WO2015076001A1 - 負圧ポンプ及びシリンダヘッドカバー - Google Patents

負圧ポンプ及びシリンダヘッドカバー Download PDF

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Publication number
WO2015076001A1
WO2015076001A1 PCT/JP2014/074135 JP2014074135W WO2015076001A1 WO 2015076001 A1 WO2015076001 A1 WO 2015076001A1 JP 2014074135 W JP2014074135 W JP 2014074135W WO 2015076001 A1 WO2015076001 A1 WO 2015076001A1
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WO
WIPO (PCT)
Prior art keywords
housing
vane
negative pressure
circular hole
shaft
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.)
Ceased
Application number
PCT/JP2014/074135
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English (en)
French (fr)
Japanese (ja)
Inventor
伸司 山▲崎▼
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanoh Industrial Co Ltd
Original Assignee
Sanoh Industrial Co Ltd
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 Sanoh Industrial Co Ltd filed Critical Sanoh Industrial Co Ltd
Priority to US14/888,959 priority Critical patent/US9562531B2/en
Priority to EP14864534.4A priority patent/EP2982865B1/en
Priority to CN201480025296.0A priority patent/CN105209762B/zh
Publication of WO2015076001A1 publication Critical patent/WO2015076001A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3442—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the inlet and outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3448—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the present invention relates to a negative pressure pump and a cylinder head cover.
  • JP-A-2004-285978 discloses a vane-type negative pressure pump that generates negative pressure by power from an engine.
  • a rotor supporting a vane passes through a bottom portion of a housing having a bottomed cylindrical shape, and an outer peripheral surface of the rotor is in contact with a part of an inner wall surface of the housing.
  • a suction port and a discharge port are formed at the bottom of the housing on the downstream side of the suction port in the vane rotation direction.
  • An object of the present invention is to provide a negative pressure pump and a cylinder head cover that suppress a decrease in pump efficiency while suppressing an excessive pressure from acting on a vane.
  • the negative pressure pump according to the first aspect of the present invention has a bottomed cylindrical shape, the opening is closed by a lid, a lubricant is supplied to the inside, and a circular hole is formed at a position eccentric from the center of the casing of the bottom.
  • a formed housing, a shaft portion fitted into the circular hole, and a diameter larger than that of the shaft portion, and is disposed in the housing and an outer peripheral surface is a part of an inner wall surface of the housing.
  • a rotating shaft that rotates when power is transmitted from a power source, and is disposed in the housing, and is capable of reciprocating in a direction orthogonal to the rotating shaft.
  • a vane that is supported and rotates integrally with the rotating shaft and whose end slides on the inner wall surface and divides the inside of the housing into a plurality of spaces, and is formed in the housing, and sucks gas into the housing
  • a suction portion that is formed on the downstream side in the rotation direction of the vane with respect to the suction portion of the housing,
  • a discharge portion that discharges the gas sucked from the inlet and the lubricant to the outside of the housing; and a bottom surface of the housing, the discharge portion in the rotation direction of the vane, and the inner wall surface that is in contact with the support portion.
  • a recess that communicates with the circular hole and guides the lubricant moved by the vane to the circular hole.
  • the vane when power is transmitted from the power source and the rotating shaft rotates, the vane also rotates integrally with the rotating shaft.
  • the vane receives a centrifugal force and moves in a direction perpendicular to the rotation axis (diameter direction of the rotation axis), and the vane end slides on the inner wall surface of the casing.
  • the shaft portion of the rotation shaft is fitted into the circular hole that is eccentric from the center of the casing, the rotation center of the rotation shaft is at a position that is eccentric with respect to the center of the casing. For this reason, when the rotating shaft and the vane rotate integrally, the volume of the space partitioned by the vane increases or decreases.
  • the vane passes through the discharge portion. After that, the lubricant remaining without being discharged enters the recess. Since the recess communicates with the circular hole, the lubricant that has entered is guided to the circular hole.
  • closed space since the space between the vane that has passed through the discharge part and the rotating shaft (support part) (hereinafter referred to as “closed space”) is increased in pressure due to the decrease in volume, it is guided to the circular hole.
  • the lubricated lubricant is pushed into the gap between the circular hole and the shaft portion by the pressure in the closed space. At this time, the gas remaining without being discharged is also mixed with the lubricant and pushed into the gap. Thereby, since the pressure rise of a closed space is suppressed, it is suppressed that an excessive pressure acts on a vane.
  • the frictional resistance between the circular hole and the shaft portion is reduced by the lubricant pushed into the gap between the circular hole and the shaft portion.
  • abrasion of a circular hole and a shaft part is controlled.
  • the rotation of the rotating shaft is smoothed by the lubricant, the energy loss of the power source is also suppressed.
  • the lubricant and gas are successively pushed into the gap through the recess and pushed out of the housing. For this reason, since the influence which the lubricant remaining without being discharged completely has on the suction amount (suction amount) of the gas sucked from the suction portion is reduced, it is possible to suppress a decrease in pump efficiency. From the above, according to the negative pressure pump of the first aspect, it is possible to suppress a decrease in pump efficiency while suppressing an excessive pressure from acting on the vane.
  • the negative pressure pump according to the second aspect of the present invention has a bottomed cylindrical shape, the opening is closed by a lid, a lubricant is supplied to the inside, and a circular hole is formed at a position eccentric from the center of the bottom case.
