US20020028153A1 - Automotive vane pump for generating anti-centrifugal force - Google Patents
Automotive vane pump for generating anti-centrifugal force Download PDFInfo
- Publication number
- US20020028153A1 US20020028153A1 US09/752,579 US75257900A US2002028153A1 US 20020028153 A1 US20020028153 A1 US 20020028153A1 US 75257900 A US75257900 A US 75257900A US 2002028153 A1 US2002028153 A1 US 2002028153A1
- Authority
- US
- United States
- Prior art keywords
- blades
- centrifugal force
- rotor
- pump
- housing
- 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.)
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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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
-
- 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
Definitions
- the present invention relates to an automotive vane pump for generating anti-centrifugal force, and more particularly to an automotive vane pump for generating anti-centrifugal force adapted to maintain constant discharge pressure and discharge amount regardless of rotating speed to prevent power loss and to improve durability via stable operation.
- the automotive device includes a stator 4 having a rotor 5 radiately equipped with a plurality of blades 6 rotated by a shaft 2 coupled to a pulley 1 driven by an engine and varied by centrifugal force, and a housing 3 where the stator 4 is received via a cover 7 .
- the present invention is disclosed to solve the aforementioned problems and it is an object of the present invention to provide an automotive vane pump for generating anti-centrifugal force adapted to react against the centrifugal force working on blades when rotor is rotated to thereby restrict radial protrusion of the blades according to increased turning effect such that a constant gap can be maintained at all times without direct contact with stator.
- an automotive vane pump for generating anti-centrifugal force comprising:
- a stator housing a rotor radiately equipped with a plurality of blades variably withdrawn according to size of centrifugal force generated by being rotated and coupled to a shaft received in a housing having inlet/outlet structure of operation oil in coupling with a pulley driven by an engine;
- centrifugal force generating means mounted at the rotor for generating centrifugal force in order to pull the blades into the rotor relative to radial withdrawal of the blades, where the centrifugal force generating means further comprises:
- a resilient member constituting a spring radiately formed at the rotor, equipped at a slot accepting the blades and compressed by movement of the blades;
- FIG. 1 is an exploded constitutional drawing of a vane pump according to the prior art
- FIG. 2 is an exploded constitutional drawing of an automotive vane pump for generating anti-centrifugal force according to the present invention
- FIG. 3 is a perspective view for illustrating counter centrifugal force generating means for forcibly reducing the size of centrifugal force against centrifugal force generated from variable means;
- FIG. 4 is a partial sectional view for illustrating counter centrifugal force generating means for forcibly reducing the size of centrifugal force against centrifugal force generated from variable means;
- FIG. 5 is an operational constitutional drawing for illustrating counter centrifugal force generating means for forcibly reducing the size of centrifugal force generated from variable means.
- FIG. 2 is an exploded constitutional drawing of an automotive vane pump for generating anti-centrifugal force according to the present invention, where the vane pump includes a shaft 2 coupled to a pulley 1 driven by an engine, a stator 4 mounted therein with a rotor 5 radiately equipped with a plurality of blades variably withdrawn according to size of centrifugal force generated in rotation with coupled shaft 2 , centrifugal generating means 9 mounted at the rotor 4 accommodated in the stator 4 for generating centrifugal force in order to pull the blades 6 into the rotor 4 against radial withdrawal of the blades 6 , a housing 3 for accepting the stator 4 , shaft 2 and the like and having an inlet/outlet structure of operation oil, and a cover 7 for sealing up the housing 3 .
- the centrifugal generating means 9 is formed with a resilient member 9 a constituting a spring radiately formed at the rotor 5 equipped at a slot 5 a accepting the blades 6 and compressed by movement of the blades 6 , and a ball pendulum 9 b exposed to a centrally-opened communicating groove 5 c through a connecting groove 5 b connected to the slot 5 a where the blades 6 are accommodated.
- the ball pendulum 9 b includes a first link ( 9 b 1 ) fixed to one end of a blade 6 , a second link ( 9 b 1 ′′) for being inserted into the communicating groove 5 c and for coupling the first and second link ( 9 b 1 and 9 b 1 ′′) each formed at the plurality of blades 6 radiately provided via a connecting ring 9 c for being inserted into the communicating groove 5 c and vertically moving according to centrifugal force.
- Unexplained reference numeral 8 is a case equipped at the rotor 5 for encompassing the ball pendulum 9 b.
- the vane pump according to the present invention is formed such that blades 6 radiately appear and disappear according to the centrifugal force generated by the rotor 5 rotating by way of turning effect of pulley 1 received via the shaft 2 along with the engine to generate vacuum suction force for sucking operation oil from an oil tank in the stator 4 and to compress the infused operation oil for generation of oil pressure.
