US20080219875A1 - Magnetic drive vane pump - Google Patents
Magnetic drive vane pump Download PDFInfo
- Publication number
- US20080219875A1 US20080219875A1 US12/073,303 US7330308A US2008219875A1 US 20080219875 A1 US20080219875 A1 US 20080219875A1 US 7330308 A US7330308 A US 7330308A US 2008219875 A1 US2008219875 A1 US 2008219875A1
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- United States
- Prior art keywords
- rotor
- magnet
- pump cavity
- pump
- casing
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- Abandoned
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Classifications
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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
- 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
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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
- F04C2/3441—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
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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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/008—Prime movers
-
- 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
- F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
- F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
Definitions
- the present invention is directed to a magnetic drive vane pump.
- Vane pumps are widely known in the art, for example, as disclosed in Japanese patent publication No. 53-2704 A.
- the vane pump includes a casing with a pump cavity and a rotor rotatable about an eccentric axis within the pump cavity.
- the rotor carries a plurality of vanes which moves radially so as to have their outer ends kept in sealed contact with an interior wall of the pump cavity as the rotor rotates, thereby drawing a fluid into the pump cavity, compressing and expelling it out of the pump cavity.
- the rotor is coupled to an external motor to be driven thereby to rotate.
- the rotor is provided with a shaft which extends outwardly of the casing for coupling with the motor. Therefore, a sealing is between the shaft and the casing.
- the shaft is a constantly moving part, there is always a problem that the sealing may become deteriorated during an extended period of use to result in an unintended lead of the fluid.
- the vane pump in accordance with the present invention includes a casing with a pump cavity, an inlet for introducing a fluid into the pump cavity, and an outlet for discharging the fluid out of the pump cavity.
- a rotor is disposed within the pump cavity to be rotatable about an eccentric axis with respect to the pump cavity.
- a plurality of vanes are carried on the rotor and are radially movable so as to be kept into sealed contact with an interior wall of the pump cavity as the rotor is driven to rotate for drawing the fluid into the pump cavity and expelling it out of the pump cavity.
- the rotor is configured to have a rotor magnet which is magnetically coupled to a stator magnet mounted on the casing outwardly of the pump cavity for driving the rotor.
- the feature of the present invention resides in that the rotor magnet is configured to have its major portion disposed in an overlapping relation with the stator magnet.
- the rotor magnet can be mechanically isolated from the stator magnet disposed outside of the casing to establish a sealless coupling therebetween for making the pump leakage free, yet requiring only a minimum thickness of the pump in the axial direction thereof.
- the rotor magnet is disposed radially outwardly of the stator magnet so that the stator magnet can be arranged within a radial dimension of the stator, which assures to give a compact structure to the pump with respect to the radial direction.
- stator magnet is configured to have its axial center offset from an axial center of the rotor magnet so as to be disposed further away from the rotor than said rotor magnet with respect to the eccentric axis.
- the rotor magnet is preferred to be fitted around a shaft extending axially from a center of the casing with a vibration absorbing member interposed therebetween.
- the vibration absorbing member can well absorb radial vibrations possibly caused by an eccentric rotary motion of the rotor, thereby assuring a smooth and silent rotary motion.
- each of the vanes which are slidable fitted respectively in radial grooves in the rotor, is configured to be movable only radially without being caused to fluctuate in the axial direction.
- each vane is formed on its opposite sides respectively with ribs which engage into guide grooves formed in opposite faces of the rotor defining the radial groove therebetween.
- FIG. 1 is an exploded perspective view of a vane pump in accordance with a first embodiment of the present invention
- FIG. 2 is a horizontal section of the above vane pump
- FIG. 3 is a cross-section taken along line X-X of FIG. 2 ;
- FIG. 4 is a cross section taken along line Y-Y of FIG. 2 ;
- FIG. 5 is an exploded perspective view of a portion of the above vane pump
- FIG. 6 is a horizontal section of a vane pump in accordance with a second embodiment of the present invention.
- FIG. 7 is a cross section taken along line 7 - 7 of FIG. 6 ;
- FIG. 8 is a horizontal section of a vane pump in accordance with a third embodiment of the present invention.
- FIG. 9 is a cross-section taken along line 9 - 9 of FIG. 8 .