  • a housing formed, a shaft portion fitted into the circular hole, and a support portion having a larger diameter than the shaft portion and disposed in the housing, and power is transmitted from a power source.
  • a rotating shaft that is rotated in this manner, and is disposed within the housing, and is supported by the support portion of the rotating shaft so as to be able to reciprocate in a direction orthogonal to the rotating shaft.
  • Three or more vanes that slide on the inner wall surface of the housing and divide the housing into a plurality of spaces, a suction portion that is formed in the housing and sucks gas into the housing, and the housing Formed on the downstream side in the rotation direction of the vane with respect to the suction portion, and the gas sucked from the suction portion and the front
  • a discharge part that discharges the lubricant to the outside of the housing; and a bottom surface of the housing that is formed between the discharge part and the suction part in the rotation direction of the vane, and communicates with the circular hole; And a recess for guiding the lubricant moved by the vane to the circular hole.
  • the vane when power is transmitted from the power source and the rotating shaft rotates, the vane also rotates integrally with the rotating shaft.
  • the vane receives a centrifugal force and moves in a direction perpendicular to the rotation axis (diameter direction of the rotation axis), and the vane end slides on the inner wall surface of the casing.
  • the shaft portion of the rotation shaft is fitted into the circular hole that is eccentric from the center of the casing, the rotation center of the rotation shaft is at a position that is eccentric with respect to the center of the casing. For this reason, when the rotating shaft and the vane rotate integrally, the volume of the space partitioned by the vane increases or decreases.
  • the vane In the negative pressure pump, since the concave portion is formed between the discharge portion and the suction portion in the rotation direction of the vane on the bottom surface of the casing, the vane remains without being discharged after passing through the discharge portion.
  • the lubricant enters the recess. Since the recess communicates with the circular hole, the lubricant that has entered is guided to the circular hole.
  • the space between the vane that has passed through the discharge part and the vane that has passed through the discharge part and has not reached the suction part before this vane hereinafter referred to as “closed space”) has a volume. Since the pressure increases due to the decrease, the lubricant guided in the circular hole is pushed into the gap between the circular hole and the shaft portion by the pressure in the closed space. At this time, the gas remaining without being discharged is also mixed with the lubricant and pushed into the gap. Thereby, since the pressure rise of a closed space is suppressed, it is suppressed that an excessive pressure acts on a vane
  • the frictional resistance between the circular hole and the shaft portion is reduced by the lubricant pushed into the gap between the circular hole and the shaft portion.
  • abrasion of a circular hole and a shaft part is controlled.
  • the rotation of the rotating shaft is smoothed by the lubricant, the energy loss of the power source is also suppressed.
  • the negative pressure pump according to a third aspect of the present invention is the negative pressure pump according to the first aspect or the second aspect, wherein the hole side groove is formed on the hole wall surface of the circular hole and communicates the recess with the outside of the housing. ,have.
  • the hole-side groove portion that communicates the recess and the outside of the housing is formed on the hole wall surface of the circular hole, the lubricant guided to the circular hole through the recess is not contained in the closed space. It is pushed into the hole side groove part which comprises the clearance gap between a circular hole and a axial part with pressure. In this way, by forming the hole side groove on the hole wall surface of the circular hole, the amount of lubricant and gas pushed out (discharged amount) from the closed space increases, so that an increase in pressure in the closed space can be further suppressed. Moreover, the fall of pump efficiency can further be suppressed.
  • the negative pressure pump according to a fourth aspect of the present invention is the negative pressure pump according to the third aspect, wherein the hole-side groove is the same as the rotation direction of the vane from the concave side of the circular hole toward the opposite side of the concave. It is a spiral that turns in the direction.
  • the hole-side groove portion is formed in a spiral shape that turns in the same direction as the vane rotation direction from the concave portion side of the circular hole toward the opposite side of the concave portion. ), A force in the rotation direction of the vane acts on the lubricant in the hole side groove. As a result, the lubricant is guided to the outside of the housing through the hole side groove and discharged.
  • the negative pressure pump according to a fifth aspect of the present invention is the negative pressure pump according to any one of the first to fourth aspects, wherein the recess is a boundary between the inner wall surface and the bottom surface from the edge of the circular hole. It extends to.
  • the lubricant near the boundary also enters the recess. Therefore, more lubricant can be discharged
  • a negative pressure pump according to a sixth aspect of the present invention is the negative pressure pump according to the first aspect, wherein the vane is formed on an outer peripheral surface of the shaft portion, and the vane is a part of the inner wall surface that is in contact with the discharge portion and the support portion.
  • a shaft-side groove that communicates the recess with the outside of the housing.
  • the shaft that communicates the recess and the outside of the housing when the vane is positioned between the discharge portion and a part of the inner wall surface that the support portion contacts. Since the side groove portion is formed, the lubricant guided to the circular hole through the concave portion is pushed into the shaft side groove portion constituting the gap between the circular hole and the shaft portion by the pressure of the closed space. In this way, by forming the shaft-side groove on the outer peripheral surface of the shaft, the amount of lubricant and gas pushed out (discharged amount) from the closed space increases, so that an increase in pressure in the closed space can be further suppressed. Moreover, the fall of pump efficiency can further be suppressed.
  • the negative pressure pump according to a seventh aspect is the negative pressure pump according to the sixth aspect, wherein the shaft-side groove portion is in a direction opposite to the rotation direction of the vane from the support portion side of the shaft portion toward the opposite side of the support portion. It has a spiral shape that swivels.