- a radius from center of the rotor 5 to the ball ( 9 b 1 ′′) of the ball pendulum 9 b is smaller than the radius of upto one end of the blade 6 such that relatively smaller centrifugal force is created and spring resilience of the resilient member 9 a provided at the slot 5 a of the rotor 5 acts to push out the blades 6 , such that the centrifugal force created from the ball pendulum 9 b cannot pull the blades 6 toward the rotor 5 whereby the blades 6 are maximally pulled from the rotor 5 to make a sliding contact with the stator 4 , thereby generating a large compression force and oil pressure at the same time.
- the centrifugal force of the ball pendulum 9 b resists the centrifugal force of the blades 6 which try to go out, and instead is pulled in to overcome repulsive force of the spring which is the resilient member 9 a, and compressed to pull in the blades.
- the blades 6 are rotated with a slight gap from an inner surface of the stator 4 , that is, rotated without sliding contact with the inner surface of the stator 4 to thereby create less compression force than the compression made during the low speed of rotation.
- the kind of compression loss is not that large compared with compression increase according to increased speed, such that no decrease of oil pressure of operation oil occurs.
- the centrifugal force of the ball pendulum 9 b resists the centrifugal force of the blades 6 trying to pull out and pulls in the blades 6 , and compresses the resilient member 9 a of spring to pull in the blades 6 .
- the connecting ring 9 c of the ball pendulum 9 b is raised with the hinge ( 9 b 1 ′) coupling the first and second links ( 9 b 1 and 9 b 1 ′′) raised by the ball ( 9 b 1 ′′′) laid down toward surface of the rotor 5 .
- the blades 6 are rotated with a relatively larger gap from the inner surface of the stator 4 compared with the rotor 5 at the intermediate speed of lower without making a sliding contact. However, the blades 6 are rotated at a speed relatively higher than the speed of low or intermediate level such that a greater compression force is generated to remarkably increase oil pressure of the operation oil.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
An automotive vane pump for generating anti-centrifugal force, and more particularly to an automotive vane pump for generating anti-centrifugal force adapted to maintain constant discharge pressure and discharge amount regardless of rotating speed to prevent power loss and to improve durability via stable operation, the pump comprising: a stator housing a rotor radiately equipped with a plurality of blades variably withdrawn according to size of centrifugal force generated by being rotated and coupled to a shaft received in a housing having inlet/outlet structure of operation oil in coupling with a pulley driven by an engine; a cover coupled to the housing mounted with the stator for sealing up the housing; and centrifugal force generating means mounted at the rotor 5 for generating centrifugal force in order to pull the blades into the rotor relative to radial withdrawal of the blades, where the centrifugal force generating means further comprises: a resilient member constituting a spring radiately formed at the rotor, equipped at a slot accepting the blades and compressed by movement of the blades; and a ball pendulum exposed to a centrally-opened communicating groove through a connecting groove connected to the slot where the blades are accommodated.
Description
- 1. Field of the Invention
- The present invention relates to an automotive vane pump for generating anti-centrifugal force, and more particularly to an automotive vane pump for generating anti-centrifugal force adapted to maintain constant discharge pressure and discharge amount regardless of rotating speed to prevent power loss and to improve durability via stable operation.
- 2. Description of the Prior Art
- In general, automotive devices such as power steering apparatus and the like operated via oil pressure utilize vane pumps driven by engine output for generation of oil pressure. As illustrated in FIG. 1, the automotive device includes a
stator 4 having arotor 5 radiately equipped with a plurality ofblades 6 rotated by ashaft 2 coupled to a pulley 1 driven by an engine and varied by centrifugal force, and a housing 3 where thestator 4 is received via acover 7. - When the pulley1 rotating with the engine and the
shaft 2 are rotated, therotor 5 in the housing 3 is rotated at the same time, and theblades 6 radiately appearing and disappearing according to rotary centrifugal force of therotor 5 make a sliding contact along the rotor-receivingstator 4 and to variably increase volume at a suction region (not shown), such that vacuum suction force is generated at the suction region to suck operation oil from and oil tank (not shown), generating oil pressure. In other words, the operation oil infused into thestator 4 is pushed into and compressed in a narrow area of thestator 4 to generate the oil pressure. - However, there is a problem in that, when the operation oil, being infused via the
blades 6 radiately protruded according to centrifugal force output from therotor 5 thus rotated, is compressed, compressed amount and pressure of vane pump rotating at a high speed are increased to simultaneously increase the centrifugal force of the blades, such that friction with thestator 4 is also increased to generate abrasion at theblades 6 andstator 4, thereby increasing great noise. - There is another problem in that the mutually-
abraded blades 6 and thestator 4 also create vibration to result in generation of resonance to peripheral devices such as engine and the like, shortening life of automobile and decreasing quality thereof. - The present invention is disclosed to solve the aforementioned problems and it is an object of the present invention to provide an automotive vane pump for generating anti-centrifugal force adapted to react against the centrifugal force working on blades when rotor is rotated to thereby restrict radial protrusion of the blades according to increased turning effect such that a constant gap can be maintained at all times without direct contact with stator.