- the pump includes a casing 10 formed in its interior with a cylindrical pump cavity 12 which accommodates therein a rotor 40 having an eccentric axis offset from an axis of the pump cavity 12 .
- the casing 10 is composed of a lower half 20 and an upper half 30 which are secured to each other with a sealing ring 14 held therebetween.
- the lower and upper halves 20 and 30 are respectively formed with a lower recess 21 and an upper recess 31 which are cooperative to define the pump cavity 12 . As seen in FIGS.
- the lower half 20 is formed to have a center stud 22 anchoring a shaft 23 , and an annular projection 26 between the center stud 22 and a peripheral wall 28 .
- the shaft 23 projects from the center stud 22 into a center concavity 29 of the lower half 20 to define the eccentric axis, and is surrounded by a bearing sleeve 24 .
- a ring 32 is fitted inside of the upper half 30 to extend around the periphery of the upper recess 31 with its one axial end resting on the peripheral wall 28 of the lower half 20 .
- the upper half 30 is formed with an inlet 34 for introducing a fluid into the pump cavity 12 through a port 35 in the ring 32 and an outlet 36 for expelling the fluid out of the pump cavity through a port 37 of the ring 32 .
- the rotor 40 is shaped into a disc disposed within the upper recess 21 and carries a plurality of vanes 50 which are slidably received respectively in circumferentially spaced radial slits 42 .
- each of the vanes 50 is shifted radially outwardly by a centrifugal force to have its outer end in sealing contact with the inside of the ring 32 , thereby forming a displacement chamber confined between the adjacent vanes and between the ring 32 and the rotor.
- the displacement chamber undergoes expansion and contraction while the rotor 40 rotates about the eccentric axis, thereby drawing the fluid into and expelling it out of the pump cavity 12 .
- the rotor 40 carries a rotor magnet 60 which is magnetically coupled to a stator magnet 70 disposed outside of the casing 10 so as to be driven thereby to rotate.
- the rotor magnet 60 is a permanent magnet which is integrated with the rotor 40 to form a unitary structure.
- the rotor magnet 60 is shaped to have a thin base 62 secured on one axial end face of the rotor 40 , a hub 64 projecting axially from the center of the base 62 , and an outer ring 67 projecting axially from the periphery of the base 62 .
- the hub 64 is received into the center concavity 29 in an overlapping relation with the stator magnet 70 with respect to the radial direction about the eccentric axis.
- the hub 64 is formed with a bearing hole 65 into which the shaft 23 extends together with the bearing sleeve 24 so that the rotor magnet 60 is freely rotatable about the shaft 23 together with the rotor 40 .
- the outer ring 67 projects into an annular groove 27 formed between the annular projection 26 and the peripheral wall 28 of the lower half 20 also in an overlapping relation with the stator magnet 70 with respect to the radial direction.
- the outer ring 67 and the hub 64 constitute a major portion of the rotor magnet 60 which are disposed radially outwardly of the stator magnet 70 in the overlapping relation therewith, which contributes to minimize the axial dimension as well as the radial dimension of the pump.
- a vibration absorbing member 25 is interposed between the bearing hole 65 and the bearing sleeve 24 of the shaft 23 .
- the stator magnet 70 is composed of a plurality of electro magnets which are mounted within an open space formed underside of the annular projection 26 and extend around the center stud 22 . As shown in FIG. 3 , the stator magnet 70 has its axial center C 70 offset axially from an axial center C 60 of the rotor magnet 60 so as to be spaced further away from the rotor 40 than rotor magnet 60 with respect to the axial direction of the eccentric axis.
- stator magnet 70 develops an attraction force of attracting the rotor magnet 60 and therefore the rotor 40 axially towards the stator magnet 70 , thereby keeping the rotor magnet 60 in abutment against the upper face of the annular projection 26 and therefore minimizing axial fluctuation of the rotor 40 during the rotation thereof.
- each of the vanes 50 is formed on its opposite sides with ribs 54 which are slidably received into guide grooves 44 formed in opposite faces defining the radial slit 42 such that the vane 50 is held slidable only within the radial slit 42 without being axially displaced out of the slit.