  • the shaft-side groove portion is formed in a spiral shape that turns in the direction opposite to the rotation direction of the vane from the support portion side of the shaft portion toward the opposite side of the support portion. ), A force in the direction opposite to the rotation direction of the vane acts on the lubricant in the shaft side groove. As a result, the lubricant is guided to the outside of the housing through the shaft side groove and discharged.
  • a cylinder head cover according to an eighth aspect of the present invention includes the negative pressure pump according to any one of the first to seventh aspects, part of which constitutes the casing and the other part as the power source. Cover the cylinder head of the engine.
  • the manufacturing cost can be reduced compared to a case where the cylinder head cover and the housing of the negative pressure pump are separated. it can.
  • the cylinder head cover includes the negative pressure pump according to any one of the first to seventh aspects, the effects obtained by this negative pressure pump are exhibited.
  • the negative pressure pump and the cylinder head cover of the present invention it is possible to suppress a decrease in pump efficiency while suppressing an excessive pressure from acting on the vane.
  • FIG. 5 is a cross-sectional view of the housing of FIG. 4 taken along the line 5X-5X. It is the expansion perspective view which expanded the part pointed by the arrow 6X of the housing
  • FIG. 7 is a cross-sectional view taken along the line 7X-7X of the recess of the housing in FIG. 6.
  • FIG. 8 is a cross-sectional view taken along the line 8X-8X of the recess of the housing in FIG. 6. It is an expansion perspective view which shows the 1st modification of the recessed part formed in the housing
  • the negative pressure pump 10 (see FIG. 1) of the present embodiment is a device that generates negative pressure using an engine as a power source, and is used in a negative pressure brake booster (not shown) of a vehicle.
  • this invention is not limited to the said structure, You may use a motor etc. as a motive power source of a negative pressure pump. Further, the negative pressure pump of the present invention may be used in addition to the negative pressure type brake booster as long as it is a device that uses negative pressure.
  • the negative pressure pump 10 has a cylindrical shape with a bottom, the opening 26 is closed by a lid 38, and a lubricant (in this embodiment, as an example, engine oil ( A non-compressible fluid).) Is supplied, a rotating shaft 40 in which the support portion 44 is disposed in the housing 20, and the rotating shaft 40 is disposed in the housing 20.
  • a lubricant in this embodiment, as an example, engine oil ( A non-compressible fluid).
  • air compressible fluid
  • the “tubular shape” of the present embodiment includes a cylindrical shape, a long cylindrical shape (elliptical cylindrical shape), a polygonal cylindrical shape having a cross-sectional shape of an inner wall surface of a circle or an ellipse (ellipse), and these cylindrical shapes.
  • a combined cylindrical shape is included.
  • the “cylindrical shape” includes a cylindrical shape whose inner diameter changes along the axial direction.
  • the bottomed cylindrical housing 20 includes a cylindrical cylindrical wall portion 22 and a bottom portion that closes the other axial side (right side in FIG. 5) of the cylindrical wall portion 22. 24.
  • One side (the left side in FIG. 5) of the cylindrical wall portion 22 in the axial direction is open and constitutes an opening portion 26 of the housing 20.
  • the inner wall surface 22A of the cylindrical wall portion 22 (housing 20) has an elliptical cross-sectional shape.
  • the outer peripheral surface 44A of the support portion 44 is in contact with a part of the inner wall surface 22A.
  • a curved surface 28 (see FIGS. 2 and 4) having a shape along the outer peripheral surface 44A is formed on the inner wall surface 22A at a portion in contact with the outer peripheral surface 44A.
  • the curved surface 28 is curved with the same curvature as the outer peripheral surface 44A.
  • the cylindrical wall portion 22 is formed with a suction portion 30 that is a mouth portion for sucking gas into the housing 20.
  • the suction portion 30 is disposed downstream of the curved surface 28 in the rotation direction of the vane 50 (hereinafter simply referred to as “vane rotation direction”). Note that the vane 50 of the present embodiment is configured to rotate counterclockwise (in the direction of arrow R in FIG. 3) when viewed from the lid 38 side when generating negative pressure.
  • the suction part 30 is configured to be connected with a check valve (not shown) having a check function.
  • the suction part 30 and a negative pressure brake booster (not shown) are connected via this check valve.
  • the check valve is configured to allow the flow of gas from the negative pressure type brake booster to the suction unit 30 and stop the flow of gas and lubricant from the suction unit 30 to the negative pressure type brake booster. Yes.
  • the bottom portion 24 is plate-shaped and extends in a direction orthogonal to the axial direction of the cylindrical wall portion 22.
  • a circular hole 32 is formed in the bottom portion 24 at a position eccentric with respect to the center of the casing (center of the cylindrical wall portion 22 (housing 20)).
  • the thickness (plate thickness) of the portion where the circular hole 32 is formed is thicker than the other portions.
  • the shaft portion 42 of the rotating shaft 40 is fitted into the circular hole 32.
  • the shaft portion 42 has an outer peripheral surface 42A in contact with the hole wall surface 32A of the circular hole 32, and is rotatably supported by the hole wall surface 32A.
  • the bottom portion 24 is formed with a discharge portion 34 (see FIG. 3) which is a mouth portion for discharging the lubricant in the housing 20 and the gas sucked from the suction portion 30.
