WO2015093395A1 - Negative-pressure-generating device - Google Patents

Negative-pressure-generating device Download PDF

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Publication number
WO2015093395A1
WO2015093395A1 PCT/JP2014/082866 JP2014082866W WO2015093395A1 WO 2015093395 A1 WO2015093395 A1 WO 2015093395A1 JP 2014082866 W JP2014082866 W JP 2014082866W WO 2015093395 A1 WO2015093395 A1 WO 2015093395A1
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WO
WIPO (PCT)
Prior art keywords
valve
negative pressure
intake passage
link
sectional area
Prior art date
Application number
PCT/JP2014/082866
Other languages
French (fr)
Japanese (ja)
Inventor
信悟 田畑
透 三澤
佑一 小池
Original Assignee
株式会社ミクニ
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社ミクニ filed Critical 株式会社ミクニ
Publication of WO2015093395A1 publication Critical patent/WO2015093395A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/04—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by mechanical control linkages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1035—Details of the valve housing
    • 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
    • F16K1/16—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 with pivoted closure-members
    • F16K1/18—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 with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—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 with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/221—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 with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves specially adapted operating means 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
    • 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
    • F16K1/52—Means for additional adjustment of the rate of flow
    • F16K1/526—Means for additional adjustment of the rate of flow for limiting the maximum flow rate, using a second valve
    • 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
    • F16K1/54—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
    • 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
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/0254—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor being operated by particular means
    • 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
    • F16K31/44—Mechanical actuating means
    • F16K31/52—Mechanical actuating means with crank, eccentric, or cam
    • F16K31/521—Mechanical actuating means with crank, eccentric, or cam comprising a pivoted disc or flap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F02D2009/0201—Arrangements; Control features; Details thereof
    • F02D2009/024—Increasing intake vacuum

Definitions

  • the present invention relates to a negative pressure generating device that generates a negative pressure by gas flowing through an intake passage.
  • An internal combustion engine such as an automobile is provided with a throttle body (negative pressure generator) into which intake air that has passed through an air cleaner, an intercooler, or the like is introduced.
  • the throttle body is provided with a butterfly throttle valve that opens and closes in conjunction with the operation of the accelerator pedal.
  • a configuration in which such a throttle valve is incorporated in an intake passage for example, there is one disclosed in Patent Document 1.
  • Patent Document 1 shows a configuration in which a venturi-shaped venturi section having a narrowed flow path is provided downstream of a throttle valve in a suction passage.
  • the venturi portion is fixedly provided.
  • the pressure loss becomes large, and the suction loss of the internal combustion engine may increase due to such pressure loss.
  • the diameter of the venturi portion is fixed, there is a region where the negative pressure cannot be sufficiently increased depending on the opening of the throttle valve.
  • the present invention has been made on the basis of the above circumstances, and its object is to provide a negative pressure generating device capable of reducing pressure loss and improving the negative pressure even at various throttle valve openings. It is intended to provide.
  • a negative pressure generating device capable of generating a negative pressure in an intake passage, which is provided in the intake passage and is changed by position change.
  • a first valve capable of changing the cross-sectional area of the flow path and a second valve provided on the downstream side of the first valve in the intake passage and capable of changing the cross-sectional area of the flow path by changing the position
  • interlocking means for causing the second valve to change its position by moving the interlocking part as the position of the first valve changes, and the interlocking means includes a flow of the intake passage.
  • a negative pressure generating device characterized in that when the road cross-sectional area is widened from the state in which the first valve is the narrowest, a play portion that does not cause a change in the position of the second valve is provided until the first opening degree. Is provided.
  • the venturi portion where the second valve is located is provided with a projecting member that projects in a direction to narrow the flow passage cross-sectional area of the venturi portion.
  • a projecting member that projects in a direction to narrow the flow passage cross-sectional area of the venturi portion.
  • the first valve is a throttle valve that changes a cross-sectional area of the flow path by rotating about a rotation shaft
  • the second valve is The slide valve is preferably a slide valve that changes the cross-sectional area of the flow path when it appears and disappears.
  • the interlocking unit is a link mechanism including a plurality of links, and two links among the plurality of links are connected to each other via a joint.
  • a joint is attached to one link, a joint is slidably inserted into the other link, and a long hole portion corresponding to the play portion is provided.
  • the second valve is inhaled by the urging means. It is preferable to be biased in the direction of narrowing the cross-sectional area of the passage.
  • the negative pressure generating device in the negative pressure generating device, it is possible to reduce the pressure loss and improve the negative pressure even at various opening degrees of the throttle valve.
  • FIG. 1 It is a perspective view which shows the structure of the throttle body which concerns on one embodiment of this invention. It is a perspective view which shows the half cross-sectional state of a structure of the throttle body of FIG. It is a perspective view which shows the structure of a slide valve with the throttle valve in the throttle body of FIG. It is a perspective view which shows the half cross-sectional state of the structure of the slide valve and storage housing
  • a throttle body 10 as a negative pressure generating device will be described with reference to the drawings.
  • an XYZ orthogonal coordinate system may be used for explanation, where the X direction is the direction in which the intake passage 21 flows, the X1 side is the upstream side to the downstream side, and the X2 side is the downstream side to the upstream side.
  • the Z direction is the direction in which the slide valve 50 moves, the Z1 side is the upper side (that is, the side where the intake passage 21 is opened), and the Z2 side is the opposite lower side (that is, the side where the intake passage 21 is closed).
  • the Y direction is a direction orthogonal to the X direction and the Z direction, the Y1 side is the right front side in FIG. 1, and the Y2 side is the left back side.
  • FIG. 1 is a perspective view showing the configuration of the throttle body 10.
  • FIG. 2 is a perspective view showing a half cross-sectional state of the configuration of the throttle body 10.
  • the throttle body 10 has a body portion 20 and a movable venturi portion 40.
  • the entire body portion 20 is integrally molded from, for example, metal or resin.
  • the body portion 20 is provided with an intake passage 21 through which a gas such as air flows.
  • the intake passage 21 is, for example, a pipe having a circular cross section, but may have a cross section other than a circle.
  • a throttle valve 30 as a first valve in the scope of claims is arranged via a rotary shaft 31.
  • the throttle valve 30 is provided in a disk shape having a diameter slightly smaller than the diameter of the intake passage 21.
  • the throttle valve 30 is a butterfly type in the present embodiment, and rotates (position changes) about the rotation shaft 31 in conjunction with an operation of an accelerator pedal (not shown). With this rotation, the throttle valve 30 changes the flow passage cross-sectional area of the portion of the intake passage 21 where the throttle valve 30 is located, and adjusts the gas flow rate.
  • the slide valve 50 as the second valve in the claims is located in the intake passage 21 on the downstream side (X1 side) of the throttle valve 30.
  • the slide valve 50 is a main component of the movable venturi unit 40, and slides in the vertical direction (Z direction) so as to protrude and retract with respect to the intake passage 21 (changes in position), whereby the flow path of the intake passage 21. Change the cross-sectional area. Therefore, in the throttle state of the slide valve 50, the negative pressure in the vicinity of the slide valve 50 in the intake passage 21 is increased.
  • FIG. 3 is a perspective view showing the configuration of the slide valve 50 together with the throttle valve 30.
  • the slide valve 50 is provided in a rectangular box-shaped cylindrical body, and a semicircular gap (referred to as a semicircular portion 53) is provided on the lower side (Z2 side). Is provided. That is, on the lower end side (Z2 side) of the slide valve 50, there is a pair of bottom wall portions 51 that abut against a locking bottom wall 614 described later, and a wall surface portion 52 between the pair of bottom wall portions 51 is , Curved upwards (depressed upwards). Thereby, a semicircular portion 53 is formed on the outer surface side of the wall surface portion 52 so that gas can be circulated even when the slide valve 50 is located at the lowest position (the narrowest state).
  • the front shape of the semicircular portion 53 is a semicircular shape.
  • both end sides in the X direction have a large channel cross-sectional area, but the channel cross-sectional area is gradually decreased from the both end sides toward the center side in the X direction. ing.
  • FIG. 4 is a perspective view showing a half cross-sectional state of the configuration of the slide valve 50 and the storage housing 60.
  • FIG. 5 is a perspective view showing a half cross-sectional state of the storage housing 60.
  • FIG. 6 is a cross-sectional view showing the throttle body 10 as viewed from the back in front (viewed from the X1 side to the X2 side), and is a view showing a cross section slightly closer to the X1 side than the protruding member 90.
  • a link mechanism 70 described later and a part of the protruding member 90 are also shown.
  • a protruding member 90 is also shown.
  • a link attachment portion 56 is provided on the lower side of the inner cylinder portion of the slide valve 50.
  • the link attachment portion 56 is a portion to which a joint 81 on the other end side of a fifth link 75 described later is attached in a rotatable state.
  • the slide valve 50 is housed in the housing housing 60, and the housing housing 60 is fixed to the X1 side of the body portion 20 via screws or the like.
  • the storage housing 60 is provided with a slide storage portion 61 and a link storage portion 62, and the upper portion is closed with a lid member 63.
  • the slide storage portion 61 is a portion that stores the slide valve 50 so as to be slidable in the vertical direction (Z direction).
  • the upper side (Z1 side) of the slide storage unit 61 is provided in a rectangular tube shape. However, a communication hole 611 passing through the outer wall of the slide storage portion 61 is provided on the lower side (Z2 side) of the slide storage portion 61 along the X direction.
  • the slide storage portion 61 stores the slide valve 50 for closing the intake passage 21, and the width (dimension in the Y direction) of the slide valve 50 is approximately the same as the diameter of the intake passage 21. Or slightly larger.
  • the lower side (Z2 side) of the slide storage unit 61 is curved and protrudes from the upper side (Z1 side).
  • part located below the slide valve 50 among the inner cylinder parts 612 is a part through which gas distribute
  • the above-described slide valve 50 can be regarded as a configuration that appears and disappears with respect to the intake passage 21.
  • the cylindrical inner cylinder part 612 of the slide storage part 61 is provided slightly larger than the slide valve 50, the dimensional difference between the inner cylinder part 612 and the slide valve 50 is such that the slide valve 50 does not rattle. It has become.
  • the slide storage portion 61 is provided wider than the link storage portion 62 (the dimension in the Y direction is larger), and both ends of the slide storage portion 61 in the Y direction are provided. It protrudes from the link storage part 62.
  • the slide storage portion 61 can cause the portion protruding from the link storage portion 62 to function as a groove portion that supports the slide of the slide valve 50.
  • a portion functioning as the groove portion is referred to as a sliding groove portion 613.
  • the sliding groove portion 613 is linearly provided in the vertical direction (Z direction) so that the width dimension (dimension in the Y direction) is constant also on the communication hole 611 side. .
  • the lower side (Z2 side) of the sliding groove 613 is positioned above the lower side (Z1 side) of the inner peripheral wall of the intake passage 21. That is, a locking bottom wall 614 for receiving the slide valve 50 is provided on the lower end side of the sliding groove 613, and the locking bottom wall 614 is higher than the lower side of the inner peripheral wall of the intake passage 21.
  • a gas flow passage (gap passage) other than the semicircular portion 53 is provided between the wall surface portion 52 of the slide valve 50 and the inner wall surface of the intake passage 21. 54).
  • a venturi portion 55 when referring to a gas flow passage including the semicircular portion 53 and the gap passage 54, it is referred to as a venturi portion 55.
  • the link storage unit 62 is a part that stores a part of the link mechanism 70 described later.
  • the link storage unit 62 is located on the X2 side with respect to the slide storage unit 61. Further, the inner cylinder part 621 of the link storage part 62 communicates with the inner cylinder part 612 of the slide storage part 61.