- FIGS. 6 and 7 illustrates a vane pump in accordance with a second embodiment of the present invention which is basically identical to the first embodiment except that the rotor 40 is itself made of a permanent magnet to constitute the rotor magnet 60 .
- the rotor 40 is disposed in the pump cavity 12 defined between the lower half 20 and the upper half 30 of the casing 10 and confined within the circumference of the ring 32 .
- the rotor 40 is shaped into a generally flat disc to have a plurality of the circumferentially spaced radial slits 42 each receiving the radially slidable vane 50 , and to have a bearing hole 65 in its center for receiving the shaft 13 and the bearing sleeve 24 so that the rotor 40 is freely rotatable about the eccentric axis defined by the shaft 13 .
- the stator magnet 70 is disposed between the lower and upper halves 20 and 30 radially outwardly of the ring 32 , and is composed of an electromagnet assembly having a yoke ring 72 with a plurality of circumferentially cores 73 each carrying a coil 74 .
- FIGS. 8 and 9 illustrates a vane pump in accordance with a third embodiment of the present invention which is basically identical to the first embodiment except that the rotor 40 is itself made of a permanent magnet to constitute the rotor magnet 60 and the stator magnet 70 is disposed within diameter of the rotor 40 .
- the rotor 40 is disposed in the pump cavity 12 defined between the lower half 20 and the upper half 30 of the casing and confined within the circumference of the ring 22 .
- the rotor 40 is shaped to have a hub 64 and an outer ring 67 integrally connected by means of a bridge 69 .
- the hub 64 has a bearing hole 65 into which the shaft 13 is fitted together with the bearing sleeve 24 so that the rotor 40 is supported to the lower half 10 to be freely rotatable about the shaft 13 or the eccentric axis defined thereby.
- the upper half 30 is formed with an annular groove 38 extending between the hub 64 and the outer ring 67 of the rotor 40 to receive therein the stator magnet 70 .
- the stator magnet 70 is arranged in an overlapping relation with the rotor magnet 60 or the rotor 40 with respect to the radial direction about the eccentric axis so as to minimize the axial dimension of the pump.
- the stator magnet 70 is an electromagnet assembly composed of a plurality of cores 73 each carrying a coil 74 .
Abstract
Description
- The present invention is directed to a magnetic drive vane pump.
- Vane pumps are widely known in the art, for example, as disclosed in Japanese patent publication No. 53-2704 A. Generally, the vane pump includes a casing with a pump cavity and a rotor rotatable about an eccentric axis within the pump cavity. The rotor carries a plurality of vanes which moves radially so as to have their outer ends kept in sealed contact with an interior wall of the pump cavity as the rotor rotates, thereby drawing a fluid into the pump cavity, compressing and expelling it out of the pump cavity. The rotor is coupled to an external motor to be driven thereby to rotate. For this purpose, the rotor is provided with a shaft which extends outwardly of the casing for coupling with the motor. Therefore, a sealing is between the shaft and the casing. However, as the shaft is a constantly moving part, there is always a problem that the sealing may become deteriorated during an extended period of use to result in an unintended lead of the fluid.
- In view of the above problem, the present invention has been achieved to provide a magnetic drive vane pump with a leakage free structure. The vane pump in accordance with the present invention includes a casing with a pump cavity, an inlet for introducing a fluid into the pump cavity, and an outlet for discharging the fluid out of the pump cavity. A rotor is disposed within the pump cavity to be rotatable about an eccentric axis with respect to the pump cavity. A plurality of vanes are carried on the rotor and are radially movable so as to be kept into sealed contact with an interior wall of the pump cavity as the rotor is driven to rotate for drawing the fluid into the pump cavity and expelling it out of the pump cavity. The rotor is configured to have a rotor magnet which is magnetically coupled to a stator magnet mounted on the casing outwardly of the pump cavity for driving the rotor. The feature of the present invention resides in that the rotor magnet is configured to have its major portion disposed in an overlapping relation with the stator magnet. Thus, the rotor magnet can be mechanically isolated from the stator magnet disposed outside of the casing to establish a sealless coupling therebetween for making the pump leakage free, yet requiring only a minimum thickness of the pump in the axial direction thereof.
