減衰弁であって、
前記リングは、バイアスカットを有している減衰弁。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14763581.7A EP2975291B1 (en) | 2013-03-13 | 2014-03-12 | Damping valve |
US14/775,081 US9644760B2 (en) | 2013-03-13 | 2014-03-12 | Damping valve |
KR1020157025549A KR101673106B1 (ko) | 2013-03-13 | 2014-03-12 | 감쇠 밸브 |
ES14763581T ES2747632T3 (es) | 2013-03-13 | 2014-03-12 | Válvula de amortiguación |
CN201480014355.4A CN105190085B (zh) | 2013-03-13 | 2014-03-12 | 阻尼阀 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-050137 | 2013-03-13 | ||
JP2013050137A JP5952762B2 (ja) | 2013-03-13 | 2013-03-13 | 減衰弁 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014142191A1 true WO2014142191A1 (ja) | 2014-09-18 |
Family
ID=51536842
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/056547 WO2014142191A1 (ja) | 2013-03-13 | 2014-03-12 | 減衰弁 |
Country Status (7)
Country | Link |
---|---|
US (1) | US9644760B2 (ja) |
EP (1) | EP2975291B1 (ja) |
JP (1) | JP5952762B2 (ja) |
KR (1) | KR101673106B1 (ja) |
CN (1) | CN105190085B (ja) |
ES (1) | ES2747632T3 (ja) |
WO (1) | WO2014142191A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107850168A (zh) * | 2015-07-13 | 2018-03-27 | Kyb株式会社 | 阻尼阀和具备阻尼阀的缓冲器 |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5952761B2 (ja) * | 2013-03-13 | 2016-07-13 | Kyb株式会社 | 減衰弁 |
JP6101179B2 (ja) * | 2013-09-17 | 2017-03-22 | Kyb株式会社 | 減衰弁 |
JP6114667B2 (ja) * | 2013-09-17 | 2017-04-12 | Kyb株式会社 | 減衰弁 |
KR102348272B1 (ko) * | 2017-09-05 | 2022-01-10 | 히다치 아스테모 가부시키가이샤 | 완충기 |
CN111226046B (zh) * | 2018-03-09 | 2022-03-15 | Kyb株式会社 | 控制阀 |
EP3767126A4 (en) | 2018-03-13 | 2021-12-22 | KYB Corporation | VALVE DEVICE AND BUFFER |
JP7104530B2 (ja) | 2018-03-13 | 2022-07-21 | Kyb株式会社 | ソレノイド、電磁弁、及び緩衝器 |
DE102019105708B4 (de) * | 2019-03-06 | 2022-05-05 | Kendrion (Villingen) Gmbh | Druckregelventil und Vorrichtung mit einem derartigen Druckregelventil zum Steuern oder Regeln eines Drucks eines Druckfluids in einem Pilotdruckraum |
JP7377035B2 (ja) | 2019-09-09 | 2023-11-09 | カヤバ株式会社 | ソレノイド、電磁弁、及び緩衝器 |
JP7377036B2 (ja) | 2019-09-09 | 2023-11-09 | カヤバ株式会社 | ソレノイド、電磁弁、及び緩衝器 |
JP7377034B2 (ja) | 2019-09-09 | 2023-11-09 | カヤバ株式会社 | ソレノイド、電磁弁、及び緩衝器 |
JP7377037B2 (ja) * | 2019-09-09 | 2023-11-09 | カヤバ株式会社 | ソレノイド、電磁弁、及び緩衝器 |
JP7253514B2 (ja) * | 2020-03-27 | 2023-04-06 | 日立Astemo株式会社 | 緩衝器 |
JP2021173303A (ja) * | 2020-04-22 | 2021-11-01 | 日立Astemo株式会社 | バルブ駆動装置及びこれを用いた緩衝器 |
KR102435308B1 (ko) * | 2020-05-06 | 2022-08-23 | 주식회사 만도 | 감쇠력 가변식 쇽업소버 |
DE102020134820A1 (de) * | 2020-12-23 | 2022-06-23 | Ktm Ag | Ventilanordnung für einen Schwingungsdämpfer |
US20230107524A1 (en) * | 2021-10-01 | 2023-04-06 | Beijingwest Industries Co., Ltd. | Solenoid assembly |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11287281A (ja) * | 1998-03-31 | 1999-10-19 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
JP2000081072A (ja) * | 1998-06-26 | 2000-03-21 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
JP2001012534A (ja) * | 1999-06-30 | 2001-01-16 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
JP2009222136A (ja) | 2008-03-17 | 2009-10-01 | Kayaba Ind Co Ltd | 減衰弁 |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4785920A (en) * | 1986-04-16 | 1988-11-22 | Boge Ag | Hydraulic adjustable shock absorber |
US5261448A (en) * | 1989-11-16 | 1993-11-16 | Atsugi Unisia Corp. | Vibration mode responsive variable damping force shock absorber with feature of automatic selection of damping mode depending upon vibration mode of vehicular body |
DE4114305A1 (de) | 1990-12-08 | 1992-06-11 | Fichtel & Sachs Ag | Absperrventileinrichtung |
