US3626265A - Vane pump or motor - Google Patents

Vane pump or motor Download PDF

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US3626265A
US3626265A US858411A US3626265DA US3626265A US 3626265 A US3626265 A US 3626265A US 858411 A US858411 A US 858411A US 3626265D A US3626265D A US 3626265DA US 3626265 A US3626265 A US 3626265A
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disc
vane
grooves
wall part
housing
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US858411A
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Hillebrand Johannes J Kraakman
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US Philips Corp
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US Philips Corp
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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
    • 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
    • F04C2/3446—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 more than one line or surface

Definitions

  • This invention relates generally to a vane pump or vane motor. Specifically it comprises a cylindrical, rotatable disc accommodated in a housing surrounding the disc.
  • the disc is provided with the disc a number of radial grooves which are regularly distributed about its circumference and extend in the axial direction.
  • the grooves support herein radially movable vanes which, have their ends, remote from the disc, guided by the inner wall of the housing.
  • the housing is provided with at least one pair of inlet and outlet apertures associated with each other for the passage of a fluid.
  • the part of the inner wall of the. housing situated between each associated pair of inlet and outlet apertures is cylindrical and has a larger diameter than the disc, and forms a boundary for a working space.
  • a vane pump or motor of the above-described type is known from Dutch Pat. specification No. 102,292.
  • the grooves are arranged at such regular distances from each other that the distance between the adjacent vanes, measured on a circle the diameter of which corresponds to that of the cylindrical wall part of the housing which bounds a working space, is substantially equal to the dimension of said wall part viewed in the direction of its circumference.
  • only one vane produces a seal between the inlet and the outlet. At the instant this one vane leaves the relative cylindrical wall part, a subsequent vane will contact said wall part. The result of this is that the differential pressure across the first vane must be immediately assumed by the next vane.
  • the present invention is based on the recognition of the fact that such a disturbance is caused as a result of a vane being tilted backwards" in its groove due to the friction contact with the inner wall of the housing, viewed in the direction of revolution of the disc when there is no pressure difference across it.
  • a vane contacts the wall part which forms a boundary of a working space, and the preceding vane leaves said wall part, the differential pressure will be across the vane which has just contacted said wall part.
  • the vane flips in its groove so that, viewed in the direction of revolution of the disc, itassumes a tilted forward" position in the groove. During; this flipping the seal between'the inlet and the outlet is momentarily broken thereby resulting. in the above-mentioned disturbance.
  • the vane pump or motor according to the invention is characterized in that the grooves in the disc are regularlydistributed about its circumference in such a. manner that the angle enclosed by radial planes passing through the center of two adjacent grooves and the axis of the disc is at most equal to half of the angle enclosed by two planes each passing through the axis of the disc and one of which passes through the end of the wall part of the housing bounding a working space adjacent to the inlet aperture and the other passes through the end of said wall part adjacent the outlet aperture.
  • each cylindrical wall part which bounds aworking space is provided, at its ends adjacent the inlet and outlet apertures, with equal circumferentially extending discharge-grooves.
  • the grooves extend over a distance equal tothe arc lengthtof the cylindrical wall part diminished by twice the distance between the vanes measured on .the same diameter as that of therelative wall part in such manner that the resistance to flow across a vane which is incontact withia track of the wall part, in which the discharge grooves are situated, is substantiallyequal to .half the resistance to flow across a vane which is in contact with the track of thewall part in which no discharge grooves are situated.
  • FIGS. 1 and 2. show two cross-sectional views at mutually right angles of a vane motor having two working spaces
  • FIG. 3 shows a workingspace of the motor shown in FIG. I and FIG. 2 onan enlarged scale.
  • reference numeral 1 denotes a cylindrical disc. This disc is provided on its circumference with anumber of regularly spaced radial, grooves 2. The grooves 2 have radially movable vanes 3.
  • the disc 1 is surrounded by a housing 4 having a pair of associated inlet and outletports 5 and 6 and a pair of associated inlet and outlet ports 7 and 8.
  • the housing 4 is closed at its ends by covers 9 and 10 in which the shaft ll of the disc is joumaled in a sealing manner.
  • the inner wall of the housing 4 surrounds the disc in such a manner that together with the flanges 12 and 13 arranged on the disc two working spaces 14 and 15 are formed.
  • the parts 16 and 17 of the inner wall of the housing 4 between the inlet ports Sand 7 and the associated outlet ports 6 and 8 are concentric with the disc but situated at a larger diameter while the parts 18 and 19 of the inner wall of the housing situated between the outlet ports 8 and 6 andthe inlet ports 5 and 7 cooperate, in a sealing manner with the disc I.
  • each angle 11: enclosed by two radial surfaces passing through the axis and through the center of two adjacent grooves is smaller than half of the angle il enclosed by a plane through the axis and through the end of the wall parts t 16 and 17,, respectively, which adjoins the inlet ports 5 and 7, respectively, and a plane through the axis and through. theend of the wall parts 16. and 17, respectively, which adjoins the outlet ports 6 and 8, respectively.
  • At least two vanes are always in contact with each of the wall parts 16 and 17 so that the sealing between theinlet and outlet is always ensured by at least two vanes.
  • FIG. 3 shows the working space 14 on an enlarged scale. From this Figure is appears that when the vane 20 leaves the wall part 16, the vane 22 already contacts the wall part 16. In the inlet 5 and in the part 23 of the working space substantially the same high pressure prevails. So no differential pressure prevails across the vane 22 and as a result of the friction between said vane and the wall 16 said vanewill assume a tilted backwards position (viewed in the direction of revolution of the disc 1). In the part 24 of the working space the pressure will have dropped due to leakage so that a differential pressure does occur across the vane 21 so that said vane (see drawing) is tilted forwards. A low pressure prevails in the outlet 6 so that the vane 20 is also tilted forwards.
  • the wall part 16 at the area of its communication with the inlet and outlet, is provided with a number of discharge grooves 26 and 27 extending in the circumferential direction.
  • the length of said discharge grooves is equal to the length of the wall part 16 diminished by the distance between the vanes 20 and 22 so that when the vane 22 contacts the wall part 16, the vane 20 just arrives in the track provided with discharge grooves 27 while at the instant at which the vane 20 leaves the wall part 16, the vane 22 just passes the end of the discharge groove 26.
  • the discharge grooves are constructed so that the resistance to flow across each of the vanes 20 and 22, when these are in the position shown in F 10.
  • the discharge grooves 26 and 27 also provide that the expansion of the liquid from the space 24 (in a pump contraction of liquid) in the outlet occurs much more gradually, which is also favorable for a number of revolutions which is as constant as possible.
  • the invention can be applied to vane motors and pumps having any number of working spaces, the only requirement being that at least two sealing vanes be present between an inlet and an associated outlet.
  • a vane pump or motor comprising a cylindrical disc rotatably arranged in a housing surrounding it, said disc having a plurality of radial grooves extending in the axial direction and regularly distributed on its circumference, said grooves being provided with radially movable vanes which, with their ends remote from the disc are guided by the inner wall of the housing, said vanes being arranged for pivotal movement within said grooves, said housing comprising at least one pair of associated inlet and outlet apertures for liquid, and means producing pressure difference across said vanes, the part of the inner wall of the housing situated between each pair of associated inlet and outlet apertures being cylindrical and having a larger diameter than the disc, said wall part also forming a boundary for a working space, said grooves in the disc being regularly distributed about the circumference thereof in such manner that the angle enclosed by radial planes passing through the center of two adjacent grooves and the axis of the disc is equal to no greater than half of the angle enclosed by two planes each passing through the axis of the disc and one of which passes

