US20150014557A1 - Automatic transmission control valve body structure - Google Patents

Automatic transmission control valve body structure Download PDF

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Publication number
US20150014557A1
US20150014557A1 US14/375,253 US201314375253A US2015014557A1 US 20150014557 A1 US20150014557 A1 US 20150014557A1 US 201314375253 A US201314375253 A US 201314375253A US 2015014557 A1 US2015014557 A1 US 2015014557A1
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US
United States
Prior art keywords
orifice
valve body
separate plate
oil passage
control valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/375,253
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English (en)
Inventor
Masaru Shimada
Hideki Ishii
Masato Urushibata
Akio NONOMURA
Kenji Matsumoto
Hideki Nakazawa
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JATCO Ltd
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JATCO Ltd
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Filing date
Publication date
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Assigned to JATCO LTD reassignment JATCO LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ISHII, HIDEKI, MATSUMOTO, KENJI, NAKAZAWA, HIDEKI, Nonomura, Akio, SHIMADA, MASARU, URUSHIBATA, Masato
Publication of US20150014557A1 publication Critical patent/US20150014557A1/en
Abandoned legal-status Critical Current

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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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration
    • 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
    • F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0807—Manifolds
    • F15B13/081—Laminated constructions
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0871—Channels for fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/08—Influencing flow of fluids of jets leaving an orifice
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0003—Arrangement or mounting of elements of the control apparatus, e.g. valve assemblies or snapfittings of valves; Arrangements of the control unit on or in the transmission gearbox
    • F16H61/0009—Hydraulic control units for transmission control, e.g. assembly of valve plates or valve units
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0276—Elements specially adapted for hydraulic control units, e.g. 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • 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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2306/00—Other features of vehicle sub-units
    • B60Y2306/09—Reducing noise
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0276—Elements specially adapted for hydraulic control units, e.g. valves
    • F16H2061/0279—Details of hydraulic valves, e.g. lands, ports, spools or springs

Definitions

  • the present invention relates to a structure of a control valve body of an automatic transmission, and more particularly to a structure of anti-vibration measures of a separate plate of the control valve body.
  • FIG. 6 is a drawing for explaining an outline of an oil passage in a control valve body of an automatic transmission for a vehicle in a related art.
  • FIG. 6( a ) is a sectional view schematically showing the oil passage in the control valve body.
  • FIG. 6( b ) is a sectional view taken along an A-A line of FIG. 6( a ).
  • FIG. 6( c ) is an enlarged view of an area B in FIG. 6( a ), for explaining vibration of a separate plate.
  • FIG. 6( d ) is an enlarged explanatory view of an orifice adjacent area of the separate plate.
  • the control valve body of the vehicle automatic transmission has a basic structure in which a separate plate 120 is sandwiched between valve body enclosures 100 and 110 which are coupled together.
  • the valve body enclosures 100 and 110 have, on opposing surfaces thereof, channels 100 a and 110 a . Openings of these channels 100 a and 110 a are closed with the separate plate 120 sandwiched between the valve body enclosures 100 and 110 , thereby separating the channels 100 a and 110 a and defining oil passages 101 and 102 in which working fluid flows.
  • the control valve body is provided with a solenoid, a spool (both not shown), etc. besides the oil passage inside the control valve body.
  • the vehicle automatic transmission is configured so that the working fluid is supplied to a certain frictional engagement element by switching or changing the oil passage that provides the working fluid by driving the solenoid and the spool.
  • control valve body there is a spot by which one side oil passage 101 and the other side oil passage 102 sandwiching the separate plate 120 communicate with each other through an orifice 121 that is provided at the separate plate 120 .
  • the working fluid in the one side oil passage 101 is pushed out to the other side oil passage 102 through the orifice 121 of this spot.
  • the working fluid pushed out to the oil passage 102 through the orifice 121 moves along a center axis X of the orifice 121 , and forms a flow F1 (see FIG. 6 ( c )) of the working fluid which flows on an extended line of the orifice 121 along the center axis X. Since there is a difference in a velocity of the flow between this working fluid flow F1 and a flow F2 of the working fluid positioned outside the extended line of the orifice 121 , a vortex ring S caused by this flow velocity difference appears in the working fluid.