  • a hole-shaped shaft support portion 622 (see FIG. 1) for supporting a connecting shaft, which will be described later, is provided on the wall surface on the Y1 side of the link storage portion 62. Further, the wall surface on the Y2 side of the link storage portion 62 is provided with a concave shaft support portion 623 (see FIG. 5) that supports the end portion on the Y2 side of the connecting shaft.
  • the shaft support 623 is provided in a recess having a circular cross section. The two shaft support portions 622 and 623 are located on the same axis line in the Y direction.
  • the throttle valve 30 is provided so as to be capable of interlocking with the slide valve 50 via a link mechanism 70 serving as a hook interlocking means in the claims.
  • the slide valve 50 does not move from the time when the throttle valve 30 is most closed (the throttle is closed) without stepping on the accelerator pedal until a certain degree of opening (first opening). Maintain the most closed state (the slide closed state).
  • the slide valve 50 is also moved in the opening direction in synchronization.
  • the link mechanism 70 of the present embodiment has a total of five links 71 to 75.
  • the first link 71, the second link 72, the third link 73, the fourth link 74, and the fifth link 75 are directed from the rotary shaft 31 toward the slide valve 50.
  • Each link 71 to 75 corresponds to the interlocking unit in the claims.
  • the number of links constituting the link mechanism 70 may be any number as long as the above-described interlocking of the throttle valve 30 and the slide valve 50 can be realized, and other members may be appropriately combined. Below, the link mechanism 70 of this Embodiment is demonstrated concretely.
  • the first link 71 is fixed to the fixed pin portion 31 a of the rotating shaft 31, and the first link 71 rotates together with the rotating shaft 31.
  • a second link 72 is connected to the first link 71 via a joint 76.
  • a long hole portion 72a corresponding to the saddle clearance portion in the claims is provided on one end side of the second link 72, and the joint 76 fixedly provided on the first link 71 is movable. Is inserted into the long hole portion 72a.
  • the joint 76 may rotate with respect to the 1st link 71, a slide is impossible.
  • the other end side of the second link 72 is connected to one end side of the third link 73 via the joint 77, and the other end side of the third link 73 is rotatable to the pin portion 78 a of the connecting shaft 78. It is connected to.
  • the end of the connecting shaft 78 on the Y2 side is rotatably supported by the shaft supporting portion 623, and the connecting shaft 78 is rotatable to the shaft supporting portion 622 via the bearing 79 on the Y1 side of the shaft supporting portion 623. It is supported by.
  • the fourth link 74 is rotatably supported on the outer periphery of the connecting shaft 78 near the other end (close to Y2). That is, the fourth link 74 is connected to the third link 73 via the connecting shaft 78.
  • the fourth link 74 is curved to prevent interference with the bottom of the link storage portion 62. However, even if the fourth link 74 is not curved, if it does not interfere with the bottom of the link storage portion 62, or if interference does not cause a problem, it may be linear as with the other links 71 to 73, 75. good.
  • the other end side of the fourth link 74 is connected to one end side of the fifth link 75 via the joint 80, and the other end side of the fifth link 75 is connected to the link mounting portion 56 of the slide valve 50 with the joint 81. Is attached through.
  • an urging spring 82 corresponding to the urging means in the claims is provided.
  • the urging spring 82 applies an urging force toward which the slide valve 50 moves downward (Z2 side).
  • the urging spring 82 is a torsion coil spring, but other springs may be used.
  • One end portion 82a of the biasing spring 82 abuts on the inner wall of the link storage portion 62, and the other end portion 82b differs from the other portions of the biasing spring 82 while being bent along the Y direction.
  • 74 abuts on the upper side.
  • the biasing spring 82 applies a biasing force that pushes the slide valve 50 downward via the fourth link 74 and the fifth link 75.
  • a projecting member 90 is provided on the lower side of the intake passage 21 on the slide accommodating portion 61 side.
  • the protruding member 90 protrudes upward (Z1 side) in the intake passage 21.
  • the wall surface portion 91 on the upstream side (X2 side) of the intake passage 21 in the projecting member 90 is provided at an angle that is perpendicular to or close to perpendicular to the flow path direction (X direction).
  • an inclined portion 92 is provided so as to gradually go downward from the top portion 91a.
  • the inclined part 92 is provided with a negative pressure outlet 93.
  • the negative pressure outlet 93 is an outlet portion of a pipe line 94 that penetrates the protruding member 90 in the vertical direction (Z direction).
  • the wall surface part 91 inclines from the direction perpendicular
  • the protruding member 90 having the wall surface portion 91 is provided in the venturi portion 55 having a narrow channel cross-sectional area, and the negative pressure outlet 93 is provided in the inclined portion 92 on the downstream side (X1 side) from the wall surface portion 91.
  • the negative pressure at the negative pressure outlet 93 can be increased.
  • gases and liquids such as EGR gas can be injected from the negative pressure outlet 93 into the intake passage 21 by using the negative pressure generated in the vicinity of the negative pressure outlet 93.
  • the negative pressure used for various actuators can be supplied.
  • the configuration in which the fixed venturi portion is provided has a problem that the pressure loss increases when the throttle valve 30 rotates in the opening direction and the gas flow rate increases. Therefore, if the opening diameter of the fixed venturi is increased in order to reduce the pressure loss, there is a problem that a sufficient negative pressure cannot be obtained at the fixed venturi.
  • a slide valve 50 is provided in place of the fixed venturi portion in the portion where the fixed venturi portion of Patent Document 1 is provided.
  • the slide of the slide valve 50 is interlocked with the movement for adjusting the opening degree of the throttle valve 30.
  • the rotary shaft 31 rotates in conjunction with the movement, and the first link 71 also rotates. Move.
  • the joint 76 located on the other end side of the first link 71 enters the long hole portion 72a on the one end side of the second link 72, it does not move to the end portion 72a1 on the X1 side of the long hole portion 72a. Then, the second link 72 does not rotate. Then, up to the portion where the joint 76 collides with the end portion 72a1, the influence of the pressure loss generated in the throttle valve 30 is large, and even if the slide valve 50 does not exist, the pressure loss does not change so much. Yes.
  • the opening degree of the throttle valve 30 further increases after the joint 76 collides with the end portion 72 a 1
  • the slide valve 50 is more than the pressure loss at the throttle valve 30.
  • the effect of the pressure loss at is increased. That is, when the throttle valve 30 is opened and the flow rate is increased, the pressure loss at the slide valve 50 increases if the slide valve 50 remains closed.
  • the slide valve 50 moves upward (Z1 side) in conjunction with the movement of the throttle valve 30 in the opening direction.
  • the sliding amount of the slide valve 50 is set to such a degree that a large negative pressure can be secured while sliding so as not to increase the pressure loss with respect to the rotation of the throttle valve 30 in the opening direction.
  • the slide valve 50 is also positioned on the uppermost side (Z1 side).
  • FIG. 7 shows a pressure loss with respect to an increase in the gas flow rate when the opening of the throttle valve 30 is changed, and a position away from the throttle valve 30 by a distance corresponding to the slide valve 50 in the flow path direction (negative pressure measurement position). It is the figure which showed the relationship of the negative pressure in () in the graph.
  • the vertical axis represents the pressure value, and in the region where the pressure is higher than 0 (Pa), the pressure value of the pressure loss is shown, and the region where the pressure is lower than 0 (Pa). The negative pressure value is shown.
  • the horizontal axis represents the gas flow rate.
  • FIG. 7 shows a case where the opening degree of the throttle valve 30 is 15 degrees (left side) and 30 degrees (right side).
  • the case where the slide valve 50 is provided in addition to the throttle valve 30 clearly increases compared to the case where only the throttle valve 30 is provided. Specifically, when the opening degree of the throttle valve 30 is 15 degrees, the negative pressure increases by 22%, and when the opening degree of the throttle valve 30 is 30 degrees, the negative pressure increases by 24%. ing.
  • the slide valve 50 interlocking with the opening operation of the throttle valve 30 is provided, so that the negative pressure is increased while suppressing an increase in pressure loss.
  • a protruding member 90 is also provided. Therefore, the negative pressure can be further increased at the negative pressure outlet 93 on the downstream side of the wall surface portion 91 in the venturi portion 55 in which the flow path is narrowed.
  • the projecting member 90 exists even when the slide valve 50 moves upward (Z1 side) as the throttle valve 30 is greatly opened, thereby reducing the negative pressure at the venturi 55.
  • the negative pressure at the negative pressure outlet 93 can be increased.
  • FIG. 8 is a graph showing how the negative pressure at the negative pressure outlet 93 is increased due to the presence of the protruding member 90.
  • the broken line indicates a case where the protruding member 90 is not present, and the solid line indicates a case where the protruding member 90 is present.
  • FIG. 8 is a plot of negative pressure at the same air amount when the throttle valve 30 has an opening of 15 degrees, the opening of 30 degrees, and the throttle valve 30 is fully open.
  • the pressure at the negative pressure outlet 93 is increased when the protruding member 90 is present, compared with the case where the protruding member 90 is not present.
  • the slide of the slide valve 50 is interlocked with the adjustment of the opening degree of the throttle valve 30, and the negative pressure in the venturi portion 55 is increased while suppressing an increase in pressure loss. .
  • the slide valve 50 is provided in addition to the throttle valve 30.
  • the slide valve 50 flows in the intake passage 21 by a position change of sliding in the vertical direction.
  • the road cross-sectional area is changed. Therefore, as compared with the case where only the throttle valve 30 is present and the slide valve 50 is not present, the negative pressure at a site away from the throttle valve 30 by a distance corresponding to the venturi portion 55 is located downstream (X1 side). It becomes possible to raise.
  • the link mechanism 70 is provided so that the rotation of the throttle valve 30 and the slide valve 50 are synchronized with each other. Due to the presence of the link mechanism 70, the slide valve 50 can be reliably slid in conjunction with the rotation of the throttle valve 30. Further, when the link mechanism 70 is used, there is an advantage that it is easy to assemble, since there is no need for adjustment and the like as compared with the case where other means such as a wire is used.
  • the second link 72 is provided with a long hole portion 72a, and a joint 76 attached to the first link 71 is inserted into the long hole portion 72a.
  • the throttle valve 30 even if the throttle valve 30 is rotated from the most closed state in a direction to gradually open, it can be set to suppress an increase in pressure loss up to the first opening.
  • the slide valve 50 is slid upward (Z1 side) in conjunction with the opening of the throttle valve 30 so that the pressure loss does not increase. .
  • the venturi portion 55 is provided with a protruding member 90 protruding.
  • the projecting member 90 is provided with a wall surface 91 for generating a gas flow that bypasses the projecting member 90, a downstream side of the wall surface 91, and a base side of the projecting member 90 with respect to the top 91 a (Z 2).
  • a negative pressure outlet 93 located on the side).
  • the throttle valve 30 is used as the first valve, and the slide valve 50 is used as the second valve.
  • the slide of the slide valve 50 which forms the venturi part 55 can be efficiently interlocked with the throttle valve 30 interlocked with the operation of the accelerator pedal.
  • the link mechanism 70 is used as the interlocking means, and the second link 72 is provided with a long hole portion 72a, and the long hole portion 72a is attached to the first link 71.
  • the joint 76 is inserted.
  • the slide valve 50 is given a biasing force that always slides downward by the biasing spring 82. For this reason, even if the joint 76 is located in the intermediate part of the long hole part 72a, the state which the slide valve 50 closed most is maintainable.
  • the throttle valve 30 that rotates as the first valve is shown.
  • the first valve is not limited to the rotating valve, and may be another valve.