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A vane pump or motor having a rotatable cylindrical disc incorporated in a housing. The disc has radial grooves provided with radially movable vanes. The housing has at least one pair of associated inlet and outlet apertures, and the part of the inner wall of the housing situated between said apertures is cylindrical and has a larger diameter than the disc. The inner wall between the apertures also forms a boundary for a working space. The number of vanes in a disc is relatively large so that at least two vanes are present between an inlet aperture and an associated outlet aperture.

Description

United States Patent [72] Inventor Hillebrand Johannes Josephus Kraaltman Emmasingel, Eindhoven, Netherlands [21] Appl. No. 858,411 [22] Filed Sept. 16, 1969 [45] Patented Dec. 7, 1971 [73] Assignee U.S. Philips (Iorporation New York, N .Y. [32] Priority Sept. 18, 1968 [3 3] Netherlands [31] 6813309 [54] VANE PUMP 0R MOTOR 1 Claim, 3 Drawing Figs.
[52] U.S. Cl 418/266 [51] Int. Cl Flllc' 1/00, F03c 3/00, F040 H00 [50] Field of Search 418/241, 15, 138,266, 157,268; 103/136 R;9l/124, 121, 135
[56] References Cited UNlTED STATES PATENTS 2,371,081 3/1945 Tucker et a1 418/268 X Primary Examiner-Carlton R. Croyle Assistant Examiner-R. E. Gluck Al!0rney-Frank R. Trifari ABSTRACT: A vane pump or motor having a rotatable cylindrical disc incorporated in a housing. The disc has radial grooves provided with radially movable vanes. The housing has at least one pair of associated inlet and outlet apertures, and the part of the inner wall of the housing situated between said apertures is cylindrical and has a larger diameter than the disc. The inner wall between the apertures also forms a boundary for a working space. The number of vanes in a disc is relatively large so that at least two vanes are present between an inlet aperture and an associated outlet aperture.
PAIENTEDHEB 71971 $626,265
SHEET 1 UF 2 VANE PUMP R MOTOR This invention relates generally to a vane pump or vane motor. Specifically it comprises a cylindrical, rotatable disc accommodated in a housing surrounding the disc. The disc is provided with the disc a number of radial grooves which are regularly distributed about its circumference and extend in the axial direction. The grooves support herein radially movable vanes which, have their ends, remote from the disc, guided by the inner wall of the housing. The housing is provided with at least one pair of inlet and outlet apertures associated with each other for the passage of a fluid. The part of the inner wall of the. housing situated between each associated pair of inlet and outlet apertures is cylindrical and has a larger diameter than the disc, and forms a boundary for a working space.
A vane pump or motor of the above-described type is known from Dutch Pat. specification No. 102,292. In this known vane pump or motor the grooves are arranged at such regular distances from each other that the distance between the adjacent vanes, measured on a circle the diameter of which corresponds to that of the cylindrical wall part of the housing which bounds a working space, is substantially equal to the dimension of said wall part viewed in the direction of its circumference. In such a pump or motor only one vane produces a seal between the inlet and the outlet. At the instant this one vane leaves the relative cylindrical wall part, a subsequent vane will contact said wall part. The result of this is that the differential pressure across the first vane must be immediately assumed by the next vane. It has been found that this sudden taking over of the full differential pressure-of one vane by the next produces certain disturbances in the operation of the pump or motor. In a motor, it is a disturbance in the number of revolutions and in a pump a disturbance in the supply of liquid. In case where a high degree of accuracy in the number of revolutions (for example, in driving precision machine tools) and in the supply of liquid (uniform supply without pressure ripples) is required, these disturbances are highly objectionable.
The present invention is based on the recognition of the fact that such a disturbance is caused as a result of a vane being tilted backwards" in its groove due to the friction contact with the inner wall of the housing, viewed in the direction of revolution of the disc when there is no pressure difference across it. When such a vane contacts the wall part which forms a boundary of a working space, and the preceding vane leaves said wall part, the differential pressure will be across the vane which has just contacted said wall part. As a result of the prevailing pressure differential, the vane flips in its groove so that, viewed in the direction of revolution of the disc, itassumes a tilted forward" position in the groove. During; this flipping the seal between'the inlet and the outlet is momentarily broken thereby resulting. in the above-mentioned disturbance.
It is accordingly an object of the invention to provide avane pump or motor in which the disturbances of prior devices is fully avoided.
