WO2013111859A1 - スプール弁 - Google Patents
スプール弁 Download PDFInfo
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- WO2013111859A1 WO2013111859A1 PCT/JP2013/051605 JP2013051605W WO2013111859A1 WO 2013111859 A1 WO2013111859 A1 WO 2013111859A1 JP 2013051605 W JP2013051605 W JP 2013051605W WO 2013111859 A1 WO2013111859 A1 WO 2013111859A1
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- WIPO (PCT)
- Prior art keywords
- cylinder
- valve body
- peripheral surface
- valve
- throttle
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
- B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
- B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
- B60T13/16—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
- B60T13/161—Systems with master cylinder
- B60T13/162—Master cylinder mechanically coupled with booster
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T7/00—Brake-action initiating means
- B60T7/02—Brake-action initiating means for personal initiation
- B60T7/04—Brake-action initiating means for personal initiation foot actuated
- B60T7/042—Brake-action initiating means for personal initiation foot actuated by electrical means, e.g. using travel or force sensors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/06—Details
- F15B7/08—Input units; Master units
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- 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
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/8671—With annular passage [e.g., spool]
Definitions
- the present invention relates to a spool valve, for example, a spool valve suitable for a hydraulic brake device of a vehicle.
- a spool valve suitable for a hydraulic brake device for a vehicle is described in, for example, Patent Document 1 below, and includes a valve body (spool) and a cylinder having an inner hole that accommodates the valve body so as to be movable in the axial direction. (Sleeve).
- a supply valve port formed between the valve body and the cylinder opens, and the supply valve port passes through the supply valve port.
- the hydraulic fluid is configured to be introduced from the hydraulic pressure source into the hydraulic pressure chamber.
- the present invention is made to suppress the occurrence of the above-described oil hammer, and includes a valve body and a cylinder having an inner hole for movably housing the valve body in the axial direction, and is in an initial position.
- a supply valve port formed between the valve body and the cylinder opens, and the hydraulic pressure source is operated from the hydraulic pressure source to the hydraulic chamber through the supply valve port.
- a spool valve configured to introduce liquid, The effective throttle area until the axial movement amount from the initial position of the valve body reaches a predetermined value in the liquid path formed on the hydraulic pressure source side of the supply valve port or the liquid path formed on the hydraulic pressure chamber side Then, an opening area formed between the valve body and the cylinder is constant, and a restricting portion that increases the opening area is provided in the restricting invalid region exceeding a predetermined value.
- the throttle portion described above is provided in a liquid passage formed on the hydraulic pressure source side of the supply valve port or a liquid passage formed on the hydraulic pressure chamber side. For this reason, when the filling degree of the working fluid in the hydraulic pressure chamber is set to reach a certain level in the above-described throttling effective region of the restricting portion, the filling degree of the working fluid in the hydraulic pressure chamber reaches a certain level. As compared with the case where the throttle portion is not provided, the supply flow rate into the hydraulic pressure chamber can be reduced, and the occurrence of oil hammer in the hydraulic pressure chamber can be suppressed.
- the throttle portion described above suppresses the occurrence of oil hammer in the hydraulic pressure chamber, and the throttle invalid region where the axial movement amount from the initial position of the valve body exceeds a predetermined value. Then, the aperture area of the above-mentioned stop portion increases. For this reason, a fixed throttle is provided in the liquid passage formed on the hydraulic pressure source side of the supply valve port or the liquid passage formed on the hydraulic pressure chamber side, and the filling degree of the working fluid in the hydraulic pressure chamber becomes a certain level.
- the supply flow rate into the hydraulic chamber is reduced to such an extent that no oil hammer is generated (in this case, the supply flow rate is always reduced by a fixed throttle, the required supply fluid amount is reduced in the hydraulic chamber).
- the increase in the amount of axial movement of the valve body relative to the cylinder can be suppressed, It is possible to suppress an increase in the overall length of the spool valve as much as possible.
- the throttle portion is provided in a portion axially away from the outer peripheral surface end of the valve body forming the supply valve port, and the inner peripheral surface of the inner hole of the cylinder And an annular groove formed between the outer peripheral surface end of the valve body forming the supply valve port and the throttle forming surface, the throttle forming surface having a predetermined width formed on the outer peripheral surface of the valve body. Can also be formed. In this case, it is possible to appropriately set the effective aperture area by appropriately setting the axial length of the annular groove.
- the throttle portion is provided at a site axially away from the inner peripheral surface end of the inner hole of the cylinder that forms the supply valve port.
