EP2075469A2 - Flügelzellenpumpe - Google Patents

Flügelzellenpumpe Download PDF

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Publication number
EP2075469A2
EP2075469A2 EP08022401A EP08022401A EP2075469A2 EP 2075469 A2 EP2075469 A2 EP 2075469A2 EP 08022401 A EP08022401 A EP 08022401A EP 08022401 A EP08022401 A EP 08022401A EP 2075469 A2 EP2075469 A2 EP 2075469A2
Authority
EP
European Patent Office
Prior art keywords
rotary unit
casing
vane pump
fluid force
axial direction
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.)
Withdrawn
Application number
EP08022401A
Other languages
English (en)
French (fr)
Inventor
Etsuo Matsuki
Masaaki Nishikata
Tsuyoshi Kusakabe
Tsukasa Hojo
Masaki Nagano
Ken Yamamoto
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.)
Panasonic Electric Works Co Ltd
Original Assignee
Panasonic Electric Works 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
Priority claimed from JP2008092263A external-priority patent/JP4636108B2/ja
Application filed by Panasonic Electric Works Co Ltd filed Critical Panasonic Electric Works Co Ltd
Publication of EP2075469A2 publication Critical patent/EP2075469A2/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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 working space, being surfaces of revolution
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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

Definitions

  • the present invention relates to a vane pump.
  • a rotary type compressor including a conventional vane pump is disclosed in Japanese patent Laid-open Application No. S64-77783 .
  • the disclosed rotary type compressor has a space of a substantially constant height formed by structural parts of a casing stacked in the rotation axis direction of a cylindrical rotary unit.
  • the rotary unit and vanes are accommodated in the space.
  • the vanes are inserted into slits which are radially formed in the rotary unit in such a way as to protrude from and be retracted into the slits.
  • the volumes of a plurality of pump chamber divided by the vanes are periodically increased or reduced, so that fluid is sucked into and discharged from the pump chamber.
  • the present invention provides a vane pump capable of reducing the axial reciprocating motion of a rotary unit or vanes thereof.
  • a vane pump including: a plurality of slits which are formed in a base portion of a rotary unit rotating in a casing and extend radially from a rotation axis of a rotary unit to be opened outwardly in a radial direction; a vane received in each of the slits to be protruded from or retreated into the slit; an annular chamber formed around the base portion in the casing; a plurality of pump rooms formed by defining the annular chamber by using the plurality of vanes, the vane pump being operated to discharge fluid sucked into an associated pump room by rotating the rotary unit and thereby periodically increasing or reducing volume of the pump rooms; and a fluid force generating portion provided on at least one of the rotary unit and the casing to generate fluid force to the upper side in an axial direction of the rotation axis by rotation of the rotary unit.
  • the rotary unit is pressed to the upper side in the axial direction in the casing by fluid force generated by the rotation of the rotary unit, thus preventing the rotary unit from reciprocating axially in the casing.
  • a guide wall may be provided on the rotary unit and placed on the lower side in the axial direction of the rotation axis to be in sliding contact with an associated vane.
  • the guide wall limits the range in which the vanes may reciprocate in the axial direction.
  • the vane pump may further includes a thrust support unit for slidably supporting the rotary unit against the casing, the rotary unit being rotated by the fluid force applied to the upper side in the axial direction, wherein a diameter of a sliding portion of the thrust support unit is smaller than a diameter of the base portion.
  • the fluid force generating portion may be provided on the rotary unit, and includes a slanting surface which is inclined with respect to a rotating direction of the rotary unit.
  • the slanting surface is formed on the rotary unit, thus allowing the fluid force generating portion to be obtained in a relatively simple construction.
  • the fluid force generating portion may preferably be provided on the rotary unit, and includes a wing brought into contact with a counter flow of the fluid resulting from rotation of the rotary unit.
  • the wing is provided on the rotary unit, thus more reliably generating fluid force.
  • the fluid force generating portion may be provided on the rotary unit, and includes a spiral projection or groove formed around the rotation axis.
  • the fluid force generating portion may preferably be provided on the casing, and includes a protrusion which is opposite to the rotary unit in such a way as to protrude towards the rotary unit.
  • the fluid force generating portion is provided on the casing, and comprises a protrusion which is opposite to the rotary unit in such a way as to protrude towards the rotary unit.
  • the protruding portion is provided on the casing, thus allowing the fluid force generating portion to be obtained in a relatively simple configuration.
  • the rotary unit includes a cylindrical skirt portion which is concentric with the rotation axis and protrudes towards the lower side in the axial direction, and a cylindrical gap is formed between the skirt portion and the casing.
  • the cylindrical, annular gap having a predetermined length in the axial direction can be formed in the outer or inner circumference of a skirt portion.