The vane pump or motor according to the invention is characterized in that the grooves in the disc are regularlydistributed about its circumference in such a. manner that the angle enclosed by radial planes passing through the center of two adjacent grooves and the axis of the disc is at most equal to half of the angle enclosed by two planes each passing through the axis of the disc and one of which passes through the end of the wall part of the housing bounding a working space adjacent to the inlet aperture and the other passes through the end of said wall part adjacent the outlet aperture.
In this manner a motor or pump is obtained in which two vanes will always contact the wall part of the housing which forms a boundary for the working space so that the seal between the inlet and the outlet is always ensured by two vanes arranged in series. The result of this is that the flipping over of a vane occurs when the succeeding vane in the direction of drum rotation has already flipped over so that no bypass situation or open communication between inlet and outlet, will occur. It has been found that the disturbance in the number of revolutions and the supply of liquid, found in prior devices, is avoided in the motor or pump of the present invention.
Since twosealing vanes are always present between an inlet and an associated outlet aperture, the contraction and expansion of the liquid in.the parts of the working space communicating with the inlet and outlet, respectively, also becomes much more gradual. It will be obvious that this also contributes to a disturbance-free running of the motor and the pump, respectively.
In a further favorable embodiment,,each cylindrical wall part which bounds aworking space is provided, at its ends adjacent the inlet and outlet apertures, with equal circumferentially extending discharge-grooves. The grooves extend over a distance equal tothe arc lengthtof the cylindrical wall part diminished by twice the distance between the vanes measured on .the same diameter as that of therelative wall part in such manner that the resistance to flow across a vane which is incontact withia track of the wall part, in which the discharge grooves are situated, is substantiallyequal to .half the resistance to flow across a vane which is in contact with the track of thewall part in which no discharge grooves are situated. As aresult of this the contraction and expansion, respectively, of liquid in the parts of the working space which communicate with the inlet and outlet occurs even more gradually I while the total resistance to flowbetween the inlet and outlet is always the same so that avoidance of the objectionable disturbances is further insured.
In order that the invention may be readily carried into effect one embodiment thereof will now be described in greater detail, byway of example, with reference to the accompanying drawings, in which FIGS. 1 and 2.show two cross-sectional views at mutually right angles of a vane motor having two working spaces, and
FIG. 3 shows a workingspace of the motor shown in FIG. I and FIG. 2 onan enlarged scale.
In FIGS. land 2, reference numeral 1 denotes a cylindrical disc. This disc is provided on its circumference with anumber of regularly spaced radial, grooves 2. The grooves 2 have radially movable vanes 3. The disc 1 is surrounded by a housing 4 having a pair of associated inlet and outletports 5 and 6 and a pair of associated inlet and outlet ports 7 and 8. The housing 4 is closed at its ends by covers 9 and 10 in which the shaft ll of the disc is joumaled in a sealing manner.
The inner wall of the housing 4 surrounds the disc in such a manner that together with the flanges 12 and 13 arranged on the disc two working spaces 14 and 15 are formed. The parts 16 and 17 of the inner wall of the housing 4 between the inlet ports Sand 7 and the associated outlet ports 6 and 8 are concentric with the disc but situated at a larger diameter while the parts 18 and 19 of the inner wall of the housing situated between the outlet ports 8 and 6 andthe inlet ports 5 and 7 cooperate, in a sealing manner with the disc I.
The number of grooves 2 and vanes 3 movable therein is chosen to. be such that each angle 11: enclosed by two radial surfaces passing through the axis and through the center of two adjacent grooves is smaller than half of the angle il enclosed by a plane through the axis and through the end of the wall parts t 16 and 17,, respectively, which adjoins the inlet ports 5 and 7, respectively, and a plane through the axis and through. theend of the wall parts 16. and 17, respectively, which adjoins the outlet ports 6 and 8, respectively.
In this manner at least two vanes are always in contact with each of the wall parts 16 and 17 so that the sealing between theinlet and outlet is always ensured by at least two vanes.