- Preferably, the rotor magnet is disposed radially outwardly of the stator magnet so that the stator magnet can be arranged within a radial dimension of the stator, which assures to give a compact structure to the pump with respect to the radial direction.
- Also, it is preferred that the stator magnet is configured to have its axial center offset from an axial center of the rotor magnet so as to be disposed further away from the rotor than said rotor magnet with respect to the eccentric axis. With this arrangement, the rotor is attracted towards the stator magnet in an axial direction such that the rotor can rotate at a constant level with regard to its axial direction, causing no substantial axial fluctuation.
- Further, the rotor magnet is preferred to be fitted around a shaft extending axially from a center of the casing with a vibration absorbing member interposed therebetween. The vibration absorbing member can well absorb radial vibrations possibly caused by an eccentric rotary motion of the rotor, thereby assuring a smooth and silent rotary motion.
- Besides, each of the vanes, which are slidable fitted respectively in radial grooves in the rotor, is configured to be movable only radially without being caused to fluctuate in the axial direction. For this purpose, each vane is formed on its opposite sides respectively with ribs which engage into guide grooves formed in opposite faces of the rotor defining the radial groove therebetween.
- These and still other advantageous features of the present invention will become more apparent from the following description of preferred embodiments of the present invention when taken in conjunction with the attached drawings.
-
FIG. 1 is an exploded perspective view of a vane pump in accordance with a first embodiment of the present invention; -
FIG. 2 is a horizontal section of the above vane pump; -
FIG. 3 is a cross-section taken along line X-X ofFIG. 2 ; -
FIG. 4 is a cross section taken along line Y-Y ofFIG. 2 ; -
FIG. 5 is an exploded perspective view of a portion of the above vane pump; -
FIG. 6 is a horizontal section of a vane pump in accordance with a second embodiment of the present invention; -
FIG. 7 is a cross section taken along line 7-7 ofFIG. 6 ; -
FIG. 8 is a horizontal section of a vane pump in accordance with a third embodiment of the present invention; and -
FIG. 9 is a cross-section taken along line 9-9 ofFIG. 8 . - Referring now to
FIGS. 1 to 4 , there is shown a magnetic drive vane pump in accordance with a first embodiment of the present invention. The pump includes acasing 10 formed in its interior with acylindrical pump cavity 12 which accommodates therein arotor 40 having an eccentric axis offset from an axis of thepump cavity 12. Thecasing 10 is composed of alower half 20 and anupper half 30 which are secured to each other with a sealingring 14 held therebetween. The lower andupper halves upper recess 31 which are cooperative to define thepump cavity 12. As seen inFIGS. 3 and 4 , thelower half 20 is formed to have acenter stud 22 anchoring ashaft 23, and anannular projection 26 between thecenter stud 22 and aperipheral wall 28. Theshaft 23 projects from thecenter stud 22 into acenter concavity 29 of thelower half 20 to define the eccentric axis, and is surrounded by abearing sleeve 24. Aring 32 is fitted inside of theupper half 30 to extend around the periphery of theupper recess 31 with its one axial end resting on theperipheral wall 28 of thelower half 20. Theupper half 30 is formed with aninlet 34 for introducing a fluid into thepump cavity 12 through aport 35 in thering 32 and anoutlet 36 for expelling the fluid out of the pump cavity through aport 37 of thering 32. - The
rotor 40 is shaped into a disc disposed within the upper recess 21 and carries a plurality ofvanes 50 which are slidably received respectively in circumferentially spacedradial slits 42. As therotor 40 is driven to rotate, each of thevanes 50 is shifted radially outwardly by a centrifugal force to have its outer end in sealing contact with the inside of thering 32, thereby forming a displacement chamber confined between the adjacent vanes and between thering 32 and the rotor. The displacement chamber undergoes expansion and contraction while therotor 40 rotates about the eccentric axis, thereby drawing the fluid into and expelling it out of thepump cavity 12. - The