  • a sliding valve may be used.
  • the slide valve 50 is shown as the second valve.
  • this slide valve 50 may also be one that is added with a rotating operation instead of only a sliding operation.
  • the link mechanism 70 is described as an interlocking unit that interlocks the throttle valve 30 and the slide valve 50.
  • the interlocking means is not limited to the link mechanism 70, and other mechanisms and configurations may be used.
  • a slide of the slide valve 50 may be interlocked with the movement of the throttle valve 30 using a wire and a pulley.
  • the slide of the slide valve 50 may be interlocked with the movement of the throttle valve 30 by a gear mechanism, a cam mechanism, or a combination thereof.
  • the long hole portion 72a as the play portion is described.
  • the play portion is not limited to the long hole portion 72a.
  • a hole shape that does not penetrate may be used.
  • a gap portion such as a long hole portion may be provided in a portion other than the second link 72.
  • Throttle body (corresponding to negative pressure generating device), 20 ... Body portion, 21 ... Intake passage, 30 ... Throttle valve (corresponding to first valve), 31 ... Rotating shaft, 31a ... Fixed pin portion, 40 ... Movable venturi 50, slide valve (corresponding to the second valve), 51 ... bottom wall portion, 52 ... wall surface portion, 53 ... semicircular portion, 54 ... gap passage, 55 ... venturi portion, 56 ... link mounting portion, 60 ... storage Housing 61: Slide storage part 62 ... Link storage part 63 ... Lid member 70 ... Link mechanism (corresponding to interlocking means) 71-75 ... Link (first to fifth links; corresponding to interlocking part), 72a ...

Abstract

　Provided is a negative-pressure-generating device capable of reducing pressure loss, and also improving negative pressure in various opening degrees of a throttle valve. A negative-pressure-generating device (10) capable of producing negative pressure within an air intake passage (21), wherein the negative-pressure-generating device (10) is provided with: a first valve (30) provided inside the air intake passage (21), the first valve (30) being capable of changing channel cross-sectional area by changing position; a second valve (50) provided further downstream than the first valve (30) within the air intake passage (21), the second valve (50) being capable of changing channel cross-sectional area by changing position; and an interlocking means (70) having interlocking parts (71-75), the interlocking means (70) causing the second valve (50) to change position by the movement of the interlocking parts (71-75) along with the position change of the first valve (30), the interlocking means (70) being provided with a clearance part (72a) that does not cause the second valve (50) to change position to a first opening degree when the channel cross-sectional area of the air intake passage (21) enlarges from the furthest closed state of the first valve (30).

Description

負圧発生装置Negative pressure generator
　本発明は、吸気通路を流通する気体によって負圧を生じさせる負圧発生装置に関する。 The present invention relates to a negative pressure generating device that generates a negative pressure by gas flowing through an intake passage.
　自動車等の内燃機関には、エアクリーナやインタークーラ等を経た吸気が導入されるスロットルボディ（負圧発生装置）が設けられている。スロットルボディには、バタフライ方式のスロットルバルブが設けられていて、このスロットルバルブがアクセルペダルの動作に連動して開閉する。このようなスロットルバルブを吸気通路に組み込んだ構成としては、たとえば特許文献１に開示のものがある。 2. Description of the Related Art An internal combustion engine such as an automobile is provided with a throttle body (negative pressure generator) into which intake air that has passed through an air cleaner, an intercooler, or the like is introduced. The throttle body is provided with a butterfly throttle valve that opens and closes in conjunction with the operation of the accelerator pedal. As a configuration in which such a throttle valve is incorporated in an intake passage, for example, there is one disclosed in Patent Document 1.
　特許文献１には、吸引通路のうちスロットルバルブよりも下流側に、流路を絞ったベンチュリ形のベンチュリ部が設けられた構成が示されている。 Patent Document 1 shows a configuration in which a venturi-shaped venturi section having a narrowed flow path is provided downstream of a throttle valve in a suction passage.
特開２０００－３２９０１０号公報JP 2000-329010 A
　ところで、特許文献１に開示の構成では、ベンチュリ部は固定的に設けられている。しかしながら、かかる構成では、圧力損失が大きくなる虞があり、そのような圧力損失によって内燃機関の吸入損失を増やしてしまう場合がある。また、特許文献１に開示の構成においては、ベンチュリ部の径は固定的となっているため、スロットルバルブの開度によっては、負圧を十分に大きくできない領域が存在する。 Incidentally, in the configuration disclosed in Patent Document 1, the venturi portion is fixedly provided. However, in such a configuration, there is a possibility that the pressure loss becomes large, and the suction loss of the internal combustion engine may increase due to such pressure loss. In the configuration disclosed in Patent Document 1, since the diameter of the venturi portion is fixed, there is a region where the negative pressure cannot be sufficiently increased depending on the opening of the throttle valve.
　本発明は上記の事情にもとづきなされたもので、その目的とするところは、圧力損失を減らすこと、およびスロットルバルブの種々の開度においても負圧を向上させることが可能な負圧発生装置を提供しよう、とするものである。 The present invention has been made on the basis of the above circumstances, and its object is to provide a negative pressure generating device capable of reducing pressure loss and improving the negative pressure even at various throttle valve openings. It is intended to provide.
　上記課題を解決するために、本発明の第１の観点によると、吸気通路内で負圧を生じさせることが可能な負圧発生装置であって、吸気通路内に設けられると共に、位置変化によって流路断面積を変化させることが可能な第１バルブと、吸気通路内のうち第１バルブよりも下流側に設けられると共に、位置変化によって流路断面積を変化させることが可能な第２バルブと、連動部を有し、第１バルブの位置変化に伴って連動部が移動することで第２バルブに位置変化を生じさせる連動手段と、を具備し、連動手段には、吸気通路の流路断面積を第１バルブが最も狭めている状態から広がる場合、第１開度までは第２バルブの位置変化を生じさせない遊隙部が設けられている、ことを特徴とする負圧発生装置が提供される。 In order to solve the above problem, according to a first aspect of the present invention, a negative pressure generating device capable of generating a negative pressure in an intake passage, which is provided in the intake passage and is changed by position change. A first valve capable of changing the cross-sectional area of the flow path and a second valve provided on the downstream side of the first valve in the intake passage and capable of changing the cross-sectional area of the flow path by changing the position And interlocking means for causing the second valve to change its position by moving the interlocking part as the position of the first valve changes, and the interlocking means includes a flow of the intake passage. A negative pressure generating device characterized in that when the road cross-sectional area is widened from the state in which the first valve is the narrowest, a play portion that does not cause a change in the position of the second valve is provided until the first opening degree. Is provided.
　また、本発明の他の側面は、上述の発明において、第２バルブが位置するベンチュリ部には、当該ベンチュリ部の流路断面積を狭める向きに突出する突出部材が設けられていて、突出部材は、当該突出部材を迂回する気体の流れを生じさせる壁面部と、当該壁面部よりも下流側に設けられると共に壁面部の頂部よりも突出部材の付け根側に位置する負圧取出口と、を備える、ことが好ましい。 According to another aspect of the present invention, in the above-described invention, the venturi portion where the second valve is located is provided with a projecting member that projects in a direction to narrow the flow passage cross-sectional area of the venturi portion. Includes a wall surface portion that causes a gas flow that bypasses the projecting member, and a negative pressure outlet that is provided on the downstream side of the wall surface portion and located on the base side of the projecting member with respect to the top portion of the wall surface portion. It is preferable to provide.
　さらに、本発明の他の側面は、上述の発明において、第１バルブは、回転軸を中心に回転することで流路断面積を変化させるスロットルバルブであり、第２バルブは、吸気通路に対して出没することで流路断面積を変化させるスライドバルブである、ことが好ましい。 Further, according to another aspect of the present invention, in the above-described invention, the first valve is a throttle valve that changes a cross-sectional area of the flow path by rotating about a rotation shaft, and the second valve is The slide valve is preferably a slide valve that changes the cross-sectional area of the flow path when it appears and disappears.
　また、本発明の他の側面は、上述の発明において、連動手段は、複数のリンクから構成されるリンク機構であり、複数のリンクのうち、２つのリンクが互いにジョイントを介して接続されている部位については、一方のリンクにジョイントが取り付けられ、他方のリンクにはジョイントがスライド自在に挿入されると共に遊隙部に対応する長孔部が設けられ、第２バルブは、付勢手段によって吸気通路の流路断面積を狭める向きに付勢されている、ことが好ましい。 According to another aspect of the present invention, in the above-described invention, the interlocking unit is a link mechanism including a plurality of links, and two links among the plurality of links are connected to each other via a joint. As for the part, a joint is attached to one link, a joint is slidably inserted into the other link, and a long hole portion corresponding to the play portion is provided. The second valve is inhaled by the urging means. It is preferable to be biased in the direction of narrowing the cross-sectional area of the passage.
　本発明によると、負圧発生装置において、圧力損失を減らすこと、およびスロットルバルブの種々の開度においても負圧を向上させることが可能となる。 According to the present invention, in the negative pressure generating device, it is possible to reduce the pressure loss and improve the negative pressure even at various opening degrees of the throttle valve.
本発明の一実施の形態に係るスロットルボディの構成を示す斜視図である。It is a perspective view which shows the structure of the throttle body which concerns on one embodiment of this invention. 図１のスロットルボディの構成の半断面状態を示す斜視図である。It is a perspective view which shows the half cross-sectional state of a structure of the throttle body of FIG. 図１のスロットルボディにおけるスロットルバルブと共にスライドバルブの構成を示す斜視図である。It is a perspective view which shows the structure of a slide valve with the throttle valve in the throttle body of FIG. 図１のスロットルボディにおけるスライドバルブおよび収納筐体の構成の半断面状態を示す斜視図である。It is a perspective view which shows the half cross-sectional state of the structure of the slide valve and storage housing | casing in the throttle body of FIG. 図１のスロットルボディにおける収納筐体の半断面状態を示す斜視図である。It is a perspective view which shows the half cross-sectional state of the storage housing | casing in the throttle body of FIG. 図１のスロットルボディを背面から正面を見た（Ｘ１側からＸ２側を見た）状態を示す断面図であり、突出部材より若干Ｘ１側の断面を示す図である。It is sectional drawing which shows the state which looked at the front of the throttle body of FIG. 1 from the back (seen from X1 side to X2 side), and is a figure which shows the cross section slightly X1 side from a protrusion member. 図１のスロットルボディにおけるスロットルバルブの開度を変化させたときの、気体の流量増大に対する圧力損失と、スロットルバルブから流路方向にスライドバルブに対応する距離だけ離れた位置（負圧測定位置）での負圧の関係をグラフで示した図である。The pressure loss due to the increase in the gas flow rate when the throttle valve opening in the throttle body in FIG. 1 is changed, and the position away from the throttle valve by the distance corresponding to the slide valve in the flow path direction (negative pressure measurement position) It is the figure which showed the relationship of the negative pressure in a graph. 図１のスロットルボディにおける突出部材の存在によって負圧取出口での負圧が増加した様子をグラフで示した図であるIt is the figure which showed the mode that the negative pressure in a negative pressure extraction outlet increased by presence of the protrusion member in the throttle body of FIG.