  • the discharge part 34 is arranged downstream of the suction part 30 in the vane rotation direction.
  • the discharge part 34 is obstruct
  • the discharge valve is configured to allow the flow of gas and lubricant from the inside of the housing 20 to the outside, and stop the flow of gas and lubricant from the outside to the housing 20.
  • a plate-like lid 38 is detachably attached to the opening 26 of the housing 20 (see FIG. 1).
  • a sealing member (not shown) is disposed at the abutting portion between the lid body 38 and the housing 20. This seal member prevents the gas and lubricant in the housing 20 from leaking between the lid 38 and the housing 20 in a state where the lid 38 is mounted on the housing 20.
  • the internal space of the housing 20 forms a pump chamber 36.
  • the pump chamber 36 includes an inner wall surface 22A, a bottom surface 24A, and a closed surface (back surface) of the lid body 38.
  • the housing 20 is made of resin. Specifically, the housing 20 is an integrally molded product of resin.
  • the resin forming the casing 20 either a thermosetting resin or a thermoplastic resin may be used.
  • the thermosetting resin include phenol resins, urea resins, melamine resins, epoxy resins, polyamide resins, and the like.
  • the thermoplastic resin include urethane resins, olefin resins, vinyl chloride resins, polyacetal resins, polyamide resins, and polyimide resins.
  • the resin forming the housing 20 is a polyamide-based resin (for example, nylon) from the viewpoint of toughness and flexibility. Note that the present invention is not limited to this configuration, and the housing 20 may be formed of metal, but the housing 20 is preferably formed of resin from the viewpoint of weight and manufacturing cost.
  • the lid body 38 is made of resin in the same manner as the housing 20.
  • the resin forming the lid 38 may be the same as or different from the resin forming the housing 20.
  • the lid body 38 is formed of the same resin as that forming the housing 20.
  • the rotating shaft 40 constitutes an intermediate portion in the axial direction, constitutes a shaft portion 42 that is rotatably fitted in the circular hole 32, and constitutes one end side in the axial direction.
  • a support portion 44 disposed in the body 20 and an engaging convex portion that constitutes the other end side in the axial direction and engages with a joint 12 (for example, Oldham coupling) attached to a camshaft (not shown). 46.
  • the shaft portion 42 and the support portion 44 are coaxial.
  • the rotating shaft 40 is disposed at a position where the rotation center C is eccentric with respect to the center of the casing with the shaft portion 42 fitted in the circular hole 32 (see FIG. 3).
  • the shaft portion 42 has a cylindrical shape and is rotatably fitted in the circular hole 32 of the housing 20.
  • a through hole 48 extending in the axial direction is formed at the center of the shaft portion 42.
  • the through hole 48 extends to the tip of the engaging convex portion 46 and opens to the tip surface.
  • the lubricant is fed into the through-hole 48 from an internal flow path of a camshaft (not shown).
  • the lubricant fed from the camshaft is supplied through the through hole 48 into the pump chamber 36 (inside the housing 20).
  • For the through hole 48 see the rotary shaft 82 of the second embodiment in FIGS.
  • the support portion 44 is substantially cylindrical and has a larger diameter than the shaft portion 42. Moreover, the support part 44 is arrange
  • a groove 45 extending along the direction orthogonal to the axial direction of the rotating shaft 40, that is, the diameter direction of the rotating shaft 40 is formed in the support portion 44.
  • the support portion 44 is divided in half by the groove 45.
  • the engaging projection 46 is connected to the camshaft, which is a constituent member of the engine, via the joint 12 described above. For this reason, when the camshaft rotates, the rotating shaft 40 rotates (power is transmitted) via the joint 12.
  • the rotary shaft 40 is a member that transmits engine power from the camshaft through the joint 12 and is therefore formed of a metal material (for example, iron or aluminum) from the viewpoint of strength. Note that the rotation shaft may be formed of resin if sufficient strength can be secured.
  • the rotary shaft 40 and the camshaft are coupled using the joint 12, but the present invention is not limited to this configuration.
  • the rotary shaft 40 and the camshaft may be directly connected without using the joint 12.
  • a plate-like vane 50 is inserted and disposed in the groove 45 of the support portion 44.
  • the vane 50 is supported by a groove wall 45 ⁇ / b> A of the groove 45 so that both plate surfaces 50 ⁇ / b> A can reciprocate in a direction perpendicular to the rotation shaft 40 (diameter direction of the rotation shaft 40). Thereby, the vane 50 rotates integrally with the rotating shaft 40.
  • the vane 50 rotates integrally with the rotating shaft 40, thereby reciprocating in the diametrical direction of the rotating shaft 40 due to centrifugal force, and the both end portions 50 ⁇ / b> B in the longitudinal direction are pressed against the inner wall surface 22 ⁇ / b> A of the housing 20. Slide on each. At this time, in the vane 50, one side portion 50C in the width direction slides on the closing surface of the lid body 38, and the other side portion in the width direction slides on the bottom surface 24A.
  • the vane 50 partitions the inside of the housing 20 (in the pump chamber 36) into a plurality of spaces.
  • the space defined by the vane 50 is configured such that the volume gradually decreases from the suction unit 30 side toward the discharge unit 34 side as the vane 50 rotates. That is, the volume of the space partitioned by the vane 50 changes as the vane 50 rotates.
  • the vane 50 is formed of resin, but the present invention is not limited to this configuration, and may be formed of metal.