  • leakage flow rate of the working fluid between the lower side of the rotary unit in the axial direction and the casing can be reduced.
  • the gap is formed to be concentric with a rotation axis.
  • the vane pump may further include a magnetized portion provided on the skirt portion; a stator core including a coil provided inside the skirt portion; and a motor having the magnetized portion and the stator core which are arranged in a radial direction of the rotation axis of the rotary unit to be spaced apart from each other.
  • the magnetized portion of the motor may be provided by effectively using the shape of the skirt portion which forms the cylindrical gap.
  • Fig. 1 is a cross sectional view showing a vane pump in accordance with the first embodiment of the present invention, taken along the line perpendicular to the rotation axis of the vane pump
  • Fig. 2 is a cross sectional view depicting the vane pump including the rotation axis
  • Fig. 3 is an exploded perspective view of the vane pump
  • Fig. 4 is an enlarged view showing a part of Fig. 2
  • Fig. 5 is a side view illustrating a rotary unit included in the vane pump.
  • the upper side in Fig. 2 , 3 and 4 is indicated as the upper side of the rotation axis Ax
  • the lower side is indicated as the lower side of the rotation axis Ax.
  • the vane pump 1 in accordance with a first embodiment of the present invention includes a casing 2.
  • An annular chamber 6 for receiving working fluid (liquid) therein is provided in the casing 2 to be positioned between the substantially cylindrical inner circumferential surface 3a of an annular ring 3 and the outer circumferential surface 5a of a substantially columnar base portion 5 of a rotary unit 4 which rotates around the rotation axis Ax.
  • the width w of the annular chamber 6 is changed along the circumferential direction of the rotation axis Ax.
  • the center C of the inner circumferential surface 3a and the rotation axis Ax are placed to be parallel to and offset from each other, so that the inner circumferential surface 3a of the ring 3 is eccentric from the base portion 5 of the rotary unit 4.
  • the annular chamber 6 has the minimum width at a right end of Fig. 1 .
  • the width w of the annular chamber 6 is gradually increased in the clockwise direction from the right end, so that the annular chamber 6 has the maximum width at the left end. Further, the width w of the annular chamber 6 is gradually reduced in the clockwise direction from the left end to the right end, so that the annular chamber 6 has the minimum width at the right end.
  • a plurality of slits 7 (four slits in the present embodiment) is formed in the base portion 5 to extend radially relative to the rotation axis Ax of the rotary unit 4 in such a way as to open outwardly in radial directions.
  • Rectangular bar-shaped or strip plate-like vanes 8 are received in the respective slits 7 so that the vanes 8 cab be protruded from or retreated into the respective slits 7.
  • the corresponding vane 8 is forced outwardly in the radial direction by the centrifugal force exerted by the rotation of the rotary unit 4 and the pressure of the working fluid flowing into the rotation axis Ax side of the slits 7. Therefore, while the vanes 8 are in sliding contact with the inner circumferential surface 3a, the vanes 8 rotate together with the rotary unit 4.
  • the annular chamber 6 is divided by the vanes 8 which are arranged at predetermined pitches in the circumferential direction of the annular chamber 6, thus forming as many pump rooms 9 as there are vanes 8 (four pump rooms in this embodiment).
  • the volume of each pump room 9 varies according to the change in the width w of the annular chamber 6. That is, each pump room 9 has the minimal volume at the right end of Fig. 1 .
  • the rotary unit 4 rotates in the rotating direction RD (the clockwise direction of Fig. 1 )
  • the volume of an associated pump room 9 is gradually increased.
  • the pump room 9 reaches the left end, the pump room 9 has the maximal volume.
  • the rotary unit 4 rotates further clockwise from the left end, the volume of the pump room 9 is gradually reduced.
  • the pump room 9 reaches the right end, the pump room 9 has the minimal volume.
  • a suction opening 11 is provided at the inner circumferential surface 3a of the ring 3 and the casing 2 (first casing 10) to face a section in which the volume of the pump room 9 is being enlarged
  • a discharge opening 12 is provided at the inner circumferential surface 3a of the ring 3 and the casing 2 to face a section in which the volume of the pump room 9 is being reduced.
  • the suction opening 11 communicates with a suction passage 14 in a suction pipe 13 which protrudes from the sidewall of the first casing 10, and the discharge opening 12 communicates with a discharge passage 16 of a discharge pipe 15 which protrudes parallel to the suction pipe 13.
  • a pump room 9 defined between two neighboring vanes 8 moves from the right end to the left end while the volume thereof is being increased.
  • the working fluid is fed from the suction passage 14 through the suction opening 11 to the pump room 9.