- the supply valve port is formed by an outer peripheral surface and a cylindrical protrusion having a predetermined thickness formed on the entire inner end of the communication hole formed in the cylinder and communicating with the inner hole of the cylinder at the inner end. It is also possible that a recess is formed between the inner peripheral end of the inner hole of the cylinder forming the cylinder and the cylindrical projection. In this case, it is possible to appropriately set the effective aperture area by appropriately setting the axial length of the recess.
- the communication hole and the cylindrical protrusion may be formed by a pipe that is liquid-tightly assembled to the cylinder.
- the throttle amount at the throttle portion it is possible to easily adjust the throttle amount at the throttle portion by changing the assembly amount (fitting amount) of the pipe to the cylinder.
- the throttle portion is provided at a site axially away from the inner peripheral surface end of the inner hole of the cylinder that forms the supply valve port.
- the cylinder between an outer peripheral surface, an inner end of a communication hole formed in the cylinder and communicating with an inner hole of the cylinder at an inner end, and an inner peripheral surface end of the cylinder forming the supply valve port.
- An inner hole of the cylinder forming the supply valve port which is formed by a flange-like protrusion that protrudes from the inner peripheral surface of the inner hole toward the outer peripheral surface of the valve body and extends annularly around the axis of the valve body
- a recess may be formed between the inner peripheral surface end and the flange-shaped protrusion. In this case, it is possible to appropriately set the effective aperture area by appropriately setting the axial length of the recess.
- FIG. 1 is a longitudinal side view schematically showing an embodiment (a first embodiment of a spool valve according to the present invention) in which a spool valve according to the present invention is applied to a hydraulic brake device for a vehicle.
- FIG. 2 is an enlarged cross-sectional view of the main part of the spool valve shown in FIG. 1, and FIG. 2A is a view when the valve body moves in the axial direction from the initial position and the throttle part starts to function (when So in FIG. (B) shows when the valve body is in the initial position, and (c) shows when the valve body has moved by a predetermined value in the axial direction from the initial position and the throttling portion has finished functioning (in S1 of FIG. 3).
- FIG. 3 is a diagram schematically showing the relationship between the valve body movement amount of the spool valve shown in FIG. 1 and the supply flow rate from the hydraulic pressure source to the hydraulic pressure chamber.
- FIG. 4 is an enlarged cross-sectional view of a main part showing a modified embodiment of the spool valve of the first embodiment shown in FIGS. 1 and 2, wherein (a) shows a state in which the valve body is in an initial position, b) shows the time when the valve body moves in the axial direction from the initial position and the throttle part starts to function, (c) shows the time when the throttle part is functioning, and (d) shows the initial state of the valve body.
- FIG. 5 is an enlarged sectional view of an essential part of a second embodiment of the spool valve according to the present invention.
- FIG. 6 is an enlarged cross-sectional view of a main part of a third embodiment of the spool valve according to the present invention.
- FIG. 7 is an enlarged cross-sectional view of a main part of a fourth embodiment of the spool valve according to the present invention.
- FIG. 1 to 3 show a first embodiment of a spool valve according to the present invention.
- the left side (vehicle) is shown by an input shaft IS in response to depression of a brake pedal BP.
- a valve body (spool) 11 that is pushed forward is accommodated in an inner hole 12a of a cylinder (sleeve piston) 12 so as to be movable in the axial direction.
- the cylinder 12 is assembled so as to be movable in the axial direction with respect to the housing 21, and the high pressure chamber R 1 always communicating with the hydraulic pressure source (accumulator) 31 and the low pressure always communicating with the reservoir 32 are included in the housing 21.
- a chamber R2 and a hydraulic chamber R3 communicating with the high pressure chamber R1 or the low pressure chamber R2 are formed according to the operation of the spool valve V1. The leftward movement of the valve body 11 and the cylinder 12 is transmitted to the piston 51 of the brake master cylinder 50 via the rod 41, the reaction rubber disk 42, the output shaft 43, etc. assembled to the cylinder 12. It is configured as follows.
- the spool valve V1 includes a valve body 11 and a cylinder 12, and a return spring 13 that is interposed between the valve body 11 and the cylinder 12 and biases the valve body 11 toward the initial position.
- the valve body 11 includes large-diameter shaft portions 11a and 11b having the same diameter, a medium-diameter shaft portion 11c, small-diameter shaft portions 11d, 11e, and 11f having the same diameter, and an annular groove 11g.