  • the vortex ring S formed in the oil passage 102 is formed cylindrically so as to surround the center axis X of the orifice 121 .
  • the vortex ring S formed in the oil passage 102 grows or develops while moving along the center axis X in a direction moving away from the orifice 121 .
  • a plurality of the vortex rings S continuously appear with the center axis X being a coaxial axis in a penetration direction (in an axial direction of the center axis X) of the orifice 121 .
  • the vortex ring S is a vortex that is different from a so-called Karman vortex.
  • the vortex ring S is a vortex that is generated, caused by the orifice 121 of the separate plate 120 , in the downstream side oil passage 102 , and is a vortex of a jet passing through the orifice 121 of the control valve body.
  • a section 120 a of the separate plate 120 which is adjacent to the orifice 121 , is not supported by being sandwiched between the valve body enclosures 100 and 110 , thus rigidity of the section 120 a in the penetration direction of the orifice 121 (in a direction orthogonal to the separate plate 120 ) is low. Therefore, when the pressure adjacent to the orifice 121 in the oil passage 102 fluctuates in the up-and-down directions, the section 120 a of the separate plate 120 , which is adjacent to the orifice 121 , vibrates in the penetration direction of the orifice 121 (see an arrow a in the drawing) due to this pressure fluctuation, then a noise resulting from this vibration might be generated.
  • Patent Document 1 Japanese Patent Provisional Publication No. 63-101355
  • An object of the present invention is to provide a structure that can adequately suppress the vibration at the section of the separate plate 120 , which is adjacent to the orifice formed at the separate plate 120 , and suppress the generation of the noise resulting from this vibration.
  • the present invention is, as described above, a structure of a control valve body of an automatic transmission, in which a separate plate is sandwiched between valve body enclosures. Then, channels are formed on opposing surfaces, which face to the separate plate, of the valve body enclosures located on both sides of the separate plate, and oil passages are defined by separating the channels by the separate plate, and one side oil passage and the other side oil passage located on both sides of the separate plate communicate with each other through an orifice that is provided at the separate plate.
  • a depth, at least in a part facing to the orifice, of the channel is set to be shallower than a depth of the channel that corresponds to an upstream side oil passage of the oil passages, and the depth h of the channel in the part facing to the orifice and a diameter d of the orifice are set so as to satisfy a relationship of h ⁇ 3d.
  • the depth h of the channel facing to the orifice is set to be shallower than a depth of the other channel, and also the depth his set, with respect to the diameter d of the orifice, so as to satisfy the relationship of h ⁇ 3d.
  • FIG. 1 is a sectional view showing a first embodiment of a control valve body structure according to the present invention.
  • FIG. 2 is an enlarged view of a main part of FIG. 1
  • FIG. 3 is a sectional view showing a second embodiment of the control valve body structure according to the present invention.
  • FIG. 4 is a sectional view showing a third embodiment of the control valve body structure according to the present invention.
  • FIG. 5 is a sectional view showing some modifications of the control valve body structure as a fourth embodiment of the present invention.
  • FIG. 6 is a sectional view for explaining an oil passage in the control valve body of an automatic transmission for a vehicle in a related art.
  • FIG. 1 shows a first embodiment of a control valve body structure according to the present invention.
  • FIG. 1( a ) is a sectional view of the control valve body structure.
  • FIG. 1( b ) is a sectional view taken along an A-A line of FIG. 1( a ).
  • FIG. 1( c ) is a sectional view taken along a C-C line of FIG. 1( a ).
  • FIG. 1( d ) is a sectional view taken along a B-B line of FIG. 1( a ).
  • FIG. 2( a ) is an enlarged view of an area D of FIG. 1( a ).
  • FIG. 2( b ) is a drawing for explaining formation of a vortex ring.
  • a control valve body 1 of an automatic transmission for a vehicle has a basic structure in which a separate plate 30 is sandwiched between valve body enclosures 10 and 20 which are coupled together.
  • the valve body enclosures 10 and 20 have, on opposing surfaces thereof, channels 10 a and 20 a . Openings of these channels 10 a and 20 a are closed with the separate plate 30 sandwiched between the valve body enclosures 10 and 20 , thereby separating the channels 10 a and 20 a and defining oil passages 11 and 21 in which working fluid flows.