FIG. 3 shows the working space 14 on an enlarged scale. From this Figure is appears that when the vane 20 leaves the wall part 16, the vane 22 already contacts the wall part 16. In the inlet 5 and in the part 23 of the working space substantially the same high pressure prevails. So no differential pressure prevails across the vane 22 and as a result of the friction between said vane and the wall 16 said vanewill assume a tilted backwards position (viewed in the direction of revolution of the disc 1). In the part 24 of the working space the pressure will have dropped due to leakage so that a differential pressure does occur across the vane 21 so that said vane (see drawing) is tilted forwards. A low pressure prevails in the outlet 6 so that the vane 20 is also tilted forwards.
When the disc 1 is further rotated, the space 24 comes in open communication with the outlet 6. The vane 21 will remain in its forward-tilted position as shown. The pressure in the space 23 will drop, the vane 22 flipping from its backwards-tilted position to its'forward'tilted position. During this flipping over a considerable leak occurs for a moment across the vane 22 but since the vane 21 does not flip and remains in the sealing position, no liquid can flow from the high-pressure inlet to the low-pressure outlet. Therefore, no bypass situation will occur each time a vane flips over, in other words open communication between the inlet is avoided and the outlet. This results in a vane motor which operates without disturbances (very constant number of revolutions). When used in a vane pump, a uniform supply of liquid without, pressure ripples, is produced.
In order to insure that the overall resistance to flow between the inlet 5 and the outlet 6 is always the same, the wall part 16, at the area of its communication with the inlet and outlet, is provided with a number of discharge grooves 26 and 27 extending in the circumferential direction. The length of said discharge grooves is equal to the length of the wall part 16 diminished by the distance between the vanes 20 and 22 so that when the vane 22 contacts the wall part 16, the vane 20 just arrives in the track provided with discharge grooves 27 while at the instant at which the vane 20 leaves the wall part 16, the vane 22 just passes the end of the discharge groove 26. The discharge grooves are constructed so that the resistance to flow across each of the vanes 20 and 22, when these are in the position shown in F 10. 3, is exactly half of the resistance to flow across the vane 21. In this manner the overall resistance to flow between the inlet and outlet will always be the same. Upon variation of this resistance to flow the number of revolutions would also vary. This is fully avoided by the existence of discharge grooves 26 and 27.
The discharge grooves 26 and 27 also provide that the expansion of the liquid from the space 24 (in a pump contraction of liquid) in the outlet occurs much more gradually, which is also favorable for a number of revolutions which is as constant as possible.
Although the drawing shows by way of example a vane motor, it will be obvious that the invention can be applied with the same advantages to a vane pump.
Furthermore it is to be noted that the invention can be applied to vane motors and pumps having any number of working spaces, the only requirement being that at least two sealing vanes be present between an inlet and an associated outlet.
What is claimed is:
l. A vane pump or motor comprising a cylindrical disc rotatably arranged in a housing surrounding it, said disc having a plurality of radial grooves extending in the axial direction and regularly distributed on its circumference, said grooves being provided with radially movable vanes which, with their ends remote from the disc are guided by the inner wall of the housing, said vanes being arranged for pivotal movement within said grooves, said housing comprising at least one pair of associated inlet and outlet apertures for liquid, and means producing pressure difference across said vanes, the part of the inner wall of the housing situated between each pair of associated inlet and outlet apertures being cylindrical and having a larger diameter than the disc, said wall part also forming a boundary for a working space, said grooves in the disc being regularly distributed about the circumference thereof in such manner that the angle enclosed by radial planes passing through the center of two adjacent grooves and the axis of the disc is equal to no greater than half of the angle enclosed by two planes each passing through the axis of the disc and one of which passes through the end of the wall part of the housing forming the boundary of the working space which communicates within the inlet aperture and the other passes through the end of said wall part which communicates with the outlet aperture, equal discharge grooves provided on each cylindrical wall part which forms a boundary for a working space communicating at its ends with inlet and outlet apertures, said discharge grooves extending in the circumferential direction over a distance equal to the arc length of the cylindrical wall part diminished by twice the distance between the vanes measured on the same diameter as that of the relative wall part, said grooves being arranged so that when a vane passes thereacross the resistance to flow across said vane is substantially equal to half the resistance to flow across a vane which contacts the track of the wall part in which no discharge grooves are arranged.