- a shaft hole portion 11h and communication holes 11i and 11j are provided.
- the right large-diameter shaft portion 11a is a portion that is slidably fitted in the axial direction with respect to the illustrated right end portion 12a1 in the inner hole 12a of the cylinder 12, and the discharge valve port is formed by the right end portion 12a1 of the inner hole 12a. Vo is formed.
- the left large-diameter shaft portion 11b is a portion that is slidably fitted in the illustrated intermediate portion 12a2 in the inner hole 12a of the cylinder 12 in the axial direction.
- the supply valve port is formed by the intermediate portion 12a2 of the inner hole 12a. Vi is formed.
- the medium-diameter shaft portion 11c is formed between the large-diameter shaft portions 11a and 11b, and the throttle portion O1 is formed by an inner peripheral surface of the inner hole 12a of the cylinder 12 at a throttle-forming surface having a predetermined width formed on the outer peripheral surface thereof. Is forming.
- the right small-diameter shaft portion 11 d is formed at the right end portion of the valve body 11 in the drawing, and is inserted into the right stepped hole portion 12 b of the cylinder 12 so as to be movable in the axial direction.
- the small-diameter shaft portion 11 e in the intermediate portion is formed between the large-diameter shaft portion 11 a and the medium-diameter shaft portion 11 c of the valve body 11 and can move in the axial direction within the inner hole 12 a of the cylinder 12.
- the left small-diameter shaft portion 11f is formed at the illustrated left end portion of the valve body 11, and is inserted through the left stepped hole portion 12c of the cylinder 12 so as to be movable in the axial direction.
- the shaft hole portion 11h is coaxially formed in the axial center portion of the valve body 11, and the right end in the drawing is opened and the left end in the drawing is closed.
- the right communication hole 11i is formed in the small-diameter shaft portion 11d, and always connects the right stepped hole portion 12b and the shaft hole portion 11h.
- the left communication hole 11j is formed in the small-diameter shaft portion 11f, and always connects the left stepped hole portion 12c and the shaft hole portion 11h.
- the discharge valve port Vo is formed between the valve body 11 and the cylinder 12, and is opened when the valve body 11 is in the initial position (the position shown in FIG. 2B), and the valve body in the initial position. 11 is configured to close by moving in the axial direction against the urging force of the return spring 13 with respect to the cylinder 12 (see FIGS. 2A, 2C, and 2D).
- the supply valve port Vi is formed between the valve body 11 and the cylinder 12, and is closed when the valve body 11 is in the initial position (the position shown in FIG. 2B), and the valve body in the initial position. 11 is configured to move in the axial direction against the urging force of the return spring 13 with respect to the cylinder 12, so that the discharge valve port Vo is closed and then opened.
- the restricting portion O1 is provided in a portion of the liquid passage formed on the hydraulic pressure chamber R3 side of the supply valve port Vi at a site that is separated from the outer peripheral surface end of the valve body 11 forming the supply valve port Vi in a required amount in the axial direction.
- the inner peripheral surface of the inner hole of the cylinder 12 and the throttle forming surface (the outer peripheral surface of the medium-diameter shaft portion 11c) having a predetermined width formed on the outer peripheral surface of the valve body 11 are formed.
- the opening area formed between the valve body 11 and the cylinder 12 is constant in the effective throttle area until the axial movement amount from the initial position of the valve body 11 reaches the predetermined value S1, and the predetermined area S1 In the stop invalid region exceeding the value S1, the aperture area is configured to increase.
- the overlap amount in the axial direction between the inner peripheral surface of the inner hole of the cylinder 12 forming the throttle portion O1 and the outer peripheral surface of the medium-diameter shaft portion 11c gradually decreases in the vicinity of the predetermined value S1, and reaches the predetermined value S1. Is set to zero.
- the cylinder 12 has inner holes 12a into which the large-diameter shaft portions 11a and 11b of the valve body 11 are slidably fitted in the axial direction, and stepped holes 12b and 12c formed at both ends of the inner hole 12a.
- the cylinder 12 has a communication hole 12d that always communicates the right end portion (the left side of the discharge valve port Vo) of the inner hole 12a with the hydraulic pressure chamber R3, and the intermediate portion of the inner hole 12a (the left side of the supply valve port Vi) is high pressure.
- a communication hole 12e that always communicates with the chamber R1 and a communication hole 12f that always communicates the large diameter portion of the stepped hole portion 12c with the low pressure chamber R2.
- the spool valve V1 has a discharge valve.