- In accordance with the object of the present invention, there is provided an automotive vane pump for generating anti-centrifugal force, the pump comprising:
- a stator housing a rotor radiately equipped with a plurality of blades variably withdrawn according to size of centrifugal force generated by being rotated and coupled to a shaft received in a housing having inlet/outlet structure of operation oil in coupling with a pulley driven by an engine;
- a cover coupled to the housing mounted with the stator for sealing up the housing; and
- centrifugal force generating means mounted at the rotor for generating centrifugal force in order to pull the blades into the rotor relative to radial withdrawal of the blades, where the centrifugal force generating means further comprises:
- a resilient member constituting a spring radiately formed at the rotor, equipped at a slot accepting the blades and compressed by movement of the blades; and
- a ball pendulum exposed to a centrally-opened communicating groove through a connecting groove connected to the slot where the blades are accommodated.
- For fuller understanding of the nature and objects of the invention, reference should be made to the following detailed description taken in conjunction with the accompanying drawings in which:
- FIG. 1 is an exploded constitutional drawing of a vane pump according to the prior art;
- FIG. 2 is an exploded constitutional drawing of an automotive vane pump for generating anti-centrifugal force according to the present invention;
- FIG. 3 is a perspective view for illustrating counter centrifugal force generating means for forcibly reducing the size of centrifugal force against centrifugal force generated from variable means;
- FIG. 4 is a partial sectional view for illustrating counter centrifugal force generating means for forcibly reducing the size of centrifugal force against centrifugal force generated from variable means; and
- FIG. 5 is an operational constitutional drawing for illustrating counter centrifugal force generating means for forcibly reducing the size of centrifugal force generated from variable means.
- Now, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
- FIG. 2 is an exploded constitutional drawing of an automotive vane pump for generating anti-centrifugal force according to the present invention, where the vane pump includes a
shaft 2 coupled to a pulley 1 driven by an engine, astator 4 mounted therein with arotor 5 radiately equipped with a plurality of blades variably withdrawn according to size of centrifugal force generated in rotation with coupledshaft 2, centrifugal generating means 9 mounted at therotor 4 accommodated in thestator 4 for generating centrifugal force in order to pull theblades 6 into therotor 4 against radial withdrawal of theblades 6, a housing 3 for accepting thestator 4,shaft 2 and the like and having an inlet/outlet structure of operation oil, and acover 7 for sealing up the housing 3. - At this location, the centrifugal generating means9, as illustrated in FIG. 3, is formed with a
resilient member 9 a constituting a spring radiately formed at therotor 5 equipped at aslot 5 a accepting theblades 6 and compressed by movement of theblades 6, and aball pendulum 9 b exposed to a centrally-opened communicatinggroove 5 c through a connectinggroove 5 b connected to theslot 5 a where theblades 6 are accommodated. - In other words, the
ball pendulum 9 b includes a first link (9 b 1) fixed to one end of ablade 6, a second link (9 b 1″) for being inserted into the communicatinggroove 5 c and for coupling the first and second link (9b 1 and 9 b 1″) each formed at the plurality ofblades 6 radiately provided via a connectingring 9 c for being inserted into the communicatinggroove 5 c and vertically moving according to centrifugal force. -
Unexplained reference numeral 8 is a case equipped at therotor 5 for encompassing theball pendulum 9 b. - Now, operational procedure will be described according to the present invention.