  • control valve body there is a spot by which one side oil passage 11 and the other side oil passage 21 sandwiching the separate plate 30 communicate with each other through an orifice 31 that is provided at the separate plate 30 .
  • the working fluid in the one side oil passage 11 moves to the other side oil passage 21 through the orifice 31 of this spot.
  • the orifice 31 is formed into a small circular hole viewed from above, and has a diameter d.
  • the orifice 31 is formed by penetrating the separate plate 30 in a thickness direction (in a coupling direction of the valve body enclosures 10 and 20 ).
  • the working fluid coming from the oil passage 11 toward the oil passage 21 through the orifice 31 flows along a center axis X passing through a center of the orifice 31 in a penetration direction of the orifice 31 as shown by an arrow F1 in FIG. 2( a ).
  • a depth of the channel 20 a of the valve body enclosure 20 defining the oil passage 21 is different between in an area facing to the orifice 31 and its adjacent area and in the other area.
  • a depth h of the area facing to the orifice 31 and its adjacent area is shallower than a depth H1 of the other area.
  • a protruding section 22 that protrudes toward an opening side of the channel 20 a , namely toward the orifice 31 , is formed in the channel 20 a of the valve body enclosure 20 , then the depth of the channel 20 a becomes shallower by this protruding section 22 .
  • the protruding section 22 is formed integrally with the valve body enclosure 20 .
  • the protruding section 22 is provided directly below the orifice 31 and in a predetermined area ranging from a position directly below the orifice 31 to upstream and downstream sides in a longitudinal direction (i.e. in right and left directions in FIG. 1( a )) of the channel 20 a with a position of the orifice 31 being a reference.
  • An opposing surface 22 a of the protruding section 22 which faces to the separate plate 30 , has a flat surface that is parallel to the separate plate 30 , and this opposing surface 22 a is orthogonal to the penetration direction of the orifice 31 . That is, the opposing surface 22 a is parallel to the separate plate 30 on which the orifice 31 is formed, and an area of the opposing surface 22 a is wider than an area of the orifice 31 having the diameter d.
  • the depth h from the orifice 31 (a lower surface 30 b of the separate plate 30 ) to the opposing surface 22 a is set to be smaller (shallower) than a distance L that is required for a vortex ring S to be formed in the penetration direction of the orifice 31 (in an orthogonal direction to the separate plate 30 ).
  • this distance L simulation and an experimental result showed that the distance L is dependent on the diameter d of the orifice 31 and if the distance L exceeds a distance that is three times that of the diameter d of the orifice 31 , the vortex ring S is formed.
  • the working fluid flowing into the oil passage 21 through the orifice 31 and forming the flow (the arrow F1 in FIG. 2 ) toward the penetration direction of the orifice 31 in the oil passage 21 hits against or strikes the protruding section 22 , and as shown by an arrow F2 in FIG. 2 , the flow of the working fluid is bent or curved in a different direction from the penetration direction of the orifice 31 .
  • the flow of the working fluid is disturbed before the vortex ring S is generated, the vortex ring can therefore be prevented from continuously appearing in the penetration direction of the orifice 31 .
  • a high pressure area H whose pressure is higher than that of part where the protruding section 22 is not provided is formed directly below the orifice 31 . Since this high pressure area H is formed directly below the orifice 31 and in its vicinity, a pressure of an area R which is adjacent to the orifice 31 in the oil passage 21 becomes high. Consequently, in this condition, the flow of the working fluid that newly passes through the orifice 31 and forms the flow F1 toward the penetration direction of the orifice 31 is impeded by the high pressure until the flow of the working fluid passes through the orifice 31 and reaches the high pressure area H, and its flow velocity decreases.
  • anti-vibration measures of the separate plate 30 in the control valve body 1 of the automatic transmission are premised on the structure in which the control valve body 1 is formed by sandwiching the separate plate 30 between the valve body enclosures 10 and 20 which are coupled together. Then, the openings of the channels 10 a and 20 a formed on the respective opposing surfaces of the valve body enclosures 10 and 20 are closed with the separate plate 30 , and the oil passages 11 and 21 are formed on one side and the other side of the separate plate 30 .
  • the protruding section 22 protruding toward the opening side of the channel 20 a is provided in the channel 20 a , then the depth h of the area facing to the orifice 31 in the channel 20 a is set to be shallower than the depth H1 of the other area where the protruding section 22 is not provided.