- the supply valve port Vi is opened, the fluid pressure chamber R3 is disconnected from the low pressure chamber R2 and communicated with the high pressure chamber R1, and the high pressure hydraulic fluid is transferred from the high pressure chamber R1 to the hydraulic pressure chamber R3. Is introduced. Therefore, the cylinder 12 is pushed forward, the piston 51 of the master cylinder 50 is pushed forward via the reaction force rubber disk 42 and the output shaft 43, and the desired brake operation is obtained.
- the working fluid is introduced from the high-pressure chamber R1 to the hydraulic chamber R3 through the communication hole 12e, the open supply valve port Vi, the communication hole 12d, and the like.
- the discharge valve port Vo is opened after the supply valve port Vi is closed in the spool valve V1, and the hydraulic pressure chamber R3 communicates with the high pressure chamber R1. Is communicated with the low-pressure chamber R2, and the hydraulic fluid is discharged from the hydraulic chamber R3 to the low-pressure chamber R2.
- the piston 51, the output shaft 43, the reaction force rubber disk 42, the spool valve V1, etc. of the master cylinder 50 are returned to the initial positions, and the brake operation is released.
- the hydraulic fluid is discharged from the hydraulic pressure chamber R3 to the low pressure chamber R2 through the communication hole 12d, the open discharge valve port Vo, the communication hole 11i, the shaft hole portion 11h, the communication hole 11j, the communication hole 12f, and the like. .
- the above-described throttle portion O1 is provided in the liquid passage formed on the hydraulic pressure chamber R3 side of the supply valve port Vi. Therefore, if the filling degree of the hydraulic fluid in the hydraulic pressure chamber R3 is set to reach a certain level in the effective throttle region (see FIG. 3) of the throttle portion O1 described above, the hydraulic fluid in the hydraulic pressure chamber R3.
- the supply flow rate into the hydraulic chamber R3 when the degree of filling reaches a certain level can be reduced as compared with the case where the throttle portion O1 is not provided, and the oil in the hydraulic chamber R3 can be reduced. It is possible to suppress the occurrence of hits.
- the occurrence of oil hammer in the hydraulic chamber R3 is suppressed by the throttle portion O1 described above, and the amount of axial movement of the valve body 11 from the initial position is suppressed.
- the aperture invalid region (see FIG. 3) where the value exceeds the predetermined value S1, the aperture area of the aperture O1 described above increases.
- a fixed throttle is provided in the liquid passage formed on the hydraulic pressure source side of the supply valve port Vi or the liquid passage formed on the hydraulic pressure chamber side, and the degree of filling of the hydraulic fluid in the hydraulic pressure chamber R3 has a certain degree.
- the supply flow rate into the hydraulic chamber R3 when reaching the level is reduced to such an extent that no oil hammer is generated (in this case, the supply flow rate is always reduced by a fixed throttle, so it is necessary in the hydraulic chamber R3)
- the axial movement amount (time) of the valve body relative to the cylinder needs to be increased by a necessary amount). It is possible to suppress the increase in the overall length of the spool valve V1 as much as possible.
- the throttle portion O1 is located at a site that is a required distance in the axial direction from the outer peripheral surface end (large diameter shaft portion 11b) of the valve body 11 that forms the supply valve port Vi. It is provided and is formed by an inner peripheral surface of the inner hole 12a of the cylinder 12 and a throttle forming surface having a predetermined width formed on the outer peripheral surface of the medium diameter shaft portion 11c of the valve body 11, and forms a supply valve port Vi.
- An annular groove 11g is formed between the outer peripheral surface end (large diameter shaft portion 11b) of the valve body 11 and the throttle forming surface (medium diameter shaft portion 11c). For this reason, it is possible to appropriately set the effective aperture area by appropriately setting the axial length of the annular groove 11g.
- the annular groove 11g and the throttle portion O1 are arranged so as to be close to the supply valve port Vi.
- the annular groove 11g and the throttle portion O1 are supplied. It is also possible to arrange and carry out a predetermined amount away from the valve port Vi.
- the valve portion A is provided between the supply valve port Vi and the throttle portion O1.
- the valve portion A is provided with an annular groove B in the inner hole 12 a of the cylinder 12 and an annular groove C in the large diameter shaft portion 11 b of the valve body 11 to ensure a space D between the valve body 11 and the cylinder 12. And is closed when the valve body 11 is in the initial position (see FIG. 4A) and opened when the throttle O1 starts to function (see FIG. 4B). ing. For this reason, in this modified embodiment, as the valve body 11 moves in the axial direction (movement leftward in FIG. 4), the hydraulic pressure is stepped between the supply valve port Vi and the throttle portion O1. Will change. Therefore, in this modified embodiment, it is possible to relax the clearance accuracy of the narrowed portion O1 as compared to the first embodiment described above.