Claims (1)

1. A vane pump or motor comprising a cylindrical disc rotatably arranged in a housing surrounding it, said disc having a plurality of radial grooves extending in the axial direction and regularly distributed on its circumference, said grooves being provided with radially movable vanes which, with their ends remote from the disc are guided by the inner wall of the housing, said vanes being arranged for pivotal movement within said grooves, said housing comprising at least one pair of associated inlet and outlet apertures for liquid, and means producing pressure difference across said vanes, the part of the inner wall of the housing situated between each pair of associated inlet and outlet apertures being cylindrical and having a larger diameter than the disc, said wall part also forming a boundary for a working space, said grooves in the disc being regularly distributed about the circumference thereof in such manner that the angle enclosed by radial planes passing through the center of two adjacent grooves and the axis of the disc is equal to no greater than half of the angle enclosed by two planes each passing through the axis of the disc and one of which passes through the end of the wall part of the housing forming the boundary of the working space which communicates within the inlet aperture and the other passes through the end of said wall part which communicates with the outlet aperture, equal discharge grooves provided on each cylindrical wall part which forms a boundary for a working space communicating at its ends with inlet and outlet apertures, said discharge grooves extending in the circumferential direction over a distance equal to the arc length of the cylindrical wall part diminished by twice the distance between the vanes measured on the same diameter as that of the relative wall part, said grooves being arranged so that when a vane passes thereacross the resistance to flow across said vane is substantially equal to half the resistance to flow across a vane which contacts the track of the wall part in which no discharge grooves are arranged.
US858411A 1968-09-18 1969-09-16 Vane pump or motor Expired - Lifetime US3626265A (en)