  • the pump room 9 moves from the left end to the right end while the volume thereof is being reduced.
  • the working fluid is discharged from the pump room 9 through the discharge opening 12 to the discharge passage 16.
  • the inflow and outflow of the working fluid relative to the pump rooms 9 are sequentially performed, so that the working fluid is continuously sucked and discharged by the vane pump 1.
  • the slits 7 formed in the base portion 5 of the rotary unit 4 are closed by the lower wall portion 17 at the lower side in the axial direction.
  • the vanes 8 reciprocate in the respective slits 7 while being in sliding contact with the lower wall portion 17. That is, in the present embodiment, the lower wall portion 17 corresponds to the guide wall.
  • communicating holes 17a are formed at the lower wall portion 17 to communicate with radially inner portions of the slits 7.
  • the working fluid of an exerting pressure is introduced into the slits 7 from a rear side of the lower wall portion 17 (the lower side in the axial direction) through the communicating holes 17a.
  • the exerting pressure has a value between the discharge pressure and the suction pressure.
  • the lower wall portion 17 has the shape of a disc which has at its center the rotation axis Ax and is perpendicular to the rotation axis Ax. A part of the lower wall portion 17 protrudes outwards from the outer circumferential surface 5a of the base portion 5 in the form of a flange. Further, a cylindrical skirt portion 18 protrudes from the outer edge of the lower wall portion 17. The skirt portion 18 is concentric with the rotation axis Ax, and protrudes in a direction away from the base portion 5 (towards the lower side in the axial direction) to have a constant thickness.
  • the skirt portion 18 serves as a rotor of the motor 19 which drives the rotary unit 4, and includes a magnetized portion 18a having N and S poles alternately in the circumferential direction to correspond to teeth 20a of a stator core 20 around which coils are wound. At least a portion of the skirt portion 18 serving as the magnetized portion 18a is made of a magnetic material. In this case, only a portion of the skirt portion 18 which faces the teeth 20a may be made of a magnetic material (e.g. a hard magnetic material including ferrite magnet or samarium-cobalt magnet), or the entire skirt portion 18 may be made of a magnetic material. Alternatively, the entire rotary unit 4 may be made of a magnetic material. In this case, the rotary unit 4 or the skirt portion 18 may be formed using a mixture which is obtained by mixing powder- or particle-type magnetic filler with resin material.
  • a magnetic material e.g. a hard magnetic material including ferrite magnet or samarium-cobalt magnet
  • recessed portions are provided on the outer circumferential surface 5a of the base portion 5 at regular pitches in such a way as to be recessed inwardly in a radial direction.
  • wings 5b are formed.
  • the wings 5b are rotated together with the base portion 5 (rotary unit 4).
  • the wings 5b face the suction opening 11
  • the performance of sucking the working fluid into the pump rooms 9 is increased.
  • the wings 5b face the discharge openings 12 the performance of discharging the working fluid from the pump rooms 9 is increased.
  • a bearing 22 for rotatably supporting a shaft is secured to the central portion of the base portion 5 (rotary unit 4).
  • the bearing 22 may include a sliding bearing such as a metal bushing, or a rolling bearing such as a needle bearing.
  • the rotary unit 4 is configured to be rotated around the rotation axis Ax in an internal space 2a (see Fig. 2 ) defined by the casing 2.
  • the casing 2 is provided with a first casing 10 which is positioned at the upper side in the axial direction (the upper sides in Figs. 2 and 3 ), a second casing 23 which is positioned at the lower side in the axial direction (the lower sides in Figs. 2 and 3 ), and a ring 3 which forms the outer circumferential surface of the annular chamber 6 (the inner circumferential surface 3a of the ring 3).
  • the ring 3 is provided with a cylindrical portion 3b which forms the outer circumferential surface of the annular chamber 6, and a flange 3c, which protrudes outwardly in the radial direction of the rotation axis Ax at the other side of the cylindrical portion 3b in the axial direction.
  • the ring 3 also includes ribs 3d which form the sidewalls of the suction passage 14 and the discharge passage 16. The cylindrical portion 3b and the ribs 3d protrude from the disc-shaped flange 3c in the axial direction of the rotation axis Ax such that their heights are almost equal to each other.
  • the ring 3 is held in a recessed portion 10b formed in the first casing 10. That is, the recessed portion 10b has a recess to allow the cylindrical portion 3b and the ribs 3d of the ring 3 to be fitted therein. Further, the outer circumference 3e of the flange 3c of the ring 3 is in contact with the annular wall 23a of the second casing 23 at the opposite side of the recessed portion 10b. The ring 3 is interposed between the first casing 10 and the second casing 23, so that the ring 3 is secured in the axial direction of the rotation axis Ax.