  • the bottom surface 24 ⁇ / b> A of the housing 20 is formed with a recess 60 that communicates with the circular hole 32 between the discharge portion 34 and the curved surface 28 in the vane rotation direction. Yes.
  • the recess 60 receives the lubricant moved by the vane 50 and guides it to the circular hole 32. Specifically, the lubricant received in the concave portion 60, in other words, the lubricant that has entered the concave portion 60 is guided to the circular hole 32 along the concave bottom surface.
  • the recess 60 extends from the edge of the circular hole 32 to the boundary 24C between the inner wall surface 22A and the bottom surface 24A.
  • the boundary 24C may be rephrased as an end portion on the outer peripheral side of the bottom surface 24A.
  • the depth from the bottom surface 24 ⁇ / b> A of the recess 60 gradually increases from the upstream side toward the downstream side in the vane rotation direction when viewed in a cross section along the circumferential direction of the bottom portion 24.
  • this invention is not limited to the said structure, You may make the depth from the bottom face 24A of the recessed part 60 into the same depth by the vane rotation direction upstream and downstream.
  • the depth from the bottom surface 24 ⁇ / b> A of the recess 60 is the same from the edge of the circular hole 32 to the boundary 24 ⁇ / b> C when viewed in a cross section along the radial direction of the bottom 24.
  • the hole wall surface 32 ⁇ / b> A of the circular hole 32 is formed with a hole-side groove 62 that allows the recess 60 to communicate with the outside of the housing 20.
  • the hole side groove 62 extends spirally along the hole wall surface 32A.
  • the hole-side groove 62 has a spiral shape that turns in the same direction as the vane rotation direction from the concave portion 60 side of the circular hole 32 toward the opposite side.
  • the hole-side groove 62 has a spiral shape that is counterclockwise (counterclockwise) when viewed from the lid 38 side.
  • the hole-side groove 62 of the present embodiment has a constant groove width and groove depth from one end on the recess 60 side to the other end opposite to the recess 60, but the present invention is not limited to this configuration. . At least one of the groove width and the groove depth of the hole-side groove 62 may be changed from the one end to the other end.
  • the vane 50 when power is transmitted from an engine as a power source and the rotation shaft rotates, the vane 50 also rotates integrally with the rotation shaft 40. By this rotation, the vane 50 receives centrifugal force and moves in a direction orthogonal to the rotation shaft 40 (diameter direction of the rotation shaft), and the end portion 50B slides on the inner wall surface 22A of the housing 20. At this time, one side portion 50C of the vane 50 slides on the closing surface (back surface) of the lid body 38, and the other side portion slides on the bottom surface 24A of the housing 20.
  • the rotation center C of the rotation shaft 40 is decentered with respect to the center of the casing, when the rotation shaft 40 and the vane 50 rotate together, the volume of the space defined by the vane 50 increases or decreases.
  • the space partitioned by the vanes 50 first, gas is sucked from the suction portion 30 when the volume is increased, and then, the gas sucked when the volume is decreased is discharged from the discharge portion 34 while being compressed.
  • a negative pressure can be generated on the device side by sucking the gas from the negative pressure type brake booster connected to the suction portion 30.
  • the vane 50 causes the discharge portion 34 to move.
  • Lubricant remaining without being completely discharged after passing is received by the recess 60, in other words, the remaining lubricant enters the recess 60.
  • the recess 60 communicates with the circular hole 32, the lubricant that has entered is guided to the circular hole 32.
  • the pressure in the space (hereinafter referred to as “closed space”) 64 between the vane 50 that has passed through the discharge portion 34 and the rotating shaft 40 (support portion 44) is increased due to a decrease in volume.
  • the lubricant guided to the circular hole 32 is pushed into the gap between the hole wall surface 32A of the circular hole 32 and the outer peripheral surface 42A of the shaft portion 42 by the pressure of the closed space 64 (see FIG. 3). At this time, the gas remaining without being discharged is also mixed with the lubricant and pushed into the gap. Thereby, since the pressure rise of the closed space 64 is suppressed, it is suppressed that an excessive pressure acts on the vane 50. FIG. As a result, the vane 50 is prevented from being damaged.
  • the frictional force between the hole wall surface 32A of the circular hole 32 and the outer peripheral surface 42A of the shaft portion 42 is reduced by the lubricant pushed into the gap between the circular hole 32 and the shaft portion 42.
  • wear of the hole wall surface 32A of the circular hole 32 and the outer peripheral surface 42A of the shaft portion 42 is suppressed.
  • the durability of the negative pressure pump 10 is improved.
  • the rotation of the rotating shaft 40 is smooth due to the lubricant, the energy loss of the engine is also suppressed.
  • the hole wall surface 32 ⁇ / b> A of the circular hole 32 is formed with the hole side groove portion 62 that allows the concave portion 60 and the outside of the housing 20 to communicate with each other.
  • the lubricant is pushed into the hole-side groove 62 that forms a gap between the circular hole 32 and the shaft portion 42 by the pressure of the closed space 64.
  • the amount of lubricant and gas pushed out (discharged amount) from the closed space 64 increases, so that the pressure in the closed space 64 is further increased. Can be suppressed. Moreover, the fall of pump efficiency can further be suppressed.