　以下、本発明の一実施の形態に係る負圧発生装置としてのスロットルボディ１０について、図面に基づいて説明する。なお、以下の説明においては、ＸＹＺ直交座標系を用いて説明することがあるものとし、Ｘ方向は吸気通路２１の流れる方向とし、Ｘ１側は上流から下流に向かう側、Ｘ２側は下流から上流に向かう側とする。また、Ｚ方向をスライドバルブ５０の移動する方向とし、Ｚ１側は上方側（すなわち吸気通路２１が開放される側）とし、Ｚ２側はその逆の下方側（すなわち吸気通路２１が閉じる側）とする。さらにＹ方向はＸ方向およびＺ方向に直交する方向とし、Ｙ１側は図１において右手前側、Ｙ２側は左奥側とする。 Hereinafter, a throttle body 10 as a negative pressure generating device according to an embodiment of the present invention will be described with reference to the drawings. In the following description, an XYZ orthogonal coordinate system may be used for explanation, where the X direction is the direction in which the intake passage 21 flows, the X1 side is the upstream side to the downstream side, and the X2 side is the downstream side to the upstream side. The side going to. The Z direction is the direction in which the slide valve 50 moves, the Z1 side is the upper side (that is, the side where the intake passage 21 is opened), and the Z2 side is the opposite lower side (that is, the side where the intake passage 21 is closed). To do. Further, the Y direction is a direction orthogonal to the X direction and the Z direction, the Y1 side is the right front side in FIG. 1, and the Y2 side is the left back side.
＜スロットルボディ１０の構成について＞
　図１は、スロットルボディ１０の構成を示す斜視図である。また、図２は、スロットルボディ１０の構成の半断面状態を示す斜視図である。図１および図２に示すように、スロットルボディ１０は、ボディ部２０と、可動ベンチュリ部４０とを有している。ボディ部２０は、その全体が、たとえば金属や樹脂を材質として一体的に成型されている。ボディ部２０には、空気等の気体を流通させる吸気通路２１が設けられている。吸気通路２１は、たとえば断面形状が円形の管路であるが、円形以外の断面形状であっても良い。 <About the structure of the throttle body 10>
FIG. 1 is a perspective view showing the configuration of the throttle body 10. FIG. 2 is a perspective view showing a half cross-sectional state of the configuration of the throttle body 10. As shown in FIGS. 1 and 2, the throttle body 10 has a body portion 20 and a movable venturi portion 40. The entire body portion 20 is integrally molded from, for example, metal or resin. The body portion 20 is provided with an intake passage 21 through which a gas such as air flows. The intake passage 21 is, for example, a pipe having a circular cross section, but may have a cross section other than a circle.
　この吸気通路２１には、回転軸３１を介して、特許請求の範囲における 第１バルブとしてのスロットルバルブ３０が配置されている。スロットルバルブ３０は、吸気通路２１の直径よりも若干小さい直径の円盤形状に設けられている。スロットルバルブ３０は、本実施の形態ではバタフライ式であり、図示せぬアクセルペダルの操作に連動して、回転軸３１を中心に回動する（位置変化する）。かかる回動によりスロットルバルブ３０は、吸気通路２１のうちスロットルバルブ３０が位置する部位の流路断面積を変化させ、気体の流量を調整する。 In the intake passage 21, a throttle valve 30 as a first valve in the scope of claims is arranged via a rotary shaft 31. The throttle valve 30 is provided in a disk shape having a diameter slightly smaller than the diameter of the intake passage 21. The throttle valve 30 is a butterfly type in the present embodiment, and rotates (position changes) about the rotation shaft 31 in conjunction with an operation of an accelerator pedal (not shown). With this rotation, the throttle valve 30 changes the flow passage cross-sectional area of the portion of the intake passage 21 where the throttle valve 30 is located, and adjusts the gas flow rate.
　吸気通路２１のうちスロットルバルブ３０よりも下流側（Ｘ１側）には、特許請求の範囲における第２バルブとしてのスライドバルブ５０が位置している。スライドバルブ５０は、可動ベンチュリ部４０の主要な構成要素であり、吸気通路２１に対して出没するように上下方向（Ｚ方向）にスライドする（位置変化する）ことで、吸気通路２１の流路断面積を変化させる。そのため、スライドバルブ５０の絞り状態では、吸気通路２１内のスライドバルブ５０の近傍での負圧を増大させる。 The slide valve 50 as the second valve in the claims is located in the intake passage 21 on the downstream side (X1 side) of the throttle valve 30. The slide valve 50 is a main component of the movable venturi unit 40, and slides in the vertical direction (Z direction) so as to protrude and retract with respect to the intake passage 21 (changes in position), whereby the flow path of the intake passage 21. Change the cross-sectional area. Therefore, in the throttle state of the slide valve 50, the negative pressure in the vicinity of the slide valve 50 in the intake passage 21 is increased.
　図３は、スロットルバルブ３０と共にスライドバルブ５０の構成を示す斜視図である。図３に示すように、スライドバルブ５０は、矩形箱形の筒状体に設けられているが、その下方側（Ｚ２側）には、半円状の空隙（半円部５３とする）が設けられている。すなわち、スライドバルブ５０の下端側（Ｚ２側）には、後述する係止底壁６１４に当接する一対の底壁部５１が存在すると共に、その一対の底壁部５１の間の壁面部５２は、上方に向かい湾曲している（上方に向かい窪んでいる）。それにより、壁面部５２の外面側には、スライドバルブ５０が最も下方に位置する状態（最も狭めている状態）でも、気体を流通させることが可能な半円部５３が形成されている。 FIG. 3 is a perspective view showing the configuration of the slide valve 50 together with the throttle valve 30. As shown in FIG. 3, the slide valve 50 is provided in a rectangular box-shaped cylindrical body, and a semicircular gap (referred to as a semicircular portion 53) is provided on the lower side (Z2 side). Is provided. That is, on the lower end side (Z2 side) of the slide valve 50, there is a pair of bottom wall portions 51 that abut against a locking bottom wall 614 described later, and a wall surface portion 52 between the pair of bottom wall portions 51 is , Curved upwards (depressed upwards). Thereby, a semicircular portion 53 is formed on the outer surface side of the wall surface portion 52 so that gas can be circulated even when the slide valve 50 is located at the lowest position (the narrowest state).
　本実施の形態では、半円部５３の正面形状は半円形状となっている。また、半円部５３のうち、Ｘ方向の両端側は、流路断面積が大きいが、その両端側からＸ方向の中央側に向かうにつれて、徐々に流路断面積が小さくなるように設けられている。 In the present embodiment, the front shape of the semicircular portion 53 is a semicircular shape. In addition, in the semicircular portion 53, both end sides in the X direction have a large channel cross-sectional area, but the channel cross-sectional area is gradually decreased from the both end sides toward the center side in the X direction. ing.
　図４は、スライドバルブ５０および収納筐体６０の構成の半断面状態を示す斜視図である。図５は、収納筐体６０の半断面状態を示す斜視図である。また、図６は、スロットルボディ１０を背面から正面を見た（Ｘ１側からＸ２側を見た）状態を示す断面図であり、突出部材９０より若干Ｘ１側の断面を示す図である。なお、図４では、後述するリンク機構７０や、突出部材９０の一部も示されている。また、図５では、突出部材９０も示されている。 FIG. 4 is a perspective view showing a half cross-sectional state of the configuration of the slide valve 50 and the storage housing 60. FIG. 5 is a perspective view showing a half cross-sectional state of the storage housing 60. FIG. 6 is a cross-sectional view showing the throttle body 10 as viewed from the back in front (viewed from the X1 side to the X2 side), and is a view showing a cross section slightly closer to the X1 side than the protruding member 90. In FIG. 4, a link mechanism 70 described later and a part of the protruding member 90 are also shown. Further, in FIG. 5, a protruding member 90 is also shown.
　図４に示すように、スライドバルブ５０の内筒部分の下方側には、リンク取付部５６が設けられている。リンク取付部５６は、後述する第５リンク７５の他端側のジョイント８１が回動自在な状態で取り付けられる部分である。 As shown in FIG. 4, a link attachment portion 56 is provided on the lower side of the inner cylinder portion of the slide valve 50. The link attachment portion 56 is a portion to which a joint 81 on the other end side of a fifth link 75 described later is attached in a rotatable state.
　スライドバルブ５０は、収納筐体６０に収納されているが、その収納筐体６０は、ボディ部２０のＸ１側にネジ等を介して固定されている。収納筐体６０には、スライド収納部６１とリンク収納部６２とが設けられていて、上方が蓋部材６３で閉塞されている。スライド収納部６１は、スライドバルブ５０を上下方向（Ｚ方向）にスライド自在に収納する部分である。 The slide valve 50 is housed in the housing housing 60, and the housing housing 60 is fixed to the X1 side of the body portion 20 via screws or the like. The storage housing 60 is provided with a slide storage portion 61 and a link storage portion 62, and the upper portion is closed with a lid member 63. The slide storage portion 61 is a portion that stores the slide valve 50 so as to be slidable in the vertical direction (Z direction).
　スライド収納部６１の上方側（Ｚ１側）は、矩形の筒状に設けられている。しかし、スライド収納部６１の下方側（Ｚ２側）には、当該スライド収納部６１の外壁を貫く連通孔６１１がＸ方向に沿うように設けられている。加えて、上記のようにスライド収納部６１には、吸気通路２１を閉じるためのスライドバルブ５０が収納され、そのスライドバルブ５０の幅（Ｙ方向の寸法）は、吸気通路２１の直径と同程度か、若干大きい。また、スライド収納部６１の下方側（Ｚ２側）は、上方側（Ｚ１側）よりも湾曲して張り出している。 The upper side (Z1 side) of the slide storage unit 61 is provided in a rectangular tube shape. However, a communication hole 611 passing through the outer wall of the slide storage portion 61 is provided on the lower side (Z2 side) of the slide storage portion 61 along the X direction. In addition, as described above, the slide storage portion 61 stores the slide valve 50 for closing the intake passage 21, and the width (dimension in the Y direction) of the slide valve 50 is approximately the same as the diameter of the intake passage 21. Or slightly larger. Further, the lower side (Z2 side) of the slide storage unit 61 is curved and protrudes from the upper side (Z1 side).
　なお、内筒部６１２のうちスライドバルブ５０よりも下方に位置する部位は、気体が流通する部分である。したがって、この部位は、スライド収納部６１の内部でありながらも、ボディ部２０の吸気通路２１と同一視することが可能である。そのため、以下の説明では、内筒部６１２のうちスライドバルブ５０よりも下方側の部位も、吸気通路２１として説明する。上述のスライドバルブ５０は、吸気通路２１に対して出没する構成と見立てることも可能である。 In addition, the site | part located below the slide valve 50 among the inner cylinder parts 612 is a part through which gas distribute | circulates. Therefore, this portion can be identified with the intake passage 21 of the body portion 20 while being inside the slide storage portion 61. Therefore, in the following description, the part below the slide valve 50 in the inner cylinder portion 612 is also described as the intake passage 21. The above-described slide valve 50 can be regarded as a configuration that appears and disappears with respect to the intake passage 21.
　スライド収納部６１の筒状の内筒部６１２は、スライドバルブ５０よりも僅かに大きく設けられているが、内筒部６１２とスライドバルブ５０の寸法差は、スライドバルブ５０をガタ付かせない程度となっている。 Although the cylindrical inner cylinder part 612 of the slide storage part 61 is provided slightly larger than the slide valve 50, the dimensional difference between the inner cylinder part 612 and the slide valve 50 is such that the slide valve 50 does not rattle. It has become.