- the opening area formed between the valve body 11 and the cylinder 12 is constant in the effective throttle area until the axial movement amount from the initial position of the valve body 11 reaches the predetermined value S1.
- the aperture ineffective area exceeding the predetermined value S1 is configured to increase the opening area (see FIG. 4D).
- the overlap amount in the axial direction between the inner peripheral surface of the inner hole of the cylinder 12 forming the throttle portion O1 and the outer peripheral surface of the medium-diameter shaft portion 11c gradually decreases in the vicinity of the predetermined value S1, and reaches the predetermined value S1. Is set to zero.
- the above-described throttle portion O1 is provided in the liquid passage formed on the hydraulic pressure chamber R3 side of the supply valve port Vi.
- the spool valve V3 of the third embodiment shown in FIG. 6, or the spool valve V4 of the fourth embodiment shown in FIG. It is also possible to implement the configuration in such a manner that the throttle portion O2, O3, or O4 is provided in the liquid path formed on the hydraulic pressure source (high pressure chamber R1) side.
- the throttle portion O2 of the second embodiment shown in FIG. 5 is provided in a portion axially away from the inner peripheral surface end of the inner hole 112a of the cylinder 112 that forms the supply valve port Vi.
- a cylindrical protrusion 112e1 of a predetermined thickness formed on the entire inner end of a communication hole 112e formed on the cylinder 112 and communicating with the inner hole 112a of the cylinder 112 at the inner end. Is formed.
- a recess 112g is formed between the inner peripheral surface end of the inner hole 112a of the cylinder 112 forming the supply valve port Vi and the cylindrical protrusion 112e1. For this reason, it is possible to appropriately set the effective aperture area by appropriately setting the axial length of the recess 112g.
- connection hole 112e and the cylindrical protrusion 112e1 are formed by a pipe P assembled liquid-tightly to the cylinder 112. Since the other configuration is substantially the same as the configuration of the aperture portion O2 of the second embodiment shown in FIG. 5, the description thereof is omitted.
- the third embodiment it is possible to easily adjust the throttle amount at the throttle portion O3 by changing (adjusting) the assembly amount (fitting amount) of the pipe P with respect to the cylinder 112.
- the throttle portion O4 of the fourth embodiment shown in FIG. 7 is provided at a site that is a required amount away from the inner peripheral surface end of the inner hole 112a of the cylinder 112 that forms the supply valve port Vi in the axial direction.
- a flange-like projection 112e1 having a predetermined width that protrudes from the inner peripheral surface of the inner hole 112a of the cylinder 112 toward the outer peripheral surface of the valve body 111 and extends annularly around the axis of the valve body 111 between the peripheral surface ends.
- an annular recess 112g is formed between the inner peripheral end of the inner hole 112a of the cylinder 112 forming the supply valve port Vi and the flange-like protrusion 112e1. For this reason, it is possible to appropriately set the effective aperture area by appropriately setting the axial length of the recess 112g.
- the large-diameter shaft portion 111b of the valve body 111 is used.
- a small diameter shaft portion 111e, a tapered portion 111k having a small diameter on the small diameter shaft portion side is formed. For this reason, it is possible to suppress the increase gradient of the supply flow rate in the restriction invalid region as compared with the first embodiment. Therefore, it is possible to similarly implement such a configuration (to form a tapered portion having a small diameter on the small diameter shaft portion side between the large diameter shaft portion and the small diameter shaft portion of the valve body) in the first embodiment. .
- the discharge valve port Vo formed between the valve body 11 and the cylinder 12 is closed by the valve body 11 in the initial position moving in the axial direction with respect to the cylinder 12.
- the timing at which the supply valve port (Vi) opens can be changed as appropriate.
- the supply valve port opens at the same time as the discharge valve port closes. It is also possible to set so that the supply valve port opens before the discharge valve port closes (immediately before).
- the present invention is applied to a spool valve that is applied to a hydraulic brake device of a vehicle, but the present invention is also applied to a spool valve that is applied to other various hydraulic devices.