  • annular recessed portion 23b and a recessed portion 23c are formed in the second casing 23.
  • the annular recessed portion 23b receives the skirt portion 18 of the rotary unit 4, and the recessed portion 23c receives a part of the bearing 22 of the rotary unit 4 which protrudes to the second casing 23 (the lower side in the axial direction, the lower side in Fig. 2 or 3 ).
  • a portion extending outwards diametrically from the annular wall 23a provided on the outer circumference of the recessed portion 23b serves as a contact surface with the first casing 10.
  • An annular groove 23d for an O-ring 34 is formed in the contact surface, and the O-ring 34 is fitted into the groove 23d, thus sealing the junction between the first casing 10 and the second casing 23.
  • sealing members such as a gasket or an O-ring may be appropriately fitted into other junctions between components (e.g. the junction between the flange 3c of the ring 3 and the first casing 10), thus improving sealing performance at respective junctions.
  • the shaft 21 is arranged between the lower wall portion 23e of the recessed portion 23c and the protruding portion 10c of the first casing 10.
  • the center of the shaft 21 is the rotation axis Ax.
  • the shaft 21 passes through the bearing 22 which is provided in the center of the rotary unit 4, and is supported by the bearing 22 to be freely rotatable.
  • annular protruding portion 23f is provided between the recessed portions 23b and 23c in such a way as to protrude from the opposite side of the rotary unit 4 (the lower side in the axial direction, the lower side in Fig. 2 ) to the rotary unit 4.
  • the stator core 20 constituting the motor 19 is accommodated in an annular recessed portion 23j which is provided in the backside of the protruding portion 23f.
  • the stator core 20 is attached to the center of the surface 24a of a substrate 24, and is provided with a cylindrical portion 20b which is placed in the center of the stator core 20 to be concentric with the rotation axis Ax, and a plurality of teeth 20a which extend radially from the cylindrical portion 20b, with coils wound around the teeth 20a.
  • various electronic parts are mounted on a backside 24b (the lower side in the axial direction, the lower side in Fig. 2 ) which is opposite to the surface 24a of the substrate 24 having the stator core 20, and a driving circuit of the motor 19 and other circuits are formed in the backside 24b.
  • the conduction state of the coil wound around each tooth 20a is appropriately changed, so that the polarity of the outer circumference of each tooth 20a is changed. Therefore, circumferential thrust force is applied to the magnetized portion 18a (skirt portion 18) which is provided outward in the radial direction in such a way as to face the teeth 20a, thus rotating the rotary unit 4. Therefore, among several components of the second casing 23, a partition wall 23g interposed between the outer circumference of the stator core 20 (teeth 20a) and the skirt portion 18 must be made of a material having magnetic permeability. For this reason, the partition wall 23g or the entire second casing 23 are made of a material having magnetic permeability (e.g. stainless steel or resin material).
  • the substrate 24 is attached to the recessed portion 23c to isolate the recessed portion 23c from the opposite side of the rotary unit 4 (the lower side in the axial direction). Further, the substrate 24 is isolated from the opposite side of the rotary unit 4 (the lower side in the axial direction) by a substrate cover 25. Spacing projections 25a are provided on the substrate cover 25 to ensure a space for holding the electronic parts between the substrate 24 and the substrate cover 25.
  • each of the first casing 10 and the second casing 23 has the shape of a square. Further, through holes 10a (or 23k) are formed in four corners of the casing 10 (or 23), so that screws 26 pass through the through holes 10a and 23k to fasten the casings 10 and 23 to each other. By inserting the screws 26 into the through holes 10a and 23k and the through holes 25b formed in four corners of the substrate cover 25, and fastening nuts 27 to the screws 26, the vane pump 1 is assembled.
  • the materials or manufacturing method of respective components which constitute the vane pump 1 are appropriately selected in consideration of abrasion-resistance, corrosion resistance, swelling resistance, formability, and machining accuracy, in addition to the above-mentioned ability to be magnetized or magnetic permeability.
  • a fluid force generating portion 28 is provided on the rotary unit 4 to generate fluid force toward the upper side of the rotation axis Ax in the axial direction (the upper sides in Figs. 2 , 3 and 5 ) by the rotation of the rotary unit 4.
  • the rotary unit 4 is pressed towards the first casing 10 disposed opposite to the lower wall portion 17.
  • slanting surfaces 28A which are inclined with respect to the rotating direction RD of the rotary unit 4 are provided on an end surface 18b of the skirt portion 18 positioned at the lower side in the axial direction.
  • Each slanting surface 28A is formed from a front edge 28F to a rear edge 28R thereof when viewed along the rotating direction RD in such a way as to be inclined upwardly from the lower side in the axial direction (the lower side in Fig. 5 ) to the upper side in the axial direction (the upper side in Fig. 5 ).