　また、図４～図６に示すように、スライド収納部６１は、リンク収納部６２よりも幅広に（Ｙ方向の寸法が大きく）設けられていて、しかもスライド収納部６１のＹ方向の両端側がリンク収納部６２よりも突出している。それにより、スライド収納部６１は、リンク収納部６２よりも突出している部分を、スライドバルブ５０のスライドを支持する溝部として機能させることができる。以下では、この溝部として機能する部分を、摺動溝部６１３とする。この摺動溝部６１３は、図５に示すように、連通孔６１１側においても、幅寸法（Ｙ方向の寸法）が一定となるように、上下方向（Ｚ方向）において直線状に設けられている。 Further, as shown in FIGS. 4 to 6, the slide storage portion 61 is provided wider than the link storage portion 62 (the dimension in the Y direction is larger), and both ends of the slide storage portion 61 in the Y direction are provided. It protrudes from the link storage part 62. As a result, the slide storage portion 61 can cause the portion protruding from the link storage portion 62 to function as a groove portion that supports the slide of the slide valve 50. Hereinafter, a portion functioning as the groove portion is referred to as a sliding groove portion 613. As shown in FIG. 5, the sliding groove portion 613 is linearly provided in the vertical direction (Z direction) so that the width dimension (dimension in the Y direction) is constant also on the communication hole 611 side. .
　ここで、図５に示すように、摺動溝部６１３の下方側（Ｚ２側）は、吸気通路２１の内周壁の下方側よりも上方側（Ｚ１側）に位置している。すなわち、摺動溝部６１３の下端側には、スライドバルブ５０を受け止めるための係止底壁６１４が設けられていて、その係止底壁６１４は、吸気通路２１の内周壁の下方側よりも高い位置に設けられている。そのため、スライドバルブ５０が摺動溝部６１３の下端側に位置した場合、スライドバルブ５０の壁面部５２と吸気通路２１の内壁面との間に、半円部５３以外の気体の流通路（隙間通路５４とする）が形成される。以後の説明では、半円部５３と隙間通路５４とを含めた気体の流通路を指す場合には、ベンチュリ部５５とする。 Here, as shown in FIG. 5, the lower side (Z2 side) of the sliding groove 613 is positioned above the lower side (Z1 side) of the inner peripheral wall of the intake passage 21. That is, a locking bottom wall 614 for receiving the slide valve 50 is provided on the lower end side of the sliding groove 613, and the locking bottom wall 614 is higher than the lower side of the inner peripheral wall of the intake passage 21. In the position. Therefore, when the slide valve 50 is positioned on the lower end side of the slide groove portion 613, a gas flow passage (gap passage) other than the semicircular portion 53 is provided between the wall surface portion 52 of the slide valve 50 and the inner wall surface of the intake passage 21. 54). In the following description, when referring to a gas flow passage including the semicircular portion 53 and the gap passage 54, it is referred to as a venturi portion 55.
　また、リンク収納部６２は、後述するリンク機構７０の一部を収納する部分である。本実施の形態では、リンク収納部６２は、スライド収納部６１よりもＸ２側に位置している。また、リンク収納部６２の内筒部６２１は、スライド収納部６１の内筒部６１２と連通している。 The link storage unit 62 is a part that stores a part of the link mechanism 70 described later. In the present embodiment, the link storage unit 62 is located on the X2 side with respect to the slide storage unit 61. Further, the inner cylinder part 621 of the link storage part 62 communicates with the inner cylinder part 612 of the slide storage part 61.
　このリンク収納部６２のＹ１側の壁面には、後述する連結軸を軸支する孔形状の軸支部６２２（図１参照）が設けられている。また、リンク収納部６２のＹ２側の壁面には、連結軸のＹ２側の端部を軸支する凹形状の軸支部６２３（図５参照）が設けられている。軸支部６２３は、本実施の形態では、断面が円形の凹部に設けられている。２つの軸支部６２２，６２３は、Ｙ方向において同一の軸線状に位置している。 A hole-shaped shaft support portion 622 (see FIG. 1) for supporting a connecting shaft, which will be described later, is provided on the wall surface on the Y1 side of the link storage portion 62. Further, the wall surface on the Y2 side of the link storage portion 62 is provided with a concave shaft support portion 623 (see FIG. 5) that supports the end portion on the Y2 side of the connecting shaft. In the present embodiment, the shaft support 623 is provided in a recess having a circular cross section. The two shaft support portions 622 and 623 are located on the same axis line in the Y direction.
　次に、リンク機構７０について説明する。スロットルバルブ３０は、特許請求の範囲における 連動手段としてのリンク機構７０を介して、スライドバルブ５０と連動可能に設けられている。具体的には、アクセルペダルを踏まずにスロットルバルブ３０が最も閉じた状態（スロットル閉じ状態とする）のときから、ある程度の開度（第１開度）までは、スライドバルブ５０は動かずに最も閉じた状態（スライド閉じ状態とする）を維持する。しかし、その第１開度を過ぎて、さらにスロットルバルブ３０が開くと、スライドバルブ５０も同期して開き方向に移動する。 Next, the link mechanism 70 will be described. The throttle valve 30 is provided so as to be capable of interlocking with the slide valve 50 via a link mechanism 70 serving as a hook interlocking means in the claims. Specifically, the slide valve 50 does not move from the time when the throttle valve 30 is most closed (the throttle is closed) without stepping on the accelerator pedal until a certain degree of opening (first opening). Maintain the most closed state (the slide closed state). However, when the first opening is passed and the throttle valve 30 is further opened, the slide valve 50 is also moved in the opening direction in synchronization.
　このような動作を可能とするために、本実施の形態のリンク機構７０は、合計５つのリンク７１～７５を有している。以下では、回転軸３１からスライドバルブ５０に向かい、第１リンク７１、第２リンク７２、第３リンク７３、第４リンク７４、第５リンク７５とする。なお、各リンク７１～７５は、特許請求の範囲における連動部に対応する。 In order to enable such an operation, the link mechanism 70 of the present embodiment has a total of five links 71 to 75. In the following description, the first link 71, the second link 72, the third link 73, the fourth link 74, and the fifth link 75 are directed from the rotary shaft 31 toward the slide valve 50. Each link 71 to 75 corresponds to the interlocking unit in the claims.
　リンク機構７０を構成するリンクの本数は、上述のようなスロットルバルブ３０とスライドバルブ５０の連動が実現できるものであれば、何本でも良く、適宜、その他の部材を組み合わせても良い。以下では、本実施の形態のリンク機構７０について具体的に説明する。 The number of links constituting the link mechanism 70 may be any number as long as the above-described interlocking of the throttle valve 30 and the slide valve 50 can be realized, and other members may be appropriately combined. Below, the link mechanism 70 of this Embodiment is demonstrated concretely.
　第１リンク７１は、回転軸３１の固定ピン部３１ａに固定され、第１リンク７１は回転軸３１と共に回転する。第１リンク７１には第２リンク７２がジョイント７６を介して連結されている。ただし、第２リンク７２の一端側には、特許請求の範囲における 遊隙部に対応する長孔部７２ａが設けられていて、第１リンク７１に固定的に設けられたジョイント７６は、移動自在に長孔部７２ａに挿入されている。なお、ジョイント７６は、第１リンク７１に対して回転しても良いが、スライドは不能となっている。 The first link 71 is fixed to the fixed pin portion 31 a of the rotating shaft 31, and the first link 71 rotates together with the rotating shaft 31. A second link 72 is connected to the first link 71 via a joint 76. However, a long hole portion 72a corresponding to the saddle clearance portion in the claims is provided on one end side of the second link 72, and the joint 76 fixedly provided on the first link 71 is movable. Is inserted into the long hole portion 72a. In addition, although the joint 76 may rotate with respect to the 1st link 71, a slide is impossible.
　また、第２リンク７２の他端側には、そのジョイント７７を介して第３リンク７３の一端側が連結され、第３リンク７３の他端側は、連結軸７８のピン部７８ａに回動自在に連結されている。連結軸７８のＹ２側の端部は、軸支部６２３に回転自在に支持されていると共に、その軸支部６２３よりもＹ１側では、連結軸７８は、軸受７９を介して軸支部６２２に回転自在に支持されている。 Further, the other end side of the second link 72 is connected to one end side of the third link 73 via the joint 77, and the other end side of the third link 73 is rotatable to the pin portion 78 a of the connecting shaft 78. It is connected to. The end of the connecting shaft 78 on the Y2 side is rotatably supported by the shaft supporting portion 623, and the connecting shaft 78 is rotatable to the shaft supporting portion 622 via the bearing 79 on the Y1 side of the shaft supporting portion 623. It is supported by.
　また、連結軸７８の他端寄り（Ｙ２寄り）の外周には、第４リンク７４が回動自在に支持されている。すなわち、第３リンク７３には、連結軸７８を介して第４リンク７４が連結されている。第４リンク７４は、リンク収納部６２の底部と干渉するのを防止すべく、湾曲している。しかし、第４リンク７４が湾曲させなくてもリンク収納部６２の底部等と干渉しない場合や干渉が問題とならない場合には、他のリンク７１～７３，７５と同様に直線状であっても良い。第４リンク７４の他端側は、ジョイント８０を介して第５リンク７５の一端側と連結されていて、この第５リンク７５の他端側は、スライドバルブ５０のリンク取付部５６にジョイント８１を介して取り付けられている。 The fourth link 74 is rotatably supported on the outer periphery of the connecting shaft 78 near the other end (close to Y2). That is, the fourth link 74 is connected to the third link 73 via the connecting shaft 78. The fourth link 74 is curved to prevent interference with the bottom of the link storage portion 62. However, even if the fourth link 74 is not curved, if it does not interfere with the bottom of the link storage portion 62, or if interference does not cause a problem, it may be linear as with the other links 71 to 73, 75. good. The other end side of the fourth link 74 is connected to one end side of the fifth link 75 via the joint 80, and the other end side of the fifth link 75 is connected to the link mounting portion 56 of the slide valve 50 with the joint 81. Is attached through.
　ここで、連結軸７８の外周側には、特許請求の範囲における付勢手段に対応する付勢バネ８２が設けられている。付勢バネ８２は、スライドバルブ５０が下方側（Ｚ２側）に向かう付勢力を与えている。この付勢バネ８２は、本実施の形態では、捩じりコイルばねを用いているが、その他のバネを用いても良い。この付勢バネ８２の一端部８２ａは、リンク収納部６２の内壁に当接し、他端部８２ｂは、付勢バネ８２の他の部分とは異なりＹ方向に沿うように曲げられつつ第４リンク７４の上部側に当接している。それにより、付勢バネ８２は、第４リンク７４および第５リンク７５を介して、スライドバルブ５０を下方に押し下げる付勢力を与えている。 Here, on the outer peripheral side of the connecting shaft 78, an urging spring 82 corresponding to the urging means in the claims is provided. The urging spring 82 applies an urging force toward which the slide valve 50 moves downward (Z2 side). In this embodiment, the urging spring 82 is a torsion coil spring, but other springs may be used. One end portion 82a of the biasing spring 82 abuts on the inner wall of the link storage portion 62, and the other end portion 82b differs from the other portions of the biasing spring 82 while being bent along the Y direction. 74 abuts on the upper side. Thus, the biasing spring 82 applies a biasing force that pushes the slide valve 50 downward via the fourth link 74 and the fifth link 75.