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US20040244765A1 (en) * 2003-06-06 2004-12-09 Elmer Brent Warren High Efficiency rotary piston combustion engine
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US9476422B2 (en) 2012-05-15 2016-10-25 Delaware Capital Formation, Inc. Sliding vane positive displacement pump having a fixed disc configuration to reduce slip paths
US20180010612A1 (en) * 2016-07-08 2018-01-11 Fenwal, Inc. Flexible Impeller Pumps And Disposable Fluid Flow Circuits Incorporating Such Pumps
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CN111998068A (en) * 2020-08-09 2020-11-27 肇庆高新区伙伴汽车技术有限公司 Sliding vane type hydraulic driver
CN112012927A (en) * 2020-08-09 2020-12-01 肇庆高新区伙伴汽车技术有限公司 Fuel cell baffle type sliding vane air compressor and device thereof
US10876318B2 (en) 2013-08-30 2020-12-29 Hayward Industries, Inc. Swimming pool cleaner
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JP4858262B2 (en) * 2007-03-27 2012-01-18 パナソニック電工株式会社 Vane pump
CN101847917B (en) * 2010-03-29 2011-12-21 燕山大学 Axially-rotating equal-width curve double-stator multi-speed motor
CN107387404A (en) * 2017-09-09 2017-11-24 湖南机油泵股份有限公司 A kind of high-efficiency blade pump

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US582280A (en) * 1897-05-11 Rotary fluid-meter
GB398141A (en) * 1932-06-11 1933-09-07 Schweizerische Lokomotiv Improvements in rotary engines
US2280272A (en) * 1940-05-13 1942-04-21 Citles Service Oil Company Fluid pump
US2371081A (en) * 1941-02-06 1945-03-06 Hydraulic Dev Corp Inc Vane pump
US2499763A (en) * 1945-07-27 1950-03-07 William T Livermore Loose slipper rotary pump
US3014431A (en) * 1958-08-15 1961-12-26 Shell Oil Co Sliding vane pump
US3171587A (en) * 1961-01-21 1965-03-02 Nsu Motorenwerke Ag Sealing structures
US3180564A (en) * 1962-07-02 1965-04-27 Goetzewerke Radial seal for rotary piston engines
US3418939A (en) * 1966-06-30 1968-12-31 Kopp Jean Ernst Rotary pumps

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US582280A (en) * 1897-05-11 Rotary fluid-meter
GB398141A (en) * 1932-06-11 1933-09-07 Schweizerische Lokomotiv Improvements in rotary engines
US2280272A (en) * 1940-05-13 1942-04-21 Citles Service Oil Company Fluid pump
US2371081A (en) * 1941-02-06 1945-03-06 Hydraulic Dev Corp Inc Vane pump
US2499763A (en) * 1945-07-27 1950-03-07 William T Livermore Loose slipper rotary pump
US3014431A (en) * 1958-08-15 1961-12-26 Shell Oil Co Sliding vane pump
US3171587A (en) * 1961-01-21 1965-03-02 Nsu Motorenwerke Ag Sealing structures
US3180564A (en) * 1962-07-02 1965-04-27 Goetzewerke Radial seal for rotary piston engines
US3418939A (en) * 1966-06-30 1968-12-31 Kopp Jean Ernst Rotary pumps