  • the hole-side groove portion 62 has a spiral shape that turns in the same direction as the vane rotation direction from the concave portion 60 side of the circular hole 32 toward the opposite side of the concave portion 60, the rotation shaft 40 (shaft portion 42). Due to the rotation, a force in the vane rotation direction acts on the lubricant in the hole-side groove 62. Thereby, the lubricant is guided to the outside of the housing 20 through the hole side groove 62 and discharged.
  • the recess 60 extends from the edge of the circular hole 32 to the boundary 24C between the inner wall surface 22A and the bottom surface 24A, the lubricant near the boundary 24C also enters the recess 60. Thereby, more lubricant can be discharged from the gap between the circular hole 32 and the shaft portion 42 (including the hole-side groove portion 62) to the outside of the housing 20 through the recess 60.
  • the negative pressure pump 10 of the present embodiment it is possible to suppress a decrease in pump efficiency while suppressing an excessive pressure from acting on the vane 50.
  • the lubricant sent from the camshaft is supplied to the inside of the housing 20 through the through hole 48 of the rotary shaft 40, and then the supplied lubricant is supplied between the circular hole 32 and the shaft portion 42. It discharges to the outside through the gap (including the hole-side groove 62). For this reason, for example, in order to interpose the lubricant between the circular hole 32 and the shaft portion 42, a flow path that branches off from the middle of the through hole 48 and opens to the outer peripheral surface 42 ⁇ / b> A of the shaft portion 42, etc.
  • the negative pressure pump 10 of the present embodiment has a simple structure of the rotary shaft 40. Thereby, the raise of the manufacturing cost of the rotating shaft 40 can be suppressed.
  • the housing 20 is formed of resin, for example, an increase in manufacturing cost and weight of the housing 20 can be suppressed as compared with a case where the housing is formed of metal.
  • the housing 20 by forming the housing 20 from resin, the recess 60 and the hole-side groove 62 can be easily formed.
  • the depth from the bottom surface 24 ⁇ / b> A of the concave portion 60 is changed from the edge of the circular hole 32 to the boundary 24 ⁇ / b> C when viewed in a cross section along the radial direction of the bottom portion 24.
  • the present invention is not limited to this configuration.
  • the depth from the bottom surface 24 ⁇ / b> A of the concave portion 60 may be gradually decreased from the edge of the circular hole 32 toward the boundary 24 ⁇ / b> C.
  • the lubricant that has entered the recess 70 can be smoothly guided to the circular hole 32.
  • it can apply also to below-mentioned 2nd Embodiment, 3rd Embodiment, etc.
  • the length along the circumferential direction of the bottom 24 of the opening that opens to the bottom 24 ⁇ / b> A of the recess 60 is changed from the edge of the circular hole 32.
  • the present invention is not limited to this configuration, and the length along the circumferential direction of the opening of the recess 60 is changed from the edge of the circular hole 32 to the boundary 24C. It is good also as a structure.
  • the length along the circumferential direction of the bottom 24 of the opening that opens to the bottom 24 ⁇ / b> A of the recess 72 is changed from the edge of the circular hole 32 to the boundary 24 ⁇ / b> C. It is good also as a structure which makes it gradually shortened toward in other words, in other words, becomes gradually long toward the edge part of the circular hole 32 from the boundary 24C. In addition, about the said structure, it can apply also to below-mentioned 2nd Embodiment, 3rd Embodiment, etc.
  • the hole-side groove 62 is configured to extend spirally along the inner wall surface 22A, but the present invention is not limited to this configuration.
  • the hole-side groove portion may be configured to extend linearly along the axial direction of the cylindrical wall portion 22, or the hole-side groove portion may be configured to extend in a curved shape (as an example, a wave shape) in the axial direction of the cylindrical wall portion.
  • the hole-side groove portion (including the hole-side groove portion 62) may be divided into a plurality of portions on the way from the concave portion 60 side to the opposite side of the concave portion 60.
  • the discharge portion 34 and the recess 60 are arranged at an interval in the vane rotation direction (the discharge portion 34 and the recess 60 are independent).
  • the present invention is not limited to this configuration.
  • a part of the discharge unit 34 and the recess 60 may be connected.
  • it can apply also to below-mentioned 2nd Embodiment, 3rd Embodiment, etc.
  • the negative pressure pump 80 of this embodiment does not form the hole side groove 62 on the hole wall surface 32A of the circular hole 32, but instead forms the shaft side groove 84 on the outer peripheral surface 42A of the shaft 42 of the rotating shaft 82. ing. In addition, about another structure, it is the same structure as 1st Embodiment.
  • the shaft-side groove portion 84 is configured to allow the recess 60 to communicate with the outside of the housing 20 when the vane 50 is located between the discharge portion 34 and the curved surface 28.
  • the shaft side groove portion 84 extends spirally along the outer peripheral surface 42 ⁇ / b> A of the shaft portion 42.
  • the shaft-side groove portion 84 has a spiral shape (clockwise spiral shape) that turns in the direction opposite to the vane rotation direction from the support portion 44 side toward the opposite side.
  • the shaft-side groove portion 84 is formed at two positions by being shifted by half a circumference with respect to the outer peripheral surface 42A of the shaft portion 42. .
  • a shaft-side groove portion 84 that allows the recess 60 and the outside of the housing 20 to communicate with each other when the vane 50 is positioned between the discharge portion 34 and the curved surface 28 is formed on the outer peripheral surface 42 ⁇ / b> A of the shaft portion 42. Because of the formation, the lubricant guided to the circular hole 32 through the recess 60 forms a gap between the hole wall surface 32A of the circular hole 32 and the outer peripheral surface 42A of the shaft part 42 by the pressure of the closed space 64.