- the present invention can be carried out in the same manner as or in accordance with the above-described embodiments, and is not limited to the above-described embodiments.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Sliding Valves (AREA)
- Braking Systems And Boosters (AREA)
- Details Of Valves (AREA)
- Check Valves (AREA)
- Multiple-Way Valves (AREA)
Abstract
Description
前記供給弁口の液圧源側に形成される液路または液圧室側に形成される液路に、前記弁体の初期位置からの軸方向移動量が所定値となるまでの絞り有効領域では前記弁体と前記シリンダとの間に形成される開口面積が一定であり、所定値を超える絞り無効領域では前記開口面積が増大する絞り部が設けられていることに特徴がある。
Claims (5)
- 弁体と、この弁体を軸方向に移動可能に収容する内孔を有するシリンダを備えていて、初期位置にある前記弁体が前記シリンダに対して軸方向に移動することにより、前記弁体と前記シリンダ間に形成されている供給弁口が開いて、この供給弁口を通して液圧源から液圧室に作動液が導入されるように構成されているスプール弁であって、
前記供給弁口の液圧源側に形成される液路または液圧室側に形成される液路に、前記弁体の初期位置からの軸方向移動量が所定値となるまでの絞り有効領域では前記弁体と前記シリンダとの間に形成される開口面積が一定であり、所定値を超える絞り無効領域では前記開口面積が増大する絞り部が設けられているスプール弁。 - 請求項1に記載のスプール弁において、
前記絞り部は、前記供給弁口を形成する前記弁体の外周面端から軸方向に所要量離れた部位に設けられていて、前記シリンダの内孔内周面と、前記弁体の外周面に形成された所定幅の絞り形成面によって形成されており、前記供給弁口を形成する前記弁体の外周面端と前記絞り形成面との間には環状溝が形成されていることを特徴とするスプール弁。 - 請求項1に記載のスプール弁において、
前記絞り部は、前記供給弁口を形成する前記シリンダの内孔内周面端から軸方向に所要量離れた部位に設けられていて、前記弁体の外周面と、前記シリンダに形成されて前記シリンダの内孔に内端にて連通する連通孔の内端全周に形成された所定肉厚の円筒状突起によって形成されており、前記供給弁口を形成する前記シリンダの内孔内周面端と前記円筒状突起との間には凹部が形成されていることを特徴とするスプール弁。 - 請求項3に記載のスプール弁において、
前記連通孔と前記円筒状突起は、前記シリンダに液密的に組付けたパイプによって形成されていることを特徴とするスプール弁。 - 請求項1に記載のスプール弁において、
前記絞り部は、前記供給弁口を形成する前記シリンダの内孔内周面端から軸方向に所要量離れた部位に設けられていて、前記弁体の外周面と、前記シリンダに形成されて前記シリンダの内孔に内端にて連通する連通孔の内端と前記供給弁口を形成する前記シリンダの内孔内周面端との間において前記シリンダの内孔内周面から前記弁体の外周面に向けて突出するとともに該弁体の軸周りに環状に延びるフランジ状突起によって形成されており、前記供給弁口を形成する前記シリンダの内孔内周面端と前記フランジ状突起との間には凹部が形成されていることを特徴とするスプール弁。
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DE201311000689 DE112013000689T5 (de) | 2012-01-25 | 2013-01-25 | Schieberventil |
US14/371,674 US9835260B2 (en) | 2012-01-25 | 2013-01-25 | Spool valve |
CN201380006388.XA CN104067041B (zh) | 2012-01-25 | 2013-01-25 | 滑阀 |
JP2013555319A JP5817847B2 (ja) | 2012-01-25 | 2013-01-25 | スプール弁 |
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WO2016010164A1 (ja) * | 2014-07-15 | 2016-01-21 | 株式会社アドヴィックス | 液圧制動装置 |
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DE102016107773A1 (de) * | 2016-03-09 | 2017-09-14 | Hilite Germany Gmbh | Hydraulikventil |
DE102016007881A1 (de) | 2016-06-28 | 2017-12-28 | Hydac Fluidtechnik Gmbh | Einrichtung zur Strömungskraft-Kompensation |
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- 2013-01-25 JP JP2013555319A patent/JP5817847B2/ja active Active
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CN104067041A (zh) | 2014-09-24 |
CN104067041B (zh) | 2016-05-18 |
US20150013808A1 (en) | 2015-01-15 |
JPWO2013111859A1 (ja) | 2015-05-11 |
DE112013000689T5 (de) | 2014-10-09 |
US9835260B2 (en) | 2017-12-05 |
JP5817847B2 (ja) | 2015-11-18 |
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