　次に、突出部材９０について説明する。図２、図４および図５に示すように、吸気通路２１のスライド収納部６１側の下方側には、突出部材９０が設けられている。突出部材９０は、吸気通路２１において上方側（Ｚ１側）に向かい突出している。この突出部材９０のうち吸気通路２１の上流側（Ｘ２側）の壁面部９１は、流路方向（Ｘ方向）に対して垂直か、または垂直に近い角度に設けられている。一方、壁面部９１の頂部９１ａよりも下流側（Ｘ１側）には、 その頂部９１ａから徐々に下方に向かうように傾斜部９２が設けられている。そして、この傾斜部９２には、負圧取出口９３が設けられている。負圧取出口９３は、突出部材９０を上下方向（Ｚ方向）に貫く管路９４の出口部分となっている。なお、壁面部９１が流路方向（Ｘ方向）に対して垂直な方向から傾斜する場合、上方側（Ｚ１側）に向かうにつれて下流側（Ｘ１側）に向かうように傾斜することが好ましい。そのように傾斜させる場合には、特段、負圧の減少や圧力損失の増大等といった能力低下を抑えることができるためである。 Next, the protruding member 90 will be described. As shown in FIGS. 2, 4, and 5, a projecting member 90 is provided on the lower side of the intake passage 21 on the slide accommodating portion 61 side. The protruding member 90 protrudes upward (Z1 side) in the intake passage 21. The wall surface portion 91 on the upstream side (X2 side) of the intake passage 21 in the projecting member 90 is provided at an angle that is perpendicular to or close to perpendicular to the flow path direction (X direction). On the other hand, on the downstream side (X1 side) of the top portion 91a of the wall surface portion 91, an inclined portion 92 is provided so as to gradually go downward from the top portion 91a. The inclined part 92 is provided with a negative pressure outlet 93. The negative pressure outlet 93 is an outlet portion of a pipe line 94 that penetrates the protruding member 90 in the vertical direction (Z direction). In addition, when the wall surface part 91 inclines from the direction perpendicular | vertical with respect to a flow-path direction (X direction), it is preferable to incline so that it may go to a downstream (X1 side) as it goes to an upper side (Z1 side). This is because such tilting can suppress a decrease in performance such as a decrease in negative pressure and an increase in pressure loss.
　このように、流路断面積の狭いベンチュリ部５５に壁面部９１を有する突出部材９０が設けられ、さらに壁面部９１よりも下流側（Ｘ１側）の傾斜部９２に負圧取出口９３が設けられていることにより、負圧取出口９３での負圧を高めることが可能となっている。なお、負圧取出口９３付近で生じた負圧を利用して、この負圧取出口９３から吸気通路２１にＥＧＲガスを始めとする種々の気体や液体を噴射することができ、またたとえばブレーキ用を始めとした、各種のアクチュエータに用いられる負圧を供給することができる。 As described above, the protruding member 90 having the wall surface portion 91 is provided in the venturi portion 55 having a narrow channel cross-sectional area, and the negative pressure outlet 93 is provided in the inclined portion 92 on the downstream side (X1 side) from the wall surface portion 91. As a result, the negative pressure at the negative pressure outlet 93 can be increased. Various gases and liquids such as EGR gas can be injected from the negative pressure outlet 93 into the intake passage 21 by using the negative pressure generated in the vicinity of the negative pressure outlet 93. The negative pressure used for various actuators can be supplied.
＜作用について＞
　以上のような構成を有するスロットルボディ１０の作用について、以下に説明する。エアクリーナやインタークーラ等を経た吸気が吸気通路２１に導入されて下流側（Ｘ１側）に向かうと、スロットルバルブ３０の存在する部分に差し掛かる。スロットルバルブ３０は、アクセルペダルの操作に連動して回動する。それにより、スロットルバルブ３０が存在する部分での、流路断面積を変化させることができ、下流側（Ｘ１側）に供給される気体の流量を調整することができる。 <About action>
The operation of the throttle body 10 having the above configuration will be described below. When intake air that has passed through an air cleaner, an intercooler, or the like is introduced into the intake passage 21 and travels downstream (X1 side), it reaches a portion where the throttle valve 30 exists. The throttle valve 30 rotates in conjunction with the operation of the accelerator pedal. Thereby, the flow path cross-sectional area in the portion where the throttle valve 30 exists can be changed, and the flow rate of the gas supplied to the downstream side (X1 side) can be adjusted.
　ところで、スロットルバルブ３０の閉じ状態では、その部位で開いている流路断面積は小さく、気体の流速は上昇するが、もしベンチュリ部５５が存在しないとすると、スロットルバルブ３０から同等程度離れた下流側（Ｘ１側）では、負圧は小さくなってしまう。かかる負圧を大きくする、という意味では、特許文献１に開示のような、固定ベンチュリ部を設けることも有効である。 By the way, when the throttle valve 30 is in the closed state, the flow passage cross-sectional area opened at that portion is small and the gas flow rate increases, but if the venturi portion 55 does not exist, the downstream is separated from the throttle valve 30 by about the same amount. On the side (X1 side), the negative pressure becomes small. In the sense of increasing the negative pressure, it is also effective to provide a fixed venturi portion as disclosed in Patent Document 1.
　しかしながら、固定ベンチュリ部を設ける構成では、スロットルバルブ３０が開く向きに回動して気体の流量が増大すると、圧力損失が大きくなる、という問題がある。そこで、圧力損失を低減すべく、固定ベンチュリ部の開口径を大きくすると、今度は、固定ベンチュリ部で十分な負圧を得られない、という問題がある。 However, the configuration in which the fixed venturi portion is provided has a problem that the pressure loss increases when the throttle valve 30 rotates in the opening direction and the gas flow rate increases. Therefore, if the opening diameter of the fixed venturi is increased in order to reduce the pressure loss, there is a problem that a sufficient negative pressure cannot be obtained at the fixed venturi.
　これに対して、本実施の形態では、特許文献１の固定ベンチュリ部を設けている部位に、固定ベンチュリ部に代えて、スライドバルブ５０を設けている。しかも、スライドバルブ５０のスライドは、スロットルバルブ３０の開度を調節する動きに連動するようにしている。 In contrast, in the present embodiment, a slide valve 50 is provided in place of the fixed venturi portion in the portion where the fixed venturi portion of Patent Document 1 is provided. In addition, the slide of the slide valve 50 is interlocked with the movement for adjusting the opening degree of the throttle valve 30.
　具体的には、スロットルバルブ３０が最も閉じている状態から、徐々にスロットルバルブ３０の開度を大きくしていくと、その動きに連動して回転軸３１も回転し、第１リンク７１も回動する。しかし、第１リンク７１の他端側に位置するジョイント７６は、第２リンク７２の一端側の長孔部７２ａに入り込んでいるので、その長孔部７２ａのＸ１側の端部７２ａ１まで移動しないと、第２リンク７２も回動しない。そして、この端部７２ａ１にジョイント７６が衝突する部位までは、スロットルバルブ３０で発生する圧力損失の影響が大きく、もしスライドバルブ５０が存在しない、としても、圧力損失がさほど変わらない状態となっている。 Specifically, when the opening of the throttle valve 30 is gradually increased from the state where the throttle valve 30 is most closed, the rotary shaft 31 rotates in conjunction with the movement, and the first link 71 also rotates. Move. However, since the joint 76 located on the other end side of the first link 71 enters the long hole portion 72a on the one end side of the second link 72, it does not move to the end portion 72a1 on the X1 side of the long hole portion 72a. Then, the second link 72 does not rotate. Then, up to the portion where the joint 76 collides with the end portion 72a1, the influence of the pressure loss generated in the throttle valve 30 is large, and even if the slide valve 50 does not exist, the pressure loss does not change so much. Yes.
　しかし、端部７２ａ１にジョイント７６が衝突した後に、さらにスロットルバルブ３０の開度が大きくなる場合、仮にスライドバルブ５０が開かないと、今度は、スロットルバルブ３０での圧力損失よりも、スライドバルブ５０での圧力損失の影響が大きくなる。すなわち、スロットルバルブ３０が開いて流量が増大したにも拘らず、スライドバルブ５０が閉じたままだと、スライドバルブ５０での圧力損失が大きくなってしまう。 However, if the opening degree of the throttle valve 30 further increases after the joint 76 collides with the end portion 72 a 1, if the slide valve 50 is not opened, this time, the slide valve 50 is more than the pressure loss at the throttle valve 30. The effect of the pressure loss at is increased. That is, when the throttle valve 30 is opened and the flow rate is increased, the pressure loss at the slide valve 50 increases if the slide valve 50 remains closed.
　そこで、本実施の形態では、端部７２ａ１にジョイント７６が衝突した後には、スロットルバルブ３０の開き方向への動きに連動して、スライドバルブ５０が上方側（Ｚ１側）に移動するように構成されている。このとき、スライドバルブ５０のスライド量は、スロットルバルブ３０の開き方向への回動に対して、圧力損失を増加させないようにスライドする一方で、負圧を大きく確保できる程度に設定されている。 Therefore, in the present embodiment, after the joint 76 collides with the end portion 72a1, the slide valve 50 moves upward (Z1 side) in conjunction with the movement of the throttle valve 30 in the opening direction. Has been. At this time, the sliding amount of the slide valve 50 is set to such a degree that a large negative pressure can be secured while sliding so as not to increase the pressure loss with respect to the rotation of the throttle valve 30 in the opening direction.
　そして、スロットルバルブ３０の全開状態では、スライドバルブ５０も最も上方側（Ｚ１側）に位置する状態となっている。 When the throttle valve 30 is fully opened, the slide valve 50 is also positioned on the uppermost side (Z1 side).
　図７は、スロットルバルブ３０の開度を変化させたときの、気体の流量増大に対する圧力損失と、スロットルバルブ３０から流路方向にスライドバルブ５０に対応する距離だけ離れた位置（負圧測定位置）での負圧の関係をグラフで示した図である。なお、図７では、縦軸は圧力値を示しており、そのうち圧力が０（Ｐａ）よりも高い領域では、圧力損失の圧力値が示されており、圧力が０（Ｐａ）よりも低い領域では、負圧の圧力値が示されている。また、図７においては、横軸は気体の流量が示されている。 FIG. 7 shows a pressure loss with respect to an increase in the gas flow rate when the opening of the throttle valve 30 is changed, and a position away from the throttle valve 30 by a distance corresponding to the slide valve 50 in the flow path direction (negative pressure measurement position). It is the figure which showed the relationship of the negative pressure in () in the graph. In FIG. 7, the vertical axis represents the pressure value, and in the region where the pressure is higher than 0 (Pa), the pressure value of the pressure loss is shown, and the region where the pressure is lower than 0 (Pa). The negative pressure value is shown. In FIG. 7, the horizontal axis represents the gas flow rate.
　また、図７においては、破線は、バタフライ方式のスロットルバルブ３０のみを設けた状態に対応しており、実線は、スロットルバルブ３０に加えて、スロットルバルブ３０に連動するスライドバルブ５０が設けられた状態に対応している。なお、図７では、スロットルバルブ３０の開度が１５度（左側）および３０度（右側）の場合を示している。 In FIG. 7, the broken line corresponds to the state where only the butterfly throttle valve 30 is provided, and the solid line is provided with the slide valve 50 linked to the throttle valve 30 in addition to the throttle valve 30. It corresponds to the state. FIG. 7 shows a case where the opening degree of the throttle valve 30 is 15 degrees (left side) and 30 degrees (right side).
　この図７から明らかなように、圧力損失に関しては、スロットルバルブ３０のみを設けた場合と、スロットルバルブ３０に加えてスライドバルブ５０を設けた場合とでは、ほとんど差がない状態となっている。すなわち、圧力損失は、スライドバルブ５０の存在によっては、ほとんど増加しない状態となっている。 As is apparent from FIG. 7, there is almost no difference in pressure loss between the case where only the throttle valve 30 is provided and the case where the slide valve 50 is provided in addition to the throttle valve 30. That is, the pressure loss hardly increases depending on the presence of the slide valve 50.