  • the shaft-side groove portion 84 has a spiral shape that turns in the direction opposite to the vane rotation direction from the support portion 44 side toward the opposite side of the support portion 44. 42), the force in the direction opposite to the vane rotation direction acts on the lubricant in the shaft-side groove 84. Thereby, the lubricant is guided to the outside of the housing 20 through the shaft side groove 84 and discharged.
  • the groove width and the groove depth of the shaft side groove portion 84 of the present embodiment are constant from one end on the support portion 44 side to the other end on the opposite side to the support portion 44, but the present invention is not limited to this configuration. At least one of the groove width and the groove depth of the hole-side groove 62 may be changed from the one end to the other end.
  • the shaft-side groove portion 84 is configured to extend spirally along the outer peripheral surface 42A of the shaft portion 42, but the present invention is not limited to this configuration.
  • the shaft-side groove portion 84 may be configured to extend linearly along the axial direction of the rotary shaft 40, or the shaft-side groove portion 84 may be configured to extend in a curved shape (as an example of a wave shape) in the axial direction of the rotary shaft 40.
  • the shaft-side groove portion (including the shaft-side groove portion 84) may be configured to branch into a plurality on the way from the support portion 44 side to the opposite side of the support portion 44.
  • the configuration related to the shaft-side groove 84 of the rotary shaft 82 used in the negative pressure pump 80 of the present embodiment may be applied to the rotary shaft 40 of the first embodiment.
  • the hole-side groove 62 and the shaft-side groove 84 can further suppress an excessive pressure from acting on the vane 50 and can further suppress a decrease in pump efficiency.
  • the cylinder head cover 100 of the present embodiment is formed of resin, specifically, the same resin as the housing 20 of the first embodiment. Further, as shown in FIG. 13, the cylinder head cover 100 is partly a negative pressure pump casing 120 having the same shape as the casing 20 of the negative pressure pump 10 of the first embodiment, and the other part is the power.
  • the cover portion 110 covers the cylinder head 92 of the engine 90 as a source.
  • the cylinder head cover 100 includes a negative pressure pump unit similar to the negative pressure pump 10 of the first embodiment.
  • the rotating shaft 40 and the camshaft 94 are directly connected.
  • the effect of the cylinder head cover 100 of this embodiment is demonstrated. Since a part of the cylinder head cover 100 is used as the negative pressure pump casing 120, for example, the manufacturing cost is reduced as compared with the case where the cylinder head cover and the negative pressure pump 10 are separated as in the first embodiment. be able to.
  • the cylinder head cover 100 of the present embodiment is formed with a negative pressure pump portion similar to the negative pressure pump 10 of the first embodiment, but a negative pressure pump portion similar to the negative pressure pump 80 of the second embodiment is provided. It may be formed. Further, the rotary shaft 82 of the second embodiment may be used instead of the rotary shaft 40.
  • the support portion 44 of the rotating shaft 40 abuts a part of the inner wall surface 22 ⁇ / b> A of the housing 20 and supports one vane 50.
  • the present invention is not limited to this configuration.
  • the support part 134 of the rotating shaft 132 does not contact the inner wall surface 22A of the housing 20, and there are three or more support parts 134 (FIG. 14, four vanes 136 may be supported.
  • the negative pressure pump 130 has the same configuration as the negative pressure pump 10 of the first embodiment except for the configuration of the support portion 134 and the vane 136 of the rotating shaft 132 and the arrangement position of the recess 60. The description is omitted.
  • the support portion 134 constitutes one end side of the rotation shaft 132 in the axial direction, and a through hole 48 extends from the shaft portion 42 in the center.
  • three or more grooves (four in FIG. 14) extending in the axial direction with an interval in the circumferential direction are formed.
  • a plate-like vane 136 is inserted and disposed in the groove 135.
  • the vane 136 is supported by the groove wall 135 ⁇ / b> A of the groove 135 so that both plate surfaces 136 ⁇ / b> A can reciprocate in a direction perpendicular to the rotation shaft 132 (diameter direction of the rotation shaft 132). Thereby, the vane 136 rotates integrally with the rotating shaft 40. In addition, the vane 136 rotates integrally with the rotation shaft 132, so that the end portion 136B is pressed against the inner wall surface 22A of the housing 20 by reciprocating in the diameter direction of the rotation shaft 132 by centrifugal force. Slide each.
  • the vane 136 partitions the inside of the housing 20 (in the pump chamber 36) into a plurality of spaces.
  • the space partitioned by the vane 136 is configured such that the volume gradually decreases from the suction unit 30 side toward the discharge unit 34 side as the vane 136 rotates. That is, the volume of the space partitioned by the vane 136 changes as the vane 136 rotates.
  • the arrangement interval of the vanes 136 is set to be narrower than the interval between the suction unit 30 and the discharge unit 34 in the vane rotation direction. In other words, as shown in FIG.
  • the arrangement interval of the vanes 136 is set so that two adjacent vanes 136 are arranged between the discharge unit 34 and the suction unit 30. Further, in the negative pressure pump 130, a recess 60 is formed between the suction part 30 and the discharge part 34 in the vane rotation direction on the bottom surface 24A. Next, the operation of the negative pressure pump 130 will be described. In the negative pressure pump 130, a recess 60 is formed between the discharge portion 34 and the suction portion 30 in the vane rotation direction on the bottom surface 24A of the housing 20. Therefore, the lubricant remaining without being discharged after the vane 136 passes through the discharge portion 34 enters the recess 60.