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3978570A (en) * 1973-08-17 1976-09-07 Itt Industries, Inc. Method of manufacturing a rotor for vane type engines
AU778515B2 (en) * 1999-10-12 2004-12-09 Hayward Industries, Inc. Turbine-driven automatic swimming pool cleaners
US6292970B1 (en) * 1999-10-12 2001-09-25 Poolvergnuegen Turbine-driven automatic swimming pool cleaners
EP1232314A1 (en) * 1999-10-12 2002-08-21 Poolvergnuegen Turbine-driven automatic swimming pool cleaners
EP1232314A4 (en) * 1999-10-12 2005-02-02 Poolvergnuegen Turbine-driven automatic swimming pool cleaners
US6439868B1 (en) * 2000-12-15 2002-08-27 Constantin Tomoiu Rotary engine
US20040244765A1 (en) * 2003-06-06 2004-12-09 Elmer Brent Warren High Efficiency rotary piston combustion engine
US6978758B2 (en) 2003-06-06 2005-12-27 Brent Warren Elmer High Efficiency rotary piston combustion engine
US20070266521A1 (en) * 2006-05-18 2007-11-22 Seagate Technology Llc Vortex-flow vacuum suction nozzle
US9357892B2 (en) * 2006-05-18 2016-06-07 Seagate Technology Llc Vortex-flow vacuum suction nozzle
US20110299359A1 (en) * 2009-02-09 2011-12-08 Christopher John Brown Distributive and dispersive mixing apparatus of the cddm type, and its use
WO2013095156A1 (en) * 2011-12-19 2013-06-27 Tocircle Industries As Rotary machine
EA027240B1 (en) * 2011-12-19 2017-07-31 Тусекл Индастриз Ас Rotary machine
US9376914B2 (en) 2011-12-19 2016-06-28 Tocircle Industries As Rotary machine
US9476422B2 (en) 2012-05-15 2016-10-25 Delaware Capital Formation, Inc. Sliding vane positive displacement pump having a fixed disc configuration to reduce slip paths
US12018510B2 (en) 2013-08-30 2024-06-25 Hayward Industries, Inc. Swimming pool cleaner
US10947750B2 (en) 2013-08-30 2021-03-16 Hayward Industries, Inc. Swimming pool cleaner
US10876318B2 (en) 2013-08-30 2020-12-29 Hayward Industries, Inc. Swimming pool cleaner
CN105508240A (en) * 2016-01-15 2016-04-20 托肯恒山科技（广州）有限公司 Anti-cavitation vane pump
US20180010612A1 (en) * 2016-07-08 2018-01-11 Fenwal, Inc. Flexible Impeller Pumps And Disposable Fluid Flow Circuits Incorporating Such Pumps
US10865805B2 (en) * 2016-07-08 2020-12-15 Fenwal, Inc. Flexible impeller pumps and disposable fluid flow circuits incorporating such pumps
US20210045979A1 (en) * 2019-06-28 2021-02-18 The Procter & Gamble Company Method of making a clear personal care comprising microcapsules
US11896689B2 (en) * 2019-06-28 2024-02-13 The Procter & Gamble Company Method of making a clear personal care comprising microcapsules
CN110578651A (en) * 2019-09-16 2019-12-17 杨甫在 one-way hydraulic motor
CN111946611A (en) * 2020-08-09 2020-11-17 肇庆高新区伙伴汽车技术有限公司 Baffle type slide machine
CN112012927A (en) * 2020-08-09 2020-12-01 肇庆高新区伙伴汽车技术有限公司 Fuel cell baffle type sliding vane air compressor and device thereof
CN111998068A (en) * 2020-08-09 2020-11-27 肇庆高新区伙伴汽车技术有限公司 Sliding vane type hydraulic driver
CN111981122A (en) * 2020-08-09 2020-11-24 肇庆高新区伙伴汽车技术有限公司 Automatic transmission automobile without clutch gearbox
US12053130B2 (en) 2021-02-12 2024-08-06 The Procter & Gamble Company Container containing a shampoo composition with an aesthetic design formed by bubbles

Also Published As

Publication number Publication date
CH510817A (en) 1971-07-31
DE1946272A1 (en) 1970-03-26
GB1287440A (en) 1972-08-31
JPS501921B1 (en) 1975-01-22
SE354688B (en) 1973-03-19
NL6813309A (en) 1970-03-20
FR2018349A1 (en) 1970-05-29

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