  • each slanting surface 28A has the front edge 28F and the rear edge 28R and is inclined upwards from the front edge 28F to the rear edge 28R.
  • the front edge 28F and the rear edge 28R correspond to a trailing and a leading edge of the each slanting surface 28A rotating in the rotation direction RD.
  • a thrust support unit 29 is provided on the first casing 10 to slidably support the rotary unit 4 that is rotated while receiving the fluid force F (thrust force) acting toward the upper side in the axial direction.
  • F thrust force
  • a portion of the first casing 10 in which the shaft 21 is inserted and supported is protruded toward the lower side in the axial direction, thereby forming the protruding portion 10c.
  • the bottom surface 4b of the recessed portion 4a formed in the central portion of the rotary unit 4 (base portion 5) is in contact with a most-protruding surface 10d of the protruding portion 10c via a washer 30.
  • the thrust support unit 29 is provided with a washer 30, which is in contact with an axial end surface 22a (which is partially exposed to the bottom surface 4b of the recessed portion 4a) of the bearing 22 provided on the central portion of the rotary unit 4, so that abrasion resistance is easily increased.
  • such a configuration allows the abrasion resistance in this region to be adjusted by the specifications (e.g., material, dimensions, hardening treatment and the like) of a sliding contact portions between the washer 30 and the bearing 22, and the specifications of the main body (e.g., base portion 5, lower wall portion 17 and the like) of the rotary unit 4 may be selected in consideration of lightness, slidability of other sliding portions, corrosion resistance, and the like.
  • the specifications e.g., material, dimensions, hardening treatment and the like
  • the main body e.g., base portion 5, lower wall portion 17 and the like
  • the diameter D2 of the sliding portion is set to be smaller than the diameter D1 of the base portion 5.
  • a top surface 5c of the base portion 5 is in sliding contact with the first casing 10, and sliding resistance may be undesirably increased unless the through support portion is provided.
  • the diameter D2 of the sliding portion is set to be smaller than the diameter D1 of the base portion 5, so that the sliding resistance and friction can be further reduced.
  • a small gap 31 is arranged between a top surface 17b of the lower wall portion 17 and a bottom surface 3f of the ring 3, so that the leakage flow rate from the gap between the surfaces 17b and 3f is reduced to be as small as possible.
  • another washer 30 is disposed on the lower side of the bearing 22 in the axial direction.
  • the rotary unit 4 is pushed up to the upper side of the rotation axis Ax by the fluid force generating portion 28.
  • Such a configuration allows the rotary unit 4 to come in contact with the upper side of the casing 2 in the axial direction (i.e. the first casing 10), thus preventing the rotary unit 4 from reciprocating during rotation. Further, such a configuration prevents vibration or noise resulting from the reciprocating motion of the rotary unit 4.
  • a gap g between the top surface 5c of the base portion 5 and a bottom surface 10e of the first casing 10 can be more easily and precisely designated by the dimension d1 of the rotary unit 4 and the dimension d2 of the first casing 10.
  • the lower wall portion 17 is provided to slidably support the vanes 8 at the lower side in the axial direction, thus preventing the vanes 8 from moving to the lower side in the axial direction, and preventing vibration or noise due to the axial reciprocation motion of the vanes 8, and preventing the leakage flow rate from being increased, therefore preventing the pump efficiency from being reduced.
  • Such a configuration moves the vanes 8 to the upper side in the axial direction together with the rotary unit 4.
  • the slanting surfaces 28A which are inclined in the rotating direction RD of the rotary unit 4 are provided. Therefore, the fluid force generating portion 28 can be obtained using a relatively simple configuration. Especially, in the present embodiment, it is easy to increase the area of the end surface 18b of the skirt portion 18 having the slanting surfaces 28A at the lower side in the axial direction. Further, since it is easy to obtain a large gap between the second casing 23 and the skirt portion 18, desired fluid force can be more easily generated.
  • annular gaps 32 and 33 are provided between the skirt portion 18 and the second casing 23.
  • the gap 32 is provided between the outer circumferential surface 18c of the skirt portion 18 and the inner circumferential surface 23h of the annular wall 23a of the second casing 23, while the gap 33 is provided between the outer circumferential surface 23i of the partition wall 23g and the inner circumferential surface 18d of the skirt portion 18.
  • gaps (fine gaps) 32 and 33 are concentric with the rotation axis Ax, even when the rotary unit 4 moves to the upper side in the axial direction, the leakage flow rate of the working fluid between the lower side of the rotary unit 4 in the axial direction and the second casing 23 can be reduced.