- The vane pump according to the present invention is formed such that
blades 6 radiately appear and disappear according to the centrifugal force generated by therotor 5 rotating by way of turning effect of pulley 1 received via theshaft 2 along with the engine to generate vacuum suction force for sucking operation oil from an oil tank in thestator 4 and to compress the infused operation oil for generation of oil pressure. - At this time, the turning effect of the
rotor 5 working to allow theblades 6 to radiately appear and disappear rotates theball pendulum 9 b at the centrifugal force generating means 9 to thereby introduce theblades 6 into therotor 5 according to size of the centrifugal force, where the rotating speed of therotor 5 is explained in detail. - First of all, when the
rotor 5 is rotated at a low speed, the centrifugal force generated by rotation of therotor 5 pushes the blades outside of therotor 5 to a maximum degree, where theball pendulum 9 b at the centrifugal force generating means 9 rotating with therotor 5 is also influenced by the centrifugal force. - However, a radius from center of the
rotor 5 to the ball (9 b 1″) of theball pendulum 9 b is smaller than the radius of upto one end of theblade 6 such that relatively smaller centrifugal force is created and spring resilience of theresilient member 9 a provided at theslot 5 a of therotor 5 acts to push out theblades 6, such that the centrifugal force created from theball pendulum 9 b cannot pull theblades 6 toward therotor 5 whereby theblades 6 are maximally pulled from therotor 5 to make a sliding contact with thestator 4, thereby generating a large compression force and oil pressure at the same time. - Successively when the
rotor 5 is accelerated in rotation thereof from a low speed to an intermediate speed, the centrifugal force generated by the rotatingrotor 5 tries to push out the blades with much greater force but theblades 6 are made to be pulled inside of therotor 5 because the centrifugal force of theball pendulum 9 b mounted with the ball (9 b 1′″) having a predetermined weight becomes relatively bigger than the centrifugal force of the rotatingrotor 5. - In other words, the centrifugal force of the
ball pendulum 9 b resists the centrifugal force of theblades 6 which try to go out, and instead is pulled in to overcome repulsive force of the spring which is theresilient member 9 a, and compressed to pull in the blades. - Successively, the
blades 6 are rotated with a slight gap from an inner surface of thestator 4, that is, rotated without sliding contact with the inner surface of thestator 4 to thereby create less compression force than the compression made during the low speed of rotation. However, the kind of compression loss is not that large compared with compression increase according to increased speed, such that no decrease of oil pressure of operation oil occurs. - Furthermore, when the
rotor 5 is increased in speed thereof from the intermediate lever to a high level, the centrifugal force generated by the rotatingrotor 5 makes the centrifugal force of theball pendulum 9 b much greater to thereby pull in theblades 6 deeper into therotor 5. - In other words, as illustrated in FIG. 5, the centrifugal force of the
ball pendulum 9 b resists the centrifugal force of theblades 6 trying to pull out and pulls in theblades 6, and compresses theresilient member 9 a of spring to pull in theblades 6. At this time, the connectingring 9 c of theball pendulum 9 b is raised with the hinge (9 b 1′) coupling the first and second links (9 b 1 and 9 b 1″) raised by the ball (9 b 1′″) laid down toward surface of therotor 5. - Successively, the
blades 6 are rotated with a relatively larger gap from the inner surface of thestator 4 compared with therotor 5 at the intermediate speed of lower without making a sliding contact. However, theblades 6 are rotated at a speed relatively higher than the speed of low or intermediate level such that a greater compression force is generated to remarkably increase oil pressure of the operation oil. - In comparison with the
rotor 5 rotating at a lower speed with sliding contact with the inner surface of thestator 4, the blades are rotated with a slight gap from the inner surface of thestator 4 at the intermediate and high speed of rotation, thereby generating no noise and friction. - Meanwhile, when the rotor is reduced in rotation thereof from high speed to intermediate speed, and again from intermediate speed to low speed, the centrifugal force acting on the
ball pendulum 9 b at the centrifugalforce generating means 9 is decreased, whereby, the spring which is theresilient member 9 a is restored to push theblades 6 to the outside, such that the connectingring 9 c is lowered along with the hinge (9 b 1′) coupling the first and the second link (9 b 1 and 9 b 1″) which moves downward, thereby making a form as shown in FIG. 4. - As apparent from the foregoing, there is an advantage in the automotive vane pump for generating anti-centrifugal force thus described according to the present invention in that centrifugal force is generated to reversely react to pull the blades toward the rotor by way of rotor allowing the blades to radiately appear and disappear via the centrifugal force, forming a gap between the blades and the stator by way of rotor increasing in rotational speed to prevent friction and noise, such that constant discharge pressure and discharge volume are maintained regardless of rotational speed to thereby avoid power loss and improve durability by way of stable operation.