US5163706A (en) * | 1991-04-24 | 1992-11-17 | General Motors Corporation | Electro-hydraulic pressure regulating valve assembly for a hydraulic damper |
US5282645A (en) * | 1992-11-25 | 1994-02-01 | General Motors Corporation | Electro-hydraulic pressure regulating valve assembly mounted in a valve boss on a hydraulic damper |
JPH07158683A (ja) * | 1993-12-08 | 1995-06-20 | Kayaba Ind Co Ltd | 油圧緩衝器 |
CN2621962Y (zh) * | 2003-05-23 | 2004-06-30 | 王锡勇 | 阻尼力可调式减震器 |
KR20060041496A (ko) * | 2004-11-09 | 2006-05-12 | 주식회사 만도 | 쇽업소버의 감쇠력 가변 밸브 |
SE531736C2 (sv) | 2005-06-14 | 2009-07-28 | Oehlins Racing Ab | Arrangemang och anordning vid störeliminerande ventil för dämpare |
US20080185246A1 (en) * | 2007-02-02 | 2008-08-07 | Mando Corporation | Damping force variable shock absorber |
KR100834504B1 (ko) * | 2007-02-08 | 2008-06-02 | 주식회사 만도 | 쇽업소버의 감쇠력 가변식 밸브 |
KR101568042B1 (ko) * | 2008-03-31 | 2015-11-10 | 가부시끼가이샤 히다치 세이사꾸쇼 | 감쇠력 조정식 완충기 |
JP5120629B2 (ja) * | 2008-03-31 | 2013-01-16 | 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及びこれを用いたサスペンション制御装置 |
KR101288609B1 (ko) * | 2008-07-03 | 2013-07-22 | 주식회사 만도 | 쇽업소버의 감쇠력 가변 밸브 |
KR101254235B1 (ko) * | 2008-07-11 | 2013-04-18 | 주식회사 만도 | 쇽업소버의 감쇠력 가변 밸브 및 이를 이용한 쇽업소버 |
KR101254288B1 (ko) | 2008-08-21 | 2013-04-12 | 주식회사 만도 | 쇽업소버의 감쇠력 가변 밸브 |
JP5626638B2 (ja) * | 2010-09-29 | 2014-11-19 | 日立オートモティブシステムズ株式会社 | 緩衝器 |
-
2013
- 2013-03-13 JP JP2013050137A patent/JP5952762B2/ja active Active
-
2014
- 2014-03-12 WO PCT/JP2014/056547 patent/WO2014142191A1/ja active Application Filing
- 2014-03-12 EP EP14763581.7A patent/EP2975291B1/en active Active
- 2014-03-12 US US14/775,081 patent/US9644760B2/en active Active
- 2014-03-12 ES ES14763581T patent/ES2747632T3/es active Active
- 2014-03-12 KR KR1020157025549A patent/KR101673106B1/ko active IP Right Grant
- 2014-03-12 CN CN201480014355.4A patent/CN105190085B/zh active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11287281A (ja) * | 1998-03-31 | 1999-10-19 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
JP2000081072A (ja) * | 1998-06-26 | 2000-03-21 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
JP2001012534A (ja) * | 1999-06-30 | 2001-01-16 | Tokico Ltd | 減衰力調整式油圧緩衝器 |
JP2009222136A (ja) | 2008-03-17 | 2009-10-01 | Kayaba Ind Co Ltd | 減衰弁 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107850168A (zh) * | 2015-07-13 | 2018-03-27 | Kyb株式会社 | 阻尼阀和具备阻尼阀的缓冲器 |
Also Published As
Publication number | Publication date |
---|---|
JP5952762B2 (ja) | 2016-07-13 |
US9644760B2 (en) | 2017-05-09 |
EP2975291A1 (en) | 2016-01-20 |
JP2014173716A (ja) | 2014-09-22 |
KR20150121087A (ko) | 2015-10-28 |
CN105190085A (zh) | 2015-12-23 |
CN105190085B (zh) | 2017-09-01 |
US20160025237A1 (en) | 2016-01-28 |
EP2975291B1 (en) | 2019-08-21 |
KR101673106B1 (ko) | 2016-11-04 |
EP2975291A4 (en) | 2016-12-21 |
ES2747632T3 (es) | 2020-03-11 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2014142191A1 (ja) | 減衰弁 | |
WO2014142208A1 (ja) | 減衰弁 | |
WO2014142196A1 (ja) | 減衰弁 | |
JP6101179B2 (ja) | 減衰弁 | |
JP6130684B2 (ja) | ソレノイドバルブ | |
US9810280B2 (en) | Damping valve | |
JP6059548B2 (ja) | ソレノイドバルブ | |
JP6059549B2 (ja) | ソレノイドバルブ | |
JP7485579B2 (ja) | 減衰バルブおよび緩衝器 | |
JP7128759B2 (ja) | 圧力制御弁 | |
JP7132874B2 (ja) | 圧力制御弁 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201480014355.4 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14763581 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14775081 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 20157025549 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2014763581 Country of ref document: EP |