  • the skirt portion 18 serves as a rotor constituting the motor 19.
  • the structures of the skirt portion 18 serving as the rotor and its surrounding parts e.g., by using the cylindrical gaps (fine gaps) 32 and 33 formed at the outside and the inside portion of the skirt portion 18 in the radial direction, the leakage flow rate can be efficiently reduced.
  • Figs. 6 to 12 are side views illustrating the modifications of slanting surfaces.
  • the drawings illustrate modifications wherein the slanting surfaces 28A serving as the fluid force generating portion 28 are provided on the end surface 18b of the skirt portion 18 of the rotary unit 4 provided on the lower side (lower sides in Figs. 6 to 12 ) in the axial direction.
  • the specifications (position, shape, angle, depth, width, pitch, curvature, etc.) of the slanting surfaces 28A can be appropriately changed.
  • the fluid force F of the working fluid acts on the slanting surfaces 28A to push the rotary unit 4 up to the upper side in the axial direction.
  • the rotary unit 4 is rotated while being pressed towards the thrust support unit 29 of the first casing 10.
  • the modifications achieve the same effect as in the first embodiment.
  • Figs. 13A and 13B are views illustrating another modification of slanting surfaces, in which Fig. 13A is a side view and Fig. 13B is a plan view seen from the arrow A shown in Fig. 13A .
  • Figs. 14 to 17 are side views illustrating other modifications of slanting surfaces.
  • Figs. 13A through 17 illustrate the modifications wherein the slanting surfaces 28A serving as the fluid force generating portion 28 are provided on the outer circumferential surface 18c of the skirt portion 18.
  • recessed portions 18e of a predetermined depth are provided in the outer circumferential surface 18c, and an end surface 18f of each recessed portion 18e provided on the upper side in the axial direction (the upper sides in Fig. 13A and Figs. 14 to 17 ) is formed as the slanting surface 28A.
  • the specifications (position, shape, angle, depth, width, pitch, curvature, etc.) of the slanting surfaces 28A can be appropriately changed.
  • the fluid force F of the working fluid acts on the slanting surfaces 28A to push the rotary unit 4 up to the upper side in the axial direction.
  • the rotary unit 4 is rotated while being pressed towards the thrust support unit 29 of the first casing 10.
  • Figs. 18A and 18B are views illustrating the modification of the fluid force generating portion, in which Fig. 18A is a side view and Fig. 18B is a plan view seen along the arrow B shown in Fig. 18A .
  • wings 28B serving as the fluid force generating portion 28 are provided at the bottom end of the skirt portion 18 of the rotary unit 4 placed at the lower side (the lower side in Fig. 18A ) in the axial direction.
  • Each wing 28B is of a flat plate shape which is inclined relative to the rotating direction RD of the rotary unit 4.
  • An elevation angle ⁇ is provided to each wing 28B to generate a predetermined lifting force by the counter flow of the working fluid generated as the rotary unit 4 rotates.
  • each wing 28B is inclined upward (toward the upper side in Fig. 18A ) from its front edge to rear edge when viewed along the rotating direction RD.
  • the fluid force F of the working fluid acts on the wings 28B to push up the rotary unit 4 to the upper side in the axial direction.
  • the rotary unit 4 is rotated while being pressed towards the thrust support unit 29 of the first casing 10.
  • Fig. 19 is a side view illustrating another modification of the fluid force generating portion.
  • a spiral groove 28C serving as the fluid force generating portion is provided on the outer circumferential surface 18c of the skirt portion 18 of the rotary unit 4.
  • the groove 28C is formed in such a way as to be inclined upwardly (toward the upper side in Fig. 19 ) from a trailing side 18T of the rotating skirt portion 18 to a leading side 18L.
  • the rotary unit 4 rotates in the rotating direction RD, the counter flow of working fluid in the groove 28C is guided towards the lower side in the axial direction.
  • Figs. 20A and 20B are views illustrating a casing (the second casing) included in a vane pump according to the second embodiment of the present invention, in which Fig. 20A is a plan view seen from the upper side in the axial direction, and Fig. 20B is a sectional view taken along the line XXb-XXb of Fig. 20A .
  • protrusions 28D are provided on a portion of the second casing 23 opposite to the rotary unit 4 in such a way as to protrude toward the rotary unit 4.
  • the second embodiment is different from the first embodiment in that the protrusions 28D are used as the fluid force generating portion 28 exerting the fluid force on the rotary unit 4 to push same towards the upper side in the axial direction. Except for the difference, the general configuration of the second embodiment remains the same as the first embodiment.