Claims (6)
1. An automotive vane pump for generating anti-centrifugal force, the pump comprising:
a stator housing a rotor radiately equipped with a plurality of blades variably withdrawn according to size of centrifugal force generated by being rotated and coupled to a shaft received in a housing having inlet/outlet structure of operation oil in coupling with a pulley driven by an engine;
a cover coupled to the housing mounted with the stator for sealing up the housing; and
centrifugal force generating means mounted at the rotor for generating centrifugal force in order to pull the blades into the rotor relative to radial withdrawal of the blades, where the centrifugal force generating means further comprises:
a resilient member constituting a spring radiately formed at the rotor, equipped at a slot accepting the blades and compressed by movement of the blades; and
a ball pendulum exposed to a centrally-opened communicating groove through a connecting groove connected to the slot where the blades are accommodated.
2. The pump as defined in claim 1 , wherein the centrifugal generating means comprises:
a resilient member constituting a spring radiately formed at the rotor equipped at a slot accepting the blades and compressed by movement of the blades; and
a ball pendulum exposed to a centrally-opened communicating groove through a connecting groove connected to the slot where the blades are accommodated.
3. The pump as defined in claim 2 , wherein the resilient member is a spring having a resilient force.
4. The pump as defined in claim 2 , the ball pendulum comprises:
a first link fixed to one end of a blade;
a second link coupled to the first link via a hinge; and
a ball coupled to one end of the second link and having a predetermined weight.
5. The pump as defined in claim 4 , therein the hinge is coupled to a connecting ring vertically moving according to centrifugal force by being inserted into a communicating groove of the rotor.
6. The pump as defined in claim 2 , wherein the centrifugal force generating means further comprises a case 8 mounted at the rotor for encompassing the ball pendulum.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020000052409A KR100356858B1 (en) | 2000-09-05 | 2000-09-05 | An automotive vane pump for generating anti-centrifugal force |
KR2000-52409 | 2000-09-05 |
Publications (2)
Publication Number | Publication Date |
---|---|
US20020028153A1 true US20020028153A1 (en) | 2002-03-07 |
US6368090B1 US6368090B1 (en) | 2002-04-09 |
Family
ID=19687446
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/752,579 Expired - Fee Related US6368090B1 (en) | 2000-09-05 | 2000-12-27 | Automotive vane pump for generating anti-centrifugal force |
Country Status (2)
Country | Link |
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US (1) | US6368090B1 (en) |
KR (1) | KR100356858B1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101614204B (en) * | 2008-06-27 | 2011-07-20 | 托克海姆控股有限公司 | Liquid conveyer with blades |
CN110985254A (en) * | 2019-12-30 | 2020-04-10 | 江苏湖润泵业科技有限公司 | High-speed common rail vane pump |
CN115127182A (en) * | 2022-08-31 | 2022-09-30 | 广东伊斐净化科技有限公司 | Household air purifier |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR200451820Y1 (en) * | 2008-07-10 | 2011-01-13 | 한만성 | A sign flag pole exchanging flag easely for informing golf green hole cup |
KR20130116709A (en) * | 2012-04-16 | 2013-10-24 | 김해남 | Vane pump apparatus |
CN112228895B (en) * | 2020-09-27 | 2023-04-25 | 福建陕科新型能源发展有限公司 | Boiler fume extractor with purifying function utilizing centrifugal force principle |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1538075A (en) * | 1923-02-27 | 1925-05-19 | Wingquist Sven Gustaf | Vane pump |
US2526621A (en) * | 1944-12-23 | 1950-10-24 | R D Fageol Co | Oscillating vane rotary pump |
US3589842A (en) * | 1969-10-24 | 1971-06-29 | Alfred E Timperley | Centrifugal force energy conserving mechanism |
KR910020329A (en) * | 1990-05-16 | 1991-12-19 | 김천경 | Centrifugal vane pump |
-
2000
- 2000-09-05 KR KR1020000052409A patent/KR100356858B1/en not_active IP Right Cessation
- 2000-12-27 US US09/752,579 patent/US6368090B1/en not_active Expired - Fee Related
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101614204B (en) * | 2008-06-27 | 2011-07-20 | 托克海姆控股有限公司 | Liquid conveyer with blades |
CN110985254A (en) * | 2019-12-30 | 2020-04-10 | 江苏湖润泵业科技有限公司 | High-speed common rail vane pump |
CN115127182A (en) * | 2022-08-31 | 2022-09-30 | 广东伊斐净化科技有限公司 | Household air purifier |
Also Published As
Publication number | Publication date |
---|---|
KR20020019244A (en) | 2002-03-12 |
US6368090B1 (en) | 2002-04-09 |
KR100356858B1 (en) | 2002-10-18 |
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Owner name: HYUNDAI MOTOR COMPANY, KOREA, REPUBLIC OF Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:KIM, JAE-CHUL;REEL/FRAME:011426/0114 Effective date: 20001214 |
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