　一方、負圧に関しては、スロットルバルブ３０のみを設けた場合よりも、スロットルバルブ３０に加えてスライドバルブ５０を設けた場合の方が、明らかに増大している。具体的には、スロットルバルブ３０の開度が１５度の場合には、負圧は２２％増加しており、スロットルバルブ３０の開度が３０度の場合には、負圧は２４％増加している。 On the other hand, regarding the negative pressure, the case where the slide valve 50 is provided in addition to the throttle valve 30 clearly increases compared to the case where only the throttle valve 30 is provided. Specifically, when the opening degree of the throttle valve 30 is 15 degrees, the negative pressure increases by 22%, and when the opening degree of the throttle valve 30 is 30 degrees, the negative pressure increases by 24%. ing.
　このように、本実施の形態では、スロットルバルブ３０の開き動作に連動するスライドバルブ５０を設けているので、圧力損失の増大を抑えながら、負圧を増加させている。 As described above, in the present embodiment, the slide valve 50 interlocking with the opening operation of the throttle valve 30 is provided, so that the negative pressure is increased while suppressing an increase in pressure loss.
　さらに、本実施の形態では、スライドバルブ５０に加えて、突出部材９０も設けている。そのため、流路が絞られたベンチュリ部５５のうち、壁面部９１よりも下流側の負圧取出口９３では、負圧をより高めることが可能となっている。特に、スロットルバルブ３０が大きく開くのに伴って、スライドバルブ５０が上方側（Ｚ１側）に移動し、それによってベンチュリ部５５での負圧が小さくなってしまう場合でも、突出部材９０が存在することで、負圧取出口９３での負圧を高めることができる。 Furthermore, in this embodiment, in addition to the slide valve 50, a protruding member 90 is also provided. Therefore, the negative pressure can be further increased at the negative pressure outlet 93 on the downstream side of the wall surface portion 91 in the venturi portion 55 in which the flow path is narrowed. In particular, the projecting member 90 exists even when the slide valve 50 moves upward (Z1 side) as the throttle valve 30 is greatly opened, thereby reducing the negative pressure at the venturi 55. Thus, the negative pressure at the negative pressure outlet 93 can be increased.
　図８は、突出部材９０の存在によって負圧取出口９３での負圧が増加した様子をグラフで示した図である。この図８では、破線は突出部材９０が存在しない場合を示しており、実線は突出部材９０が存在する場合を示している。また、図８は、スロットルバルブ３０が開度１５度、開度３０度、およびスロットルバルブ３０が全開のときにそれぞれ同一の空気量における負圧をプロットしたものである。 FIG. 8 is a graph showing how the negative pressure at the negative pressure outlet 93 is increased due to the presence of the protruding member 90. In FIG. 8, the broken line indicates a case where the protruding member 90 is not present, and the solid line indicates a case where the protruding member 90 is present. FIG. 8 is a plot of negative pressure at the same air amount when the throttle valve 30 has an opening of 15 degrees, the opening of 30 degrees, and the throttle valve 30 is fully open.
　この図８から明らかなように、突出部材９０が存在しない場合よりも、突出部材９０が存在した方が、負圧取出口９３での圧力が増大している。 As is apparent from FIG. 8, the pressure at the negative pressure outlet 93 is increased when the protruding member 90 is present, compared with the case where the protruding member 90 is not present.
　本実施の形態では、以上のようにして、スロットルバルブ３０の開度調整にスライドバルブ５０のスライドを連動させて、圧力損失の増大を抑えながら、ベンチュリ部５５での負圧を増大させている。 In the present embodiment, as described above, the slide of the slide valve 50 is interlocked with the adjustment of the opening degree of the throttle valve 30, and the negative pressure in the venturi portion 55 is increased while suppressing an increase in pressure loss. .
＜効果について＞
　以上のような構成の負圧発生装置であるスロットルボディ１０によると、スロットルバルブ３０以外にスライドバルブ５０が設けられ、そのスライドバルブ５０は、上下方向へのスライドという位置変化によって吸気通路２１の流路断面積を変化させている。そのため、スロットルバルブ３０のみが存在して、スライドバルブ５０が存在しない場合と比較して、スロットルバルブ３０から下流側（Ｘ１側）にベンチュリ部５５に対応する距離だけ離れた部位での負圧を高めることが可能となる。 <About effects>
According to the throttle body 10 which is the negative pressure generating device having the above-described configuration, the slide valve 50 is provided in addition to the throttle valve 30. The slide valve 50 flows in the intake passage 21 by a position change of sliding in the vertical direction. The road cross-sectional area is changed. Therefore, as compared with the case where only the throttle valve 30 is present and the slide valve 50 is not present, the negative pressure at a site away from the throttle valve 30 by a distance corresponding to the venturi portion 55 is located downstream (X1 side). It becomes possible to raise.
　また、本実施の形態では、スロットルバルブ３０の回動とスライドバルブ５０とが同期して連動するように、リンク機構７０が設けられている。かかるリンク機構７０の存在により、スロットルバルブ３０の回動に連動させて、スライドバルブ５０を確実にスライドさせることができる。また、リンク機構７０を用いる場合には、ワイヤ等の他の手段を用いる場合と比較して、調整等の手間が不要であるので、組み付けし易い、というメリットも生じさせることができる。 Further, in the present embodiment, the link mechanism 70 is provided so that the rotation of the throttle valve 30 and the slide valve 50 are synchronized with each other. Due to the presence of the link mechanism 70, the slide valve 50 can be reliably slid in conjunction with the rotation of the throttle valve 30. Further, when the link mechanism 70 is used, there is an advantage that it is easy to assemble, since there is no need for adjustment and the like as compared with the case where other means such as a wire is used.
　さらに、本実施の形態では、第２リンク７２には、長孔部７２ａが設けられていて、その長孔部７２ａに、第１リンク７１に取り付けられたジョイント７６が差し込まれる。それにより、スロットルバルブ３０が最も閉じた状態から、スロットルバルブ３０の第１開度までは、第１リンク７１の回動に伴ってジョイント７６が長孔部７２ａ内を移動しても、第２リンク７２側が移動しない。そのため、スロットルバルブ３０が開く向きに動いても、スライドバルブ５０が直ちには上方側（Ｚ１側）にスライドせずに、両者の動き始めに位相差を持たせることができる。 Furthermore, in the present embodiment, the second link 72 is provided with a long hole portion 72a, and a joint 76 attached to the first link 71 is inserted into the long hole portion 72a. Thereby, even if the joint 76 moves in the long hole portion 72a with the rotation of the first link 71 from the state where the throttle valve 30 is most closed to the first opening of the throttle valve 30, the second The link 72 side does not move. Therefore, even if the throttle valve 30 moves in the opening direction, the slide valve 50 does not immediately slide upward (Z1 side), and a phase difference can be given to the beginning of the movement of both.
　すなわち、スロットルバルブ３０が最も閉じている状態から徐々に開く向きに回動しても、第１開度までは、圧力損失の増加を抑えるように設定することができる。その場合、第１開度よりもスロットルバルブ３０が大きく開くときには、圧力損失が増加しないように、スライドバルブ５０をスロットルバルブ３０の開きに連動させて、上方側（Ｚ１側）にスライドさせている。それにより、圧力損失の増大の抑制と、ベンチュリ部５５での負圧の増大とのバランスを良好にとることができる。 That is, even if the throttle valve 30 is rotated from the most closed state in a direction to gradually open, it can be set to suppress an increase in pressure loss up to the first opening. In that case, when the throttle valve 30 opens larger than the first opening, the slide valve 50 is slid upward (Z1 side) in conjunction with the opening of the throttle valve 30 so that the pressure loss does not increase. . Thereby, it is possible to satisfactorily balance the suppression of the increase in pressure loss and the increase in the negative pressure at the venturi portion 55.
　また、本実施の形態では、特許文献１のような固定ベンチュリ部を設ける構成と比較すると、特に気体の流量が増大する領域での圧力損失を減らすことが可能となる。さらに、スライドバルブ５０が存在しない構成と比較すると、スロットルバルブ３０の種々の開度において、負圧を向上させることが可能となる。 Further, in the present embodiment, compared to a configuration in which a fixed venturi portion is provided as in Patent Document 1, it is possible to reduce pressure loss particularly in a region where the gas flow rate increases. Furthermore, compared with a configuration in which the slide valve 50 does not exist, the negative pressure can be improved at various opening degrees of the throttle valve 30.
　また、本実施の形態では、ベンチュリ部５５には、突出部材９０が突出して設けられている。しかも、突出部材９０には、その突出部材９０を迂回する気体の流れを生じさせる壁面部９１と、壁面部９１よりも下流側に設けられ、かつ頂部９１ａよりも突出部材９０の付け根側（Ｚ２側）に位置する負圧取出口９３とを備えている。このような構成により、頂部９１ａよりも下流側（Ｚ２側）の負圧取出口９３での負圧を一層増大させることができる。また、スライドバルブ５０が全開の場合、もし突出部材９０がないときには、負圧取出口付近での負圧は小さくなる。しかしながら、突出部材９０を設けることにより、スライドバルブ５０の全開状態でも、負圧取出口９３付近の負圧を増大させることができる。 In the present embodiment, the venturi portion 55 is provided with a protruding member 90 protruding. In addition, the projecting member 90 is provided with a wall surface 91 for generating a gas flow that bypasses the projecting member 90, a downstream side of the wall surface 91, and a base side of the projecting member 90 with respect to the top 91 a (Z 2). And a negative pressure outlet 93 located on the side). With such a configuration, the negative pressure at the negative pressure outlet 93 on the downstream side (Z2 side) of the top portion 91a can be further increased. Also, when the slide valve 50 is fully open, if there is no protruding member 90, the negative pressure near the negative pressure outlet is reduced. However, by providing the projecting member 90, the negative pressure near the negative pressure outlet 93 can be increased even when the slide valve 50 is fully opened.
　さらに、本実施の形態では、第１バルブとしてスロットルバルブ３０が用いられており、さらに第２バルブとしてスライドバルブ５０が用いられている。このため、アクセルペダルの操作に連動するスロットルバルブ３０に、ベンチュリ部５５を形成するスライドバルブ５０のスライドを効率的に連動させることができる。 Furthermore, in this embodiment, the throttle valve 30 is used as the first valve, and the slide valve 50 is used as the second valve. For this reason, the slide of the slide valve 50 which forms the venturi part 55 can be efficiently interlocked with the throttle valve 30 interlocked with the operation of the accelerator pedal.
　また、本実施の形態では、連動手段として、リンク機構７０が用いられていると共に、そのうち第２リンク７２には長孔部７２ａが設けられ、その長孔部７２ａには第１リンク７１に取り付けられたジョイント７６が挿入されている。このため、スロットルバルブ３０が最も閉じた状態から第１開度までは、スライドバルブ５０が最も閉じた状態を維持することが可能となる。それにより、ベンチュリ部５５で圧力損失が増大しないにも関わらず流路断面積が増加し、それによって負圧が小さくなってしまうのを防ぐことができる。それにより、たとえば自動車等においては、さほど速度を出さない領域（街乗り程度の速度領域）では、スロットルバルブ３０のみが開くように動くがスライドバルブ５０が上方側（Ｚ１側）にスライドせずに、ベンチュリ部５５での流速を速くすることができ、そのベンチュリ部５５での負圧を増加させることができる。 In the present embodiment, the link mechanism 70 is used as the interlocking means, and the second link 72 is provided with a long hole portion 72a, and the long hole portion 72a is attached to the first link 71. The joint 76 is inserted. For this reason, it is possible to maintain the slide valve 50 in the most closed state from the state in which the throttle valve 30 is most closed to the first opening. Thereby, although the pressure loss does not increase in the venturi portion 55, it is possible to prevent the flow path cross-sectional area from increasing, thereby reducing the negative pressure. As a result, for example, in an automobile or the like, in a region where the speed is not so high (a speed region around the city), only the throttle valve 30 moves so that the slide valve 50 does not slide upward (Z1 side). The flow velocity at the venturi section 55 can be increased, and the negative pressure at the venturi section 55 can be increased.