  • the vibration of the section 30 a of the separate plate 30 which is adjacent to the orifice 31 , is suppressed and the noise resulting from the vibration can be suppressed. Therefore, there is no need for the control valve body to be machined more than necessary. As a consequence, the vibration and the generation of the noise resulting from the vibration can be suppressed without increasing a manufacturing cost.
  • the high pressure area H is formed directly below the orifice 31 , and the flow velocity of the working fluid forming the flow F1 toward the penetration direction of the orifice 31 decreases, then the flow velocity difference between the working fluid forming the flow F1 and the working fluid flowing outside the area positioned directly below the orifice 31 becomes small.
  • the vortex flow (the vortex ring) is generated in the oil passage 21 , it is the generation of the weak or poor vortex, then the vortex ring formed in the oil passage 21 becomes small.
  • the depth of the channel 20 a located directly below the orifice 31 becomes shallower than a depth required for the generation and the growth of the vortex ring, and flow of the working fluid is disturbed before the first vortex ring is generated directly below the orifice 31 . This thus prevents the vortex ring from continuously appearing in the penetration direction of the orifice 31 in the oil passage 21 .
  • the vortex ring S does not grow and is not continuously formed in the penetration direction of the orifice 31 .
  • the vortex flow (the vortex ring) is generated in the oil passage 21 , it is the generation of the weak or poor vortex, then the vortex ring formed in the oil passage 21 becomes small.
  • FIG. 3 is a drawing for explaining the protruding section according to the second embodiment.
  • FIG. 3( a ) is a sectional view of the control valve body when cut along the longitudinal direction of the oil passage 21 .
  • FIG. 3( b ) is a sectional view taken along an A-A line of FIG. 3( a ).
  • FIG. 3( c ) is an enlarged view of an area B of FIG. 3( a ).
  • a protruding section 25 of the present embodiment has a circular truncated cone shape.
  • the protruding section 25 is provided so that a top portion flat surface section 25 a having a small diameter faces toward the orifice 31 side on the center axis X passing through the center of the orifice 31 and extending in the penetration direction of the orifice 31 .
  • the top portion flat surface section 25 a has a flat surface that is parallel to the separate plate 30 , and is orthogonal to the moving or flowing direction (see an arrow F1 in the drawing) of the working fluid passing through the orifice 31 .
  • a depth h from the orifice 31 (the lower surface 30 b of the separate plate 30 ) to the top portion flat surface section 25 a is set to be smaller (shallower) than the distance L that is required for the first vortex ring to be formed in the penetration direction of the orifice 31 .
  • an area of the top portion flat surface section 25 a of the protruding section 25 is smaller than an area of the orifice 31 having the diameter d.
  • An outer peripheral surface 25 b of the protruding section 25 is inclined at a predetermined angle ⁇ with respect to the center axis X.
  • the working fluid flowing into the oil passage 21 through the orifice 31 is guided in a direction moving away from the center axis X by this outer peripheral surface 25 b , then the working fluid flow is converted to a flow of a direction which radially expands or spreads when viewed from the center axis X.
  • the depth h from the orifice 31 (the lower surface 30 b of the separate plate 30 ) to the top portion flat surface section 25 a which is the narrowest separation distance between the orifice 31 (the lower surface 30 b of the separate plate 30 ) and the protruding section 25 , is set to be smaller (shallower) than the distance L that is required for the first vortex ring to be formed in the penetration direction of the orifice 31 (i.e. h ⁇ 3d)
  • the flow of the working fluid is disturbed before the vortex ring is generated. It is therefore possible to prevent the vortex ring from continuously appearing in the penetration direction of the orifice 31 and prevent the vortex ring from growing.
  • the second embodiment has the structure in which the circular truncated cone-shaped protruding section 25 is formed in the position directly below the orifice 31 in the channel 20 a with the top portion flat surface section 25 a facing toward the orifice 31 side, and the depth h from the orifice 31 (the lower surface 30 b of the separate plate 30 ) to the top portion flat surface section 25 a is set to be smaller (shallower) than a depth H1 of the other area where the protruding section 25 is not provided.