  • the protrusions 28D are provided on the bottom surface 23m of the recessed portion 23b of the second casing 23 to protrude towards the skirt portion 18 (rotary unit 4), i.e., towards the upper side in the axial direction (the upper side in Fig. 20A ). That is, the protrusions 28D are provided on the portion disposed at the lower side of the end surface 18b, which is provided at the lower side of the skirt portion 18 (rotary unit 4) in the axial direction.
  • the protrusions 28D are provided on a plurality of places along the circumferential direction of the rotation axis Ax (four places, each at the angular interval of 90 degrees in the present embodiment).
  • an annular space is formed between the end surface 18b of the skirt portion 18 and the bottom surface 23m of the recessed portion 23b to receive working fluid therein.
  • the working fluid is pulled to the rotating skirt portion 18 by the viscosity of the working fluid, and flows in the rotating direction RD of the rotary unit 4.
  • the protrusions 28D form narrow portions to the flow of the working fluid
  • the pressure of the working fluid is increased at a place provided with each protrusion 28D (i.e. the place from the narrowest portion to the edge of the protrusion 28D at the upstream side in the rotating direction RD).
  • fluid force F acts on the end surface 18b of the skirt portion 18 to push the rotary unit 4 toward the upper side in the axial direction.
  • each protrusion 28D is provided with a slanting surface 28Da, wherein each slanting surface 28Da is inclined upwards from a front edge 28DF to a rear edge 28DR thereof when viewed along the rotating direction RD. That is, when viewed along the rotating direction RD, the slanting surface 28Da is inclined upwards, i.e., from the second casing 23 side to the first casing 10 side.
  • the flow of the working fluid is angled to the upper side in the axial direction along the slanting surface 28Da, so that the fluid force F can more efficiently act.
  • the second embodiment achieves the same effect as in the first embodiment.
  • the protrusions 28D are provided on the second casing 23, so that the fluid force generating portion can be obtained in a relatively simple configuration.
  • Figs. 21 through 26 are sectional views illustrating second casings having slanting surfaces in accordance with the modifications, and are sectional views taken at the same position as the line XXb-XXb of Fig. 20 .
  • the drawings illustrate the modifications wherein the protrusions 28D serving as the fluid force generating portion 28 are provided on the recessed portion 23b of the second casing 23.
  • each protrusion 28D need not be a slanting surface but may rather be a horizontal surface.
  • the fluid force F of the working fluid contacting the protrusions 28D acts on the rotary unit 4 to push it up to the upper side in the axial direction.
  • the rotary unit 4 is rotated while being pressed towards the thrust support unit 29 of the first casing 10.
  • Figs. 27A and 27B are views illustrating a second casing included in a vane pump in accordance with the third embodiment of the present invention, in which Fig. 27A is a plan view of the second casing when it is seen from the upper side in the axial direction, and Fig. 27B is a sectional view taken along line XXVIIb-XXVIIb of Fig. 27A .
  • protrusions 28E are provided on the portion of the second casing 23 opposite to the rotary unit 4 in such a way as to protrude towards the rotary unit 4.
  • the third embodiment is different from the first embodiment in that the protrusions 28E are used as the fluid force generating portion 28 exerting the fluid force on the rotary unit 4 to push same towards the upper side in the axial direction. Except for the difference, the general configuration of the third embodiment remains the same as the first embodiment.
  • the protrusions 28E are provided on the protruding portion 23f of the second casing 23 to protrude towards the lower wall portion 17 (rotary unit 4), that is, the upper side in the axial direction (the upper side in Fig. 27B ).
  • the protrusions 28E are provided on a plurality of places along the circumferential direction of the rotation axis Ax (four places, each at the angular interval of 90 degrees in this embodiment).
  • an annular space is formed between the lower wall portion 17 and the protruding portion 23f to receive working fluid therein.
  • the working fluid in the annular space is pulled to the lower wall portion 17 which is rotated by the viscosity of the working fluid, and flows in the rotating direction RD of the rotary unit 4.
  • the protrusions 28E form narrow portions to the flow of the working fluid
  • the pressure of the working fluid is increased at a place provided with each protrusion 28E (i.e. at the place from the narrowest portion to the edge of the protrusions 28E at the upstream side in the rotating direction RD).
  • fluid force F acts on the lower wall portion 17, that is, the rotary unit 4 such that it is moved to the upper side in the axial direction.
  • each protrusion 28E is provided with a slanting surface 28Ea, wherein each slanting surface 28Ea is inclined upwards from a front edge 28EF to a rear edge 28ER thereof when viewed along the rotating direction RD. That is, when viewed along the rotating direction RD, the slanting surface 28Ea is inclined upwards, i.e., from the second casing 23 side to the first casing 10 side.
  • the flow of the working fluid is angled to the upper side in the axial direction along the slanting surface 28Ea, so that the fluid force F can more efficiently act.