　また、本実施の形態では、スライドバルブ５０は、付勢バネ８２によって、常に下方にスライドする向きの付勢力が与えられている。このため、ジョイント７６が長孔部７２ａの中間的な部位に位置していても、スライドバルブ５０が最も閉じた状態を維持することができる。 Further, in the present embodiment, the slide valve 50 is given a biasing force that always slides downward by the biasing spring 82. For this reason, even if the joint 76 is located in the intermediate part of the long hole part 72a, the state which the slide valve 50 closed most is maintainable.
＜変形例＞
　以上、本発明の各実施の形態について説明したが、本発明はこれ以外にも種々変形可能となっている。以下、それについて述べる。 <Modification>
As mentioned above, although each embodiment of this invention was described, this invention can be variously deformed besides this. This will be described below.
　上述の実施の形態においては、第１バルブとして回動するスロットルバルブ３０が示されている。しかしながら、第１バルブは、かかる回動するものには限られず、他のバルブとしても良い。他のバルブとしては、たとえば、スライドするバルブを用いるようにしても良い。また、上述の実施の形態では、第２バルブとしてスライドバルブ５０が示されている。しかしながら、このスライドバルブ５０も、スライドのみの動作ではなく、回動する動作を加えたものであっても良い。 In the above-described embodiment, the throttle valve 30 that rotates as the first valve is shown. However, the first valve is not limited to the rotating valve, and may be another valve. As another valve, for example, a sliding valve may be used. In the above-described embodiment, the slide valve 50 is shown as the second valve. However, this slide valve 50 may also be one that is added with a rotating operation instead of only a sliding operation.
　また、上述の実施の形態では、スロットルバルブ３０とスライドバルブ５０とを連動させる連動手段として、リンク機構７０について説明している。しかしながら、連動手段は、リンク機構７０には限られず、他の機構や構成を用いても良い。たとえば、ワイヤと滑車等を用いて、スロットルバルブ３０の動きにスライドバルブ５０のスライドが連動するように構成しても良い。また、ギヤ機構やカム機構、およびそれらの組み合わせによって、スロットルバルブ３０の動きにスライドバルブ５０のスライドが連動するように構成しても良い。 In the above-described embodiment, the link mechanism 70 is described as an interlocking unit that interlocks the throttle valve 30 and the slide valve 50. However, the interlocking means is not limited to the link mechanism 70, and other mechanisms and configurations may be used. For example, a slide of the slide valve 50 may be interlocked with the movement of the throttle valve 30 using a wire and a pulley. Further, the slide of the slide valve 50 may be interlocked with the movement of the throttle valve 30 by a gear mechanism, a cam mechanism, or a combination thereof.
　また、上述の実施の形態では、遊隙部としての長孔部７２ａについて説明している。しかしながら、遊隙部は、かかる長孔部７２ａには限られない。たとえば、孔形状以外に、貫通しない穴形状（凹部形状）としても良い。また、ジョイント７６が衝突する突起形状を設け、この突起形状に衝突するまでの部位を遊隙部としても良い。 Further, in the above-described embodiment, the long hole portion 72a as the play portion is described. However, the play portion is not limited to the long hole portion 72a. For example, in addition to the hole shape, a hole shape that does not penetrate (recessed shape) may be used. Moreover, it is good also considering the protrusion shape which the joint 76 collides as a clearance gap part as a site | part until it collides with this protrusion shape.
　また、上述の実施の形態では、遊隙部である長孔部７２ａが第２リンク７２に設けられた構成について説明している。しかしながら、長孔部等の遊隙部は、第２リンク７２以外の部位に設けるようにしても良い。たとえば第２リンク７２と他のリンク７３の間、第４リンク７４と第５リンク７５の間を始めとする、他の部位に設ける構成としても良い。 Further, in the above-described embodiment, a configuration in which the long hole portion 72a that is a play portion is provided in the second link 72 is described. However, a gap portion such as a long hole portion may be provided in a portion other than the second link 72. For example, it is good also as a structure provided in other parts, such as between the 2nd link 72 and the other link 73, and between the 4th link 74 and the 5th link 75.
　１０…スロットルボディ（負圧発生装置に対応）、２０…ボディ部、２１…吸気通路、３０…スロットルバルブ（第１バルブに対応）、３１…回転軸、３１ａ…固定ピン部、４０…可動ベンチュリ部、５０…スライドバルブ（第２バルブに対応）、５１…底壁部、５２…壁面部、５３…半円部、５４…隙間通路、５５…ベンチュリ部、５６…リンク取付部、６０…収納筐体、６１…スライド収納部、６２…リンク収納部、６３…蓋部材、７０…リンク機構（連動手段に対応）、７１～７５…リンク（第１～第５リンク；連動部に対応）、７２ａ…長孔部（遊隙部に対応）、７２ａ１…端部、７６，７７，８０，８１…ジョイント、７８…連結軸、７８ａ…ピン部、７９…軸受、８２…付勢バネ（付勢手段に対応）、８２ａ…一端部、８２ｂ…他端部、９０…突出部材、９１…壁面部、９１ａ…頂部、９２…傾斜部、９３…負圧取出口、９４…管路、６１１…連通孔、６１２，６２１…内筒部、６１３…摺動溝部、６１４…係止底壁、６２２，６２３…軸支部
  DESCRIPTION OF SYMBOLS 10 ... Throttle body (corresponding to negative pressure generating device), 20 ... Body portion, 21 ... Intake passage, 30 ... Throttle valve (corresponding to first valve), 31 ... Rotating shaft, 31a ... Fixed pin portion, 40 ... Movable venturi 50, slide valve (corresponding to the second valve), 51 ... bottom wall portion, 52 ... wall surface portion, 53 ... semicircular portion, 54 ... gap passage, 55 ... venturi portion, 56 ... link mounting portion, 60 ... storage Housing 61: Slide storage part 62 ... Link storage part 63 ... Lid member 70 ... Link mechanism (corresponding to interlocking means) 71-75 ... Link (first to fifth links; corresponding to interlocking part), 72a ... long hole portion (corresponding to the gap portion), 72a1 ... end, 76, 77, 80, 81 ... joint, 78 ... connecting shaft, 78a ... pin portion, 79 ... bearing, 82 ... biasing spring (biasing) 82a ... one end, 82b ... End part, 90 ... projecting member, 91 ... wall surface part, 91a ... top part, 92 ... inclined part, 93 ... negative pressure outlet, 94 ... pipe, 611 ... communication hole, 612, 621 ... inner cylinder part, 613 ... sliding Moving groove part, 614... Locking bottom wall, 622, 623.

Claims (4)

  1. 　吸気通路内で負圧を生じさせることが可能な負圧発生装置であって、
    　前記吸気通路内に設けられると共に、位置変化によって流路断面積を変化させることが可能な第１バルブと、
    　前記吸気通路内のうち前記第１バルブよりも下流側に設けられると共に、位置変化によって流路断面積を変化させることが可能な第２バルブと、
    　連動部を有し、前記第１バルブの位置変化に伴って前記連動部が移動することで前記第２バルブに位置変化を生じさせる連動手段と、
    　を具備し、
    　前記連動手段には、前記吸気通路の流路断面積を前記第１バルブが最も狭めている状態から広がる場合、第１開度までは前記第２バルブの位置変化を生じさせない遊隙部が設けられている、
    　ことを特徴とする負圧発生装置。     A negative pressure generating device capable of generating a negative pressure in an intake passage,
    A first valve provided in the intake passage and capable of changing a flow path cross-sectional area by a position change;
    A second valve that is provided on the downstream side of the first valve in the intake passage, and capable of changing a flow path cross-sectional area by a position change;
    Interlocking means having an interlocking part, and causing the second valve to change its position by moving the interlocking part with a change in position of the first valve;
    Comprising
    When the flow passage cross-sectional area of the intake passage widens from the state in which the first valve is narrowest, the interlocking means is provided with a gap portion that does not cause a change in the position of the second valve until the first opening degree. Being
    A negative pressure generator characterized by that.
  2. 　請求項１記載の負圧発生装置であって、
    　前記第２バルブが位置するベンチュリ部には、当該ベンチュリ部の流路断面積を狭める向きに突出する突出部材が設けられていて、
    　前記突出部材は、当該突出部材を迂回する気体の流れを生じさせる壁面部と、当該壁面部よりも下流側に設けられると共に前記壁面部の頂部よりも前記突出部材の付け根側に位置する負圧取出口と、を備える、
    　ことを特徴とする負圧発生装置。     The negative pressure generator according to claim 1,
    The venturi part where the second valve is located is provided with a projecting member that projects in a direction to narrow the cross-sectional area of the venturi part,
    The projecting member is provided with a wall surface that generates a gas flow that bypasses the projecting member, and a negative pressure that is provided on the downstream side of the wall surface portion and located closer to the base of the projecting member than the top of the wall surface portion. An outlet,
    A negative pressure generator characterized by that.
  3. 　請求項１または２記載の負圧発生装置であって、
    　前記第１バルブは、回転軸を中心に回転することで流路断面積を変化させるスロットルバルブであり、
    　前記第２バルブは、前記吸気通路に対して出没することで流路断面積を変化させるスライドバルブである、
    　ことを特徴とする負圧発生装置。     The negative pressure generator according to claim 1 or 2,
    The first valve is a throttle valve that changes a cross-sectional area of the flow path by rotating around a rotation axis;
    The second valve is a slide valve that changes a flow passage cross-sectional area by moving in and out of the intake passage.
    A negative pressure generator characterized by that.
  4. 　請求項１から３のいずれか１項に記載の負圧発生装置であって、
    　前記連動手段は、複数のリンクから構成されるリンク機構であり、
    　複数の前記リンクのうち、２つの前記リンクが互いにジョイントを介して接続されている部位については、一方の前記リンクにジョイントが取り付けられ、他方の前記リンクには前記ジョイントがスライド自在に挿入されると共に前記遊隙部に対応する長孔部が設けられ、
    　前記第２バルブは、付勢手段によって前記吸気通路の流路断面積を狭める向きに付勢されている、
    　ことを特徴とする負圧発生装置。
          The negative pressure generator according to any one of claims 1 to 3,
    The interlocking means is a link mechanism composed of a plurality of links,
    Of the plurality of links, for a portion where the two links are connected to each other via a joint, the joint is attached to one of the links, and the joint is slidably inserted into the other link. And a slot corresponding to the play portion is provided,
    The second valve is urged by an urging means in a direction to narrow the flow passage cross-sectional area of the intake passage.
    A negative pressure generator characterized by that.
PCT/JP2014/082866 2013-12-20 2014-12-11 Negative-pressure-generating device WO2015093395A1 (en)

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JPS53125527A (en) * 1977-02-23 1978-11-01 Smith Mervyn Noel Carburetor unit for internal combustion engine
JPS5725136U (en) * 1980-07-18 1982-02-09
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JPH0628233U (en) * 1992-09-09 1994-04-15 株式会社ミクニ Engine intake air amount control device
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WO2020009952A1 (en) * 2018-07-05 2020-01-09 Fisher Controls International Llc Rotary axial globe valve
CN110686122A (en) * 2018-07-05 2020-01-14 费希尔控制产品国际有限公司 Rotary axial stop valve
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CN110686122B (en) * 2018-07-05 2023-11-28 费希尔控制产品国际有限公司 Rotary axial stop valve

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