  • the present embodiment shows, as an example, the circular truncated cone-shaped protruding section 25 , a conical shape or a cylindrical shape could be possible. Further, polygonal pyramid shape, polygonal truncated pyramid shape and polygonal prism shape such as quadrangular pyramid, truncated square pyramid and quadrangular prism could be possible. Also in this case, the same effect can be obtained.
  • FIG. 4 is a drawing for explaining the protruding section according to the third embodiment.
  • FIG. 4( a ) is a sectional view of the control valve body when cut along the longitudinal direction of the oil passage 21 .
  • FIG. 4( b ) is a sectional view taken along an A-A line of FIG. 4( a ).
  • FIG. 4( c ) is an enlarged view of an area B of FIG. 4( a ).
  • a protruding section 26 of this third embodiment is formed integrally with the valve body enclosure 20 .
  • the protruding section 26 is provided directly below the orifice 31 and in a predetermined area ranging from a position directly below the orifice 31 to upstream and downstream sides in a longitudinal direction (i.e. in right and left directions in FIG. 4( a )) of the channel 20 a.
  • An opposing surface 26 a of the protruding section 26 which faces to the separate plate 30 , is not parallel to the separate plate 30 , and has a flat inclined surface that is inclined at a predetermined angle 61 .
  • a separation distance from the lower surface 30 b of the separate plate 30 on the oil passage 21 side to the opposing surface 26 a of the protruding section 26 is greater, as a position on the opposing surface 26 a gets closer to the downstream side of the oil passage 21 .
  • a minimum depth h from the orifice 31 to the opposing surface 26 a in a part directly below the orifice 31 is set to be smaller (shallower) than the distance L that is required for the first vortex ring to be formed in the penetration direction of the orifice 31 .
  • an area of the opposing surface 26 a is greater than the area of the orifice 31 having the diameter d.
  • a flow direction of the working fluid flowing into the oil passage 21 through the orifice 31 and forming the flow (an arrow F1 in FIG. 4 ) toward the penetration direction of the orifice 31 in the oil passage 21 is bent or curved to a downward direction of the oil passage 21 by the opposing surface 26 a of the protruding section 26 (see an arrow F2).
  • the minimum depth h from the orifice 31 to the opposing surface 26 a is set to be smaller (shallower) than the distance L that is required for the first vortex ring to be formed in the penetration direction of the orifice 31 (i.e. h ⁇ 3d)
  • the flow of the working fluid is disturbed before the vortex ring is generated. It is therefore possible to prevent the vortex ring from continuously appearing in the penetration direction of the orifice 31 and prevent the vortex ring from growing.
  • a minimum depth h′ from the orifice 31 to the opposing surface 26 a is greater (deeper) than the minimum depth h in the upstream side U, and the vortex ring is formed more easily than the upstream side U.
  • the opposing surface 26 a is inclined so that the flow F2 of the working fluid whose moving or flowing direction is changed at the opposing surface 26 a in the upstream side U crosses the downstream side D, the generation of the vortex ring in the downstream side D is inhibited by this working fluid flow F2.
  • the high pressure area H is momentarily formed directly below the orifice 31 .
  • the protruding section 26 having the opposing surface 26 a that is inclined with respect to the separate plate 30 is formed directly below the orifice 31 and in its vicinity in the channel 20 a , and the depth h from the orifice 31 (the lower surface 30 b of the separate plate 30 ) to the opposing surface 26 a is greater, as the position on the opposing surface 26 a gets closer to the downstream side of the oil passage 21 .
  • FIG. 5 is a drawing for explaining the shape of the orifice and a speed (the velocity) of the working fluid in the downstream side oil passage.
  • FIG. 5( a ) is a drawing for explaining an orifice 35 having a substantially cruciform shape.
  • FIG. 5( c ) is a drawing for explaining an orifice 36 having an almost star shape.
  • FIG. 5( e ) is a drawing for explaining an orifice 37 having the other shape.
  • FIGS. 5( b ), 5 ( d ) and 5 ( f ) are drawings that show the speed (the velocity) of the flow of the working fluid formed in the downstream side oil passage by sizes of arrows. As can be appreciated from FIG.
  • each of the orifices 35 , 36 and 37 shown in FIGS. 5( a ), 5 ( c ) and 5 ( e ) is comprehensively an orifice whose plane shape is noncircular and has a substantially inner tooth shape.