  • the lubricant that has entered is guided to the circular hole 32.
  • a space between the vane 136 that has passed through the discharge unit 34 and the vane 136 that has passed through the discharge unit 34 and has not reached the suction unit 30 prior to the vane 136 (hereinafter referred to as “closed space”).
  • .) 138 is increased in pressure due to a decrease in volume, so that the lubricant guided in the circular hole 32 is moved between the hole wall surface 32A of the circular hole 32 and the outer peripheral surface 42A of the shaft portion 42 by the pressure of the closed space 138. It is pushed into the gap.
  • the gas remaining without being discharged is also mixed with the lubricant and pushed into the gap.
  • the pressure rise of closed space 138 is suppressed, it is suppressed that an excessive pressure acts on the vane 136.
  • FIG. As a result, the vane 136 is prevented from being damaged.
  • Other functions and effects are the same as those of the negative pressure pump 10 of the first embodiment.
  • the configuration of the negative pressure pump 130 may be applied to the negative pressure pump 80 of the second embodiment and the negative pressure pump portion of the cylinder head cover of the third embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2014/074135 2013-11-22 2014-09-11 負圧ポンプ及びシリンダヘッドカバー Ceased WO2015076001A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US14/888,959 US9562531B2 (en) 2013-11-22 2014-09-11 Negative pressure pump and cylinder head cover
EP14864534.4A EP2982865B1 (en) 2013-11-22 2014-09-11 Negative pressure pump
CN201480025296.0A CN105209762B (zh) 2013-11-22 2014-09-11 负压泵及汽缸头盖

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-242292 2013-11-22
JP2013242292A JP6210859B2 (ja) 2013-11-22 2013-11-22 負圧ポンプ及びシリンダヘッドカバー

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WO2015076001A1 true WO2015076001A1 (ja) 2015-05-28

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EP (1) EP2982865B1 (https=)
JP (1) JP6210859B2 (https=)
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WO (1) WO2015076001A1 (https=)

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Publication number Priority date Publication date Assignee Title
JP5833797B1 (ja) * 2014-06-12 2015-12-16 三桜工業株式会社 負圧ポンプ及びその製造方法
JP6382877B2 (ja) 2016-03-24 2018-08-29 大豊工業株式会社 ベーンポンプ
EP3862532B1 (en) * 2020-02-07 2025-11-05 Fluid-O-Tech S.r.l. Pump particularly for pumping a liquid such as ink, paint, glue or the like

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Publication number Priority date Publication date Assignee Title
JPS5928081A (ja) * 1982-05-25 1984-02-14 テイ−ア−ルダブリユ・インコ−ポレ−テツド 回転ポンプ組立体
JP2004263690A (ja) * 2003-02-13 2004-09-24 Aisan Ind Co Ltd ベーン式バキュームポンプ
JP2004285978A (ja) 2003-03-25 2004-10-14 Toyoda Mach Works Ltd ベーン式気体ポンプ
JP2006226166A (ja) * 2005-02-16 2006-08-31 Taiho Kogyo Co Ltd ベーンポンプ
WO2006122516A1 (de) * 2005-05-19 2006-11-23 Ixetic Hückeswagen Gmbh Flügelzellenpumpe
JP2012036807A (ja) * 2010-08-06 2012-02-23 Nissan Motor Co Ltd ベーンポンプ

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Publication number Priority date Publication date Assignee Title
US3499600A (en) * 1968-03-21 1970-03-10 Whirlpool Co Rotary compressor
CN200964870Y (zh) * 2006-10-31 2007-10-24 黄庆培 一种旋转叶片活塞
JP5447149B2 (ja) * 2010-04-27 2014-03-19 大豊工業株式会社 ベーンポンプ

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Publication number Priority date Publication date Assignee Title
JPS5928081A (ja) * 1982-05-25 1984-02-14 テイ−ア−ルダブリユ・インコ−ポレ−テツド 回転ポンプ組立体
JP2004263690A (ja) * 2003-02-13 2004-09-24 Aisan Ind Co Ltd ベーン式バキュームポンプ
JP2004285978A (ja) 2003-03-25 2004-10-14 Toyoda Mach Works Ltd ベーン式気体ポンプ
JP2006226166A (ja) * 2005-02-16 2006-08-31 Taiho Kogyo Co Ltd ベーンポンプ
WO2006122516A1 (de) * 2005-05-19 2006-11-23 Ixetic Hückeswagen Gmbh Flügelzellenpumpe
JP2012036807A (ja) * 2010-08-06 2012-02-23 Nissan Motor Co Ltd ベーンポンプ

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Title
See also references of EP2982865A4

Also Published As

Publication number Publication date
US20160084252A1 (en) 2016-03-24
JP2015101999A (ja) 2015-06-04
CN105209762B (zh) 2016-12-21
US9562531B2 (en) 2017-02-07
EP2982865B1 (en) 2017-03-22
EP2982865A1 (en) 2016-02-10
JP6210859B2 (ja) 2017-10-11
CN105209762A (zh) 2015-12-30
EP2982865A4 (en) 2016-05-18

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