rotor 40 carries arotor magnet 60 which is magnetically coupled to astator magnet 70 disposed outside of thecasing 10 so as to be driven thereby to rotate. Therotor magnet 60 is a permanent magnet which is integrated with therotor 40 to form a unitary structure. Therotor magnet 60 is shaped to have athin base 62 secured on one axial end face of therotor 40, ahub 64 projecting axially from the center of thebase 62, and anouter ring 67 projecting axially from the periphery of thebase 62. Thehub 64 is received into thecenter concavity 29 in an overlapping relation with thestator magnet 70 with respect to the radial direction about the eccentric axis. Thehub 64 is formed with abearing hole 65 into which theshaft 23 extends together with thebearing sleeve 24 so that therotor magnet 60 is freely rotatable about theshaft 23 together with therotor 40. Theouter ring 67 projects into anannular groove 27 formed between theannular projection 26 and theperipheral wall 28 of thelower half 20 also in an overlapping relation with thestator magnet 70 with respect to the radial direction. Theouter ring 67 and thehub 64 constitute a major portion of therotor magnet 60 which are disposed radially outwardly of thestator magnet 70 in the overlapping relation therewith, which contributes to minimize the axial dimension as well as the radial dimension of the pump. - In order to reduce radial vibrations of the
rotor 40 which may occur during its rotation about the eccentric axis, avibration absorbing member 25 is interposed between thebearing hole 65 and thebearing sleeve 24 of theshaft 23. - The
stator magnet 70 is composed of a plurality of electro magnets which are mounted within an open space formed underside of theannular projection 26 and extend around thecenter stud 22. As shown inFIG. 3 , thestator magnet 70 has its axial center C70 offset axially from an axial center C60 of therotor magnet 60 so as to be spaced further away from therotor 40 thanrotor magnet 60 with respect to the axial direction of the eccentric axis. Thus, thestator magnet 70 develops an attraction force of attracting therotor magnet 60 and therefore therotor 40 axially towards thestator magnet 70, thereby keeping therotor magnet 60 in abutment against the upper face of theannular projection 26 and therefore minimizing axial fluctuation of therotor 40 during the rotation thereof. - As shown in
FIG. 5 , each of thevanes 50 is formed on its opposite sides withribs 54 which are slidably received intoguide grooves 44 formed in opposite faces defining theradial slit 42 such that thevane 50 is held slidable only within theradial slit 42 without being axially displaced out of the slit. -
FIGS. 6 and 7 illustrates a vane pump in accordance with a second embodiment of the present invention which is basically identical to the first embodiment except that therotor 40 is itself made of a permanent magnet to constitute therotor magnet 60. Like parts are designated by like reference numerals and no duplicate explanation is made herein for simplicity. Therotor 40 is disposed in thepump cavity 12 defined between thelower half 20 and theupper half 30 of thecasing 10 and confined within the circumference of thering 32. Therotor 40 is shaped into a generally flat disc to have a plurality of the circumferentially spacedradial slits 42 each receiving the radiallyslidable vane 50, and to have abearing hole 65 in its center for receiving theshaft 13 and thebearing sleeve 24 so that therotor 40 is freely rotatable about the eccentric axis defined by theshaft 13. Thestator magnet 70 is disposed between the lower andupper halves ring 32, and is composed of an electromagnet assembly having ayoke ring 72 with a plurality of circumferentiallycores 73 each carrying acoil 74. -
FIGS. 8 and 9 illustrates a vane pump in accordance with a third embodiment of the present invention which is basically identical to the first embodiment except that therotor 40 is itself made of a permanent magnet to constitute therotor magnet 60 and thestator magnet 70 is disposed within diameter of therotor 40. Like parts are designated by like reference numerals and no duplicate explanation is made herein for simplicity. Therotor 40 is disposed in thepump cavity 12 defined between thelower half 20 and theupper half 30 of the casing and confined within the circumference of thering 22. Therotor 40 is shaped to have ahub 64 and anouter ring 67 integrally connected by means of abridge 69. Thehub 64 has abearing hole 65 into which theshaft 13 is fitted together with the bearingsleeve 24 so that therotor 40 is supported to thelower half 10 to be freely rotatable about theshaft 13 or the eccentric axis defined thereby. Theupper half 30 is formed with anannular groove 38 extending between thehub 64 and theouter ring 67 of therotor 40 to receive therein thestator magnet 70. Thus, thestator magnet 70 is arranged in an overlapping relation with therotor magnet 60 or therotor 40 with respect to the radial direction about the eccentric axis so as to minimize the axial dimension of the pump. Thestator magnet 70 is an electromagnet assembly composed of a plurality ofcores 73 each carrying acoil 74. - Although the present invention is explained specifically with reference to the above embodiments, it should not be delimited to the embodiments and can encompass any combination of the individual features disclosed in the above embodiments.