  • the orifice 35 shown in FIG. 5( a ) has such shape that two long holes whose both ends have an R-shape are arranged with a phase of one of the two long holes shifted by 90 degrees on the center axis X, which is the substantially cruciform shape viewed from above.
  • a velocity difference which results from the passage cross-sectional area, between the working fluid passing through a middle area D1 where the two long holes cross and the working fluid passing through a peripheral area D2 that encloses the middle area D1 arises.
  • a flow velocity of a flow Fa of the working fluid passing through the middle area D1 is higher than that of a flow Fb of the working fluid passing through the peripheral area D2.
  • the generation and the growth of the vortex ring become noticeable when the velocity difference between the working fluid flowing directly below the orifice 35 and the working fluid flowing outside the area positioned directly below the orifice 35 is great.
  • the orifice 35 when looking at the flow of the working fluid in cross section of the line L1 (in cross section of the line L1, passing along the center axis X), the flow velocities Fa and Fb of the working fluid are lower from a middle of the orifice 35 toward a vicinity of the orifice 35 . Then, a difference from a flow velocity Fc of the working fluid flowing outside the area positioned directly below the orifice 35 becomes small (Fa>Fb>Fc). Therefore, the generation and the growth of the vortex ring in the oil passage 21 located on the downstream side of the orifice 35 can be suppressed as compared with the orifice 31 of the above embodiments.
  • a large flow velocity difference part (the cross section of the line L1) and a small flow velocity difference part (the cross section of the line L2) are alternately positioned on the center axis X of the orifice 35 . Then, the flow velocity difference becomes small as compared with the above embodiments. Thus, the generation and the growth of the vortex ring can be suppressed as compared with the orifice 31 of the above embodiments.
  • the substantially cruciform-shaped orifice 35 having such shape that the two long holes whose both ends have the R-shape are arranged with the phase of one of the two long holes shifted by 90 degrees on the center axis X, the generation and the growth of the vortex ring in the downstream side oil passage 21 can be suppressed. Then, the pressure of the area R adjacent to the orifice 35 of the separate plate 30 can be inhibited from periodically fluctuating in the up-and-down directions, and the generation of the noise caused by the fact that the section 30 a of the separate plate 30 , which is adjacent to the orifice 35 , vibrates can be prevented.
  • the orifice 36 shown in FIG. 5( c ) has the almost star shape viewed from above. Also in the case of the orifice 36 having this shape, a velocity difference, which results from the passage cross-sectional area, between the working fluid passing through a middle area D1 and the working fluid passing through a peripheral area D2 that encloses the middle area D1 arises. Then, as shown in FIG. 5( d ), in a part where the peripheral area D2 is provided in an area positioned directly below the orifice 36 , a difference from a flow velocity Fc of the working fluid flowing outside the area positioned directly below the orifice 36 becomes small (Fa>Fb>Fc). Therefore, the generation and the growth of the vortex ring in the oil passage 21 located on the downstream side of the orifice 36 can be suppressed as compared with the orifice 31 of the above embodiments.
  • a plurality of peripheral areas D2 are formed so that the peripheral areas D2 extend from a circumference of a middle area D1 formed by an imaginary circle Im1 in a direction moving away from the imaginary circle Im1.
  • Each peripheral area D2 has a different passage cross-sectional area, and is arranged at random on a center axis X of the orifice 37 .
  • the orifice 35 , 36 or 37 shown in FIG. 5 could be combined with the control valve body 1 having the protruding section 22 , 25 or 26 of the above embodiments. Also with this combination, it is possible to prevent the vortex ring from being continuously formed in an orthogonal direction of the orifice.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Control Of Transmission Device (AREA)
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JP2012-017950 2012-01-31
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KR101692597B1 (ko) 2017-01-03
WO2013115057A1 (ja) 2013-08-08
CN104094023B (zh) 2016-08-17
US9945496B2 (en) 2018-04-17
JPWO2013115057A1 (ja) 2015-05-11
EP2811206A1 (en) 2014-12-10
US20160363239A1 (en) 2016-12-15
KR20140111294A (ko) 2014-09-18
EP2811206A4 (en) 2015-10-14
CN104094023A (zh) 2014-10-08
JP5740011B2 (ja) 2015-06-24

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