  • the fluid force generating portion 28 is provided on the second casing 23.
  • the rotary unit 4 which is subjected to fluid force F acting towards the upper side in the axial direction by the fluid force generating portion 28 is rotated while being pressed towards the thrust support unit 29 of the first casing 10. Therefore, the third embodiment achieves the same effect as in the first and second embodiments.
  • the protrusions 28E are provided on the second casing 23, so that the fluid force generating portion can be obtained in a relatively simple construction.
  • Figs. 28 through 33 are sectional views illustrating second casings having slanting surfaces in accordance with the modifications, and are sectional views taken at the same position as line XXVIIb-XXVIIb of Fig. 27A .
  • the drawings illustrate the modifications wherein the protrusions 28E serving as the fluid force generating portion 28 are provided on the protruding portion 23f of the second casing 23.
  • the specifications (position, shape, angle, depth, width, pitch, curvature, etc.) of the protrusions 28E and the slanting surfaces 28Ea provided at the front side thereof when viewed along the rotating direction RD may be appropriately changed.
  • each protrusion 28E need not be a slanting surface but may rather be a horizontal surface.
  • the fluid force F of the working fluid contacting the protrusions 28E acts on the rotary unit 4 to push it up to the upper side in the axial direction.
  • the rotary unit 4 is rotated while being pressed towards the thrust support unit 29 of the first casing 10.
  • the present invention is not limited thereto and various changes and modifications may be made.
  • the detailed configuration of the rotary unit, ring, or casing of the vane pump is not limited to the above-mentioned embodiments.
  • the rotary unit may be pressed towards a side opposite to the side described in the embodiments by the fluid force generating portion. That is, the rotary unit may be pressed towards the casing located on the same side as the motor.
  • the fluid force generating portion may be provided on both of the rotary unit and the casing.
  • the skirt portion may not be installed steplessly to lower wall portion serving as the guide wall, as in the embodiments of the present invention.
  • a step may be provided between the skirt portion and a flange radially protruding outwardly from the guide wall and the base portion, or the skirt portion may protrude directly from the base portion.
  • each wing may be formed to have the shape of a general wing which is dull at its upstream side and is sharp at an edge of its downstream side.
  • the spiral projection may be used instead of the spiral groove.
  • the slanting surface or the spiral groove or projection may be discontinuously formed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP08022401A 2007-12-25 2008-12-23 Flügelzellenpumpe Withdrawn EP2075469A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007332179 2007-12-25
JP2008092263A JP4636108B2 (ja) 2007-12-25 2008-03-31 ベーンポンプ

Publications (1)

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EP2075469A2 true EP2075469A2 (de) 2009-07-01

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EP08022401A Withdrawn EP2075469A2 (de) 2007-12-25 2008-12-23 Flügelzellenpumpe

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US (1) US20090162232A1 (de)
EP (1) EP2075469A2 (de)
KR (1) KR20090069244A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011131598A3 (de) * 2010-04-22 2013-01-31 Robert Bosch Gmbh Flügelzellenpumpe
EP2146096A3 (de) * 2008-07-18 2015-01-14 Panasonic Corporation Flügelzellenpumpe
EP3957822A1 (de) * 2020-08-20 2022-02-23 GKN Sinter Metals Engineering GmbH Pumpenanordnung
EP3957823A1 (de) * 2020-08-20 2022-02-23 GKN Sinter Metals Engineering GmbH Pumpenanordnung

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6477783A (en) 1987-09-18 1989-03-23 Hitachi Ltd Closed type rotary compressor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6477783A (en) 1987-09-18 1989-03-23 Hitachi Ltd Closed type rotary compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2146096A3 (de) * 2008-07-18 2015-01-14 Panasonic Corporation Flügelzellenpumpe
WO2011131598A3 (de) * 2010-04-22 2013-01-31 Robert Bosch Gmbh Flügelzellenpumpe
CN103038452A (zh) * 2010-04-22 2013-04-10 罗伯特·博世有限公司 叶片泵
EP3957822A1 (de) * 2020-08-20 2022-02-23 GKN Sinter Metals Engineering GmbH Pumpenanordnung
EP3957823A1 (de) * 2020-08-20 2022-02-23 GKN Sinter Metals Engineering GmbH Pumpenanordnung
WO2022038137A1 (de) * 2020-08-20 2022-02-24 Gkn Sinter Metals Engineering Gmbh Pumpenanordnung
WO2022038136A1 (de) * 2020-08-20 2022-02-24 Gkn Sinter Metals Engineering Gmbh Pumpenanordnung

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KR20090069244A (ko) 2009-06-30
US20090162232A1 (en) 2009-06-25

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