Claims (5)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2007-056122 | 2007-03-06 | ||
JP2007056122A JP4791987B2 (en) | 2007-03-06 | 2007-03-06 | Vane pump |
Publications (1)
Publication Number | Publication Date |
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US20080219875A1 true US20080219875A1 (en) | 2008-09-11 |
Family
ID=39672842
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US12/073,303 Abandoned US20080219875A1 (en) | 2007-03-06 | 2008-03-04 | Magnetic drive vane pump |
Country Status (5)
Country | Link |
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US (1) | US20080219875A1 (en) |
EP (1) | EP1967733A2 (en) |
JP (1) | JP4791987B2 (en) |
KR (1) | KR100965475B1 (en) |
TW (1) | TW200839098A (en) |
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US20060245961A1 (en) * | 2005-04-28 | 2006-11-02 | Tecumseh Products Company | Rotary compressor with permanent magnet motor |
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US20120163997A1 (en) * | 2010-12-27 | 2012-06-28 | Charles Shepard | Vane compressor with integrated motor |
CN109312736A (en) * | 2016-05-03 | 2019-02-05 | 实用动力集团 | Pump unit with integrated piston pump and electric motor |
CN111788392A (en) * | 2018-02-28 | 2020-10-16 | 安捷伦科技有限公司 | Vacuum pumping system comprising a vacuum pump and its motor |
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TWI743157B (en) * | 2016-09-15 | 2021-10-21 | 瑞士商雀巢製品股份有限公司 | Compressor arrangement with integrated motor |
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Cited By (7)
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US20060245961A1 (en) * | 2005-04-28 | 2006-11-02 | Tecumseh Products Company | Rotary compressor with permanent magnet motor |
CN101813085A (en) * | 2010-03-22 | 2010-08-25 | 黄武源 | Self-sucking energy-saving high-efficiency water pump |
US20120163997A1 (en) * | 2010-12-27 | 2012-06-28 | Charles Shepard | Vane compressor with integrated motor |
CN109312736A (en) * | 2016-05-03 | 2019-02-05 | 实用动力集团 | Pump unit with integrated piston pump and electric motor |
US20190154036A1 (en) * | 2016-05-03 | 2019-05-23 | Actuant Corporation | Pump unit with integrated piston pump and electric motor |
US10598177B2 (en) * | 2016-05-03 | 2020-03-24 | Power Packer North America, Inc. | Pump unit with integrated piston pump and electric motor |
CN111788392A (en) * | 2018-02-28 | 2020-10-16 | 安捷伦科技有限公司 | Vacuum pumping system comprising a vacuum pump and its motor |
Also Published As
Publication number | Publication date |
---|---|
TW200839098A (en) | 2008-10-01 |
JP2008215262A (en) | 2008-09-18 |
EP1967733A2 (en) | 2008-09-10 |
KR100965475B1 (en) | 2010-06-24 |
JP4791987B2 (en) | 2011-10-12 |
KR20080081862A (en) | 2008-09-10 |
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Legal Events
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AS | Assignment |
Owner name: MATSUSHITA ELECTRIC WORKS, LTD., JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NISHIKATA, MASAAKI;KUSAKABE, TSUYOSHI;HOJO, TSUKASA;AND OTHERS;REEL/FRAME:020648/0394 Effective date: 20080220 |
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AS | Assignment |
Owner name: PANASONIC ELECTRIC WORKS CO., LTD., JAPAN Free format text: CHANGE OF NAME;ASSIGNOR:MATSUSHITA ELECTRIC WORKS, LTD.;REEL/FRAME:022206/0574 Effective date: 20081001 Owner name: PANASONIC ELECTRIC WORKS CO., LTD.,JAPAN Free format text: CHANGE OF NAME;ASSIGNOR:MATSUSHITA ELECTRIC WORKS, LTD.;REEL/FRAME:022206/0574 Effective date: 20081001 |
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |