US20130170959A1 - Power steering pump - Google Patents

Power steering pump Download PDF

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Publication number
US20130170959A1
US20130170959A1 US13/717,180 US201213717180A US2013170959A1 US 20130170959 A1 US20130170959 A1 US 20130170959A1 US 201213717180 A US201213717180 A US 201213717180A US 2013170959 A1 US2013170959 A1 US 2013170959A1
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US
United States
Prior art keywords
oil
pump
pump body
distributing plate
cavity
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.)
Abandoned
Application number
US13/717,180
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English (en)
Inventor
Dong Liu
Jun Chen
Shaohua Wu
Mingshan ZHOU
Yuangao JIN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Quanxing Machining Group Co Ltd
Original Assignee
Quanxing Machining Group Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Quanxing Machining Group Co Ltd filed Critical Quanxing Machining Group Co Ltd
Assigned to QUANXING MACHINING GROUP CO., LTD reassignment QUANXING MACHINING GROUP CO., LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHEN, JUN, JIN, YUANGAO, LIU, DONG, WU, SHAOHUA, ZHOU, MINGSHAN
Publication of US20130170959A1 publication Critical patent/US20130170959A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present invention generally relates to a vehicle hydraulic power steering pump, in particular, the present invention relates to a vehicle hydraulic power steering pump that can reduce the temperature of vehicle steering system.
  • FIG. 1 mainly consists of a pump body 3 , a rear cover 19 , a rear oil distributing plate 10 , stator 12 , rotor 13 , blades 14 , front oil distributing plate 15 , positioning pin 11 , a pump shaft 17 , a bearing 2 , a flow securing control valve installed within a valve bore of said pump body 3 , valve seat 8 , and a conical valve core 6 , as well as a number of seals and springs.
  • a high pressure oil passage B is disposed nearby the rear cover 19 .
  • FIG. 2 shows the configuration of internal high pressure oil passage 21 of said pump body 3 within the steering pump in detail (the portion displayed in dense section line), the configuration of said high pressure oil passage 21 is long and exists bending, generating the following defects like:
  • the valve seat in pump body assembly of traditional steering pump substantially is in two configurations that a configuration with non strainer screen where impurities 22 block in the conical valve seal 23 causing untight sealing and causing the pressure never built up, even not changing direction or difficult steering, and another configuration with strainer where single-layer strainer 23 with deep structure can easily lead to impurities stacking on said strainer, even make the steering pump body explosion since the strainer is completely blocked under high pressure, as illustrated all in FIG. 3 .
  • the traditional processing of interior oil return passage within the pump body is generally achieved by drilling in direction perpendicular to the valve bore in which the drilled bore is in a circular shape.
  • the small opening of the shape leading to overflow rate high is easy to cause the temperature rising very fast at overflow rate, even at high temperature, wearing the internal components of steering pump out and decreasing their lifetime.
  • the present invention imposes to resolve the aforementioned technical problems of the prior art, further provides a power steering pump for decreasing the temperature from heat source, thereby reducing the oil temperature of vehicle steering system and improving the service life thereof.
  • a power steering pump comprising a pump body within which an inner cavity being formed, wherein a rear oil distributing plate, a blade assembly consisting of stators, rotors and blades, front oil distributing plate, and pressing springs being sequentially disposed within said inner cavity from its rear portion to front portion, a pump shaft being mounted into said inner cavity of the pump body after connecting the rear oil distributing plate, the blade assembly and the front oil distributing plate in series into one together which front end projects outwards from the front portion of the pump body and further mates with a drive gear, and which rear end is supported into the rear oil distributing plate, which is characterized in that the front oil distributing plate is enclosed with front wall of the inner cavity of the pump body to form a front outlet cavity, a valve bore being formed at outer circumference side of the inner cavity of the pump body communicates with the front outlet cavity, a flow securing control valve is disposed within the valve bore, the front outlet cavity communicates with an oil outlet
  • the high-pressure oil passage includes a horizontal oil passage and a longitudinal oil passage vertically below the oil outlet hole, wherein the horizontal oil passage in parallel with the pump shaft which opening communicates with the front outlet cavity, the longitudinal oil passage perpendicular to the horizontal oil passage or inclined to it at an angle from 60 to 90 degree which opening communicates with the oil outlet hole.
  • the front portion of the pump body is a flange portion
  • rolling bearings and oil seals are arranged between the flange portion and the pump shaft, wherein the oil seal is utilized with dual lips and skeleton rotating oil seal configuration.
  • a sliding bearing is further arranged between the pump shaft and the rear oil distributing plate.
  • a conical valve being arranged within the flow securing control valve that comprises a conical valve core and a pressure limiting spring, wherein a conical opening matched with the conical valve core is arranged within a valve seat, the pressure limiting spring compresses the conical valve core to push it against the conical opening.
  • outer-layer strainer of said dual-layer strainer has 60 mesh with diameter ⁇ 0.18, inner-layer strainer of said dual-layer strainer has 120 mesh with diameter ⁇ 0.06, wherein both strainers are outward bulge configuration.
  • oil return passage is obliquely drilled in direction of the valve bore
  • opening of the oil return passage within the valve bore represents an ellipse shape
  • 0-shape sealing rings are disposed between the outer circumference of the front oil distributing plate and inner cavity wall of the pump body, and between the rear oil distributing plate and inner cavity wall of the pump body respectively, and an 0-shape sealing ring is disposed on the surface of the flange portion of the pump body.
  • the advantage of the present invention states in that it adopts a high-pressure front cavity configuration of the pump body to shorten the length of high-pressure oil passage and make the passage's smooth transition, further reduce the flow pressure loss, which hence avoids steering pump failure caused by aggressive overheating generated in the traditional configuration with excessive length of the flow passage and bending. Because of inner flow passage of the pump body designed in high-pressure front cavity configuration, few processing procedures, easy process, and lower cost are achieved. Meanwhile, the integrated assembly design of rear cover with rear oil distributing plate not only reduces the manufacturing cost in aspect of the material and the processing, but also improves the stability and lifetime of assembly in view of its simplified structure.
  • the valve seat of the invention adopts a dual-layer strainer configuration that possesses excellent straining effect and prevents being blocked resulting in explosion of the pump body.
  • Oil return passage of the invention being obliquely drilled in direction of the valve bore within which the oil return passage represents an ellipse shape and its enough length of the opening promotes higher efficiency while effusion at low flow speed, less heat and pressure loss.
  • the pump of the invention decreasing the temperature from heat source not only can improve the service life of the pump itself, but also the vehicle steering system.
  • FIG. 1 is a schematic cutaway view illustrating the traditional configuration of a steering pump assembly in prior art
  • FIG. 2 is a schematic cutaway view illustrating the traditional configuration of an inner high-pressure oil passage within pump body of the power steering pump in prior art
  • FIG. 3 is a schematic diagram illustrating the traditional configuration of a valve assembly of the steering pump in prior art
  • FIG. 4 is a schematic diagram illustrating the position of the traditional configuration of valve assembly of the steering pump within the valve bore in prior art
  • FIG. 5 is a schematic cutaway view illustrating the power steering pump assembly with front high-pressure cooling cavity of the present invention
  • FIG. 6 is a schematic cutaway view illustrating high-pressure oil passage within the pump body of the power steering pump assembly with front high-pressure cooling cavity of the present invention
  • FIG. 7 is a schematic diagram illustrating the configuration of a valve seat in the valve assembly of the power steering pump of the present invention.
  • FIG. 8 is a schematic diagram illustrating the position of the valve assembly of the power steering pump within the valve bore of the present invention.
  • a preferred embodiment of the power steering pump with front high-pressure cooling cavity of the present invention comprising a pump body 3 within which an inner cavity being formed, wherein a rear oil distributing plate 10 , a blade assembly consisting of stators 12 , rotors 13 and blades 14 , front oil distributing plate 15 , and pressing springs 16 being sequentially disposed within said inner cavity from its rear portion to front portion.
  • a pump shaft 17 being mounted into said inner cavity of the pump body 3 after connecting the rear oil distributing plate 10 , the blade assembly and the front oil distributing plate 15 in series into one together which front end projects outwards from the front portion of the pump body 3 and further mates with a drive gear 1 , and which rear end is supported into the rear oil distributing plate 10 , the front oil distributing plate 15 is enclosed with front wall of the inner cavity of the pump body 3 to form a front outlet cavity A, a valve bore being formed at outer circumference side of the inner cavity of the pump body 3 communicates with the front outlet cavity A, a flow securing control valve is disposed within the valve bore, the front outlet cavity A communicates with an oil outlet hole 20 at the front portion of pump body 3 through a high-pressure oil passage 21 , the outer circumference portion of the blade assembly is enclosed with inner wall of the inner cavity of the pump body 3 to form a rear cavity of the pump body 3 , the valve bore communicates with said rear cavity of the pump body 3 through an oil return passage B, the blades driven
  • the front outlet cavity A is positioned vertically below the oil outlet hole
  • the high-pressure oil passage includes a horizontal oil passage and a longitudinal oil passage vertically below the oil outlet hole, wherein the horizontal oil passage in parallel with the pump shaft 17 which opening communicates with the front outlet cavity A, the longitudinal oil passage perpendicular to the horizontal oil passage or inclined to it at an angle from 60 to 90 degree which opening communicates with the oil outlet hole.
  • An opening is formed at the rear portion of the inner cavity of the pump body 3 and enclosed by the rear oil distributing plate 10 .
  • the front portion of the pump body 3 is a flange portion, and rolling bearings 2 and oil seals 18 are arranged between the flange portion and the pump shaft 17 , wherein the oil seal 18 is utilized with dual lips and skeleton rotating oil seal configuration.
  • a sliding bearing 9 is further arranged between the pump shaft 17 and the rear oil distributing plate 10 .
  • the rear oil distributing plate 10 , the blade assembly and the front oil distributing plate 15 are connected in series through positioning pins into one together.
  • a conical valve being arranged within the flow securing control valve that comprises a conical valve core 6 and a pressure limiting spring 5 , wherein a conical opening matched with the conical valve core 6 is arranged within a valve seat 8 , the pressure limiting spring 5 compresses the conical valve core 6 to push it against the conical opening.
  • the valve seat 8 in the flow securing control valve is utilized with dual-layer strainer configuration, outer-layer strainer of said dual-layer strainer has 60 mesh with diameter ⁇ 0.18, inner-layer strainer of said dual-layer strainer has 120 mesh with diameter ⁇ 0.06, wherein both strainers are outward bulge configuration.
  • the oil return passage B is obliquely drilled in direction of the valve bore, wherein opening of the oil return passage B within the valve bore represents an ellipse shape.
  • 0-shape sealing rings are disposed between the outer circumference of the front oil distributing plate 15 and inner cavity wall of the pump body 3 , and between the rear oil distributing plate 10 and inner cavity wall of the pump body 3 respectively, and an 0-shape sealing ring is disposed on the surface of the flange portion of the pump body 3 .
  • the working principle of the front high-pressure cooling cavity of the power steering pump of the invention is that in two enclosure chambers enclosed by the stators 12 , rotors 13 , blades 14 , front oil distributing plate 15 and rear oil distributing plate 10 as blades 14 are glued to the inner surface of the stator 12 under the action of centrifugal force when the steering pump driven by the engine being on work, their working volume changes from being small to being large, and then from being large to being small, compressing oil to complete an absorbing and draining oil process.
  • the oil volume drained from the pump increases along with increasing rotate speed of rotor 13 , each enclosure chamber completes twice oil absorbing and draining processes as the pump shaft 17 rotates each cycle.
  • the drained oil is controlled through a flow securing control valve 4 and a throttle so that maintains the oil volume drained from oil outlet hole at a substantially constant value.
  • the flow rate proceeding to increase with the increasing rotate speed promotes differential pressure of the oil drained through the throttle also increased, pushing the flow securing control valve 4 toward right, chamber A (front outlet cavity) is communicated with chamber B (the oil return passage) to form overflow therebetween so that controls excess oil flow back into the oil inlet hole.
  • chamber A front outlet cavity
  • chamber B the oil return passage
  • the pump body 3 is utilized in a front high-pressure cavity configuration, wherein the high-pressure oil passage 21 is nearby the oil outlet channel 20 , allowing for with simple and widen passage, low corner bending, further smoothly high-pressure oil flowing, reducing the pressure loss of flow, as well as promoting the steering pump on work in normal parameters, and improving the stability of the system. Meanwhile, and the quantities of holes required for processing, with simplified processing method, shortened processing period, and less manufacturing equipments, cutting and measuring tools, of the high-pressure flow passage within the pump body 3 is less than the conventional pump body in prior art, which hence can reduce the production cost and suitable for batch production.
  • the valve seat 8 in the valve assembly is utilized in dual-layer strainer configuration, wherein the outer-layer strainer of said dual-layer strainer has 60 mesh with diameter ⁇ 0.18, inner-layer strainer of said dual-layer strainer with more dense screens has 120 mesh with diameter ⁇ 0.06.
  • Both strainers are outward arc bulge configuration with preferred filtering effect. Under the high-pressure oil impact, impurities 22 cannot rest on the top portion of said arc configuration, thereby avoiding blocking the pump, or clogging in the conical valve of the valve body caused by the impurities entering therein, even not changing direction or difficult steering, and aggravating the aging of the steering pump.
  • the oil return passage within the pump body is drilled incline to the direction of the valve bore 27 (the direction indicated as the arrow delineated in the diagram), wherein opening of the oil return passage within the valve bore represents an ellipse shape 26 .
  • the high-pressure oil pushes the valve to move for a short displacement, in the same conditions, the exposed area 25 is larger than the circular hole to achieve higher efficiency of overflow and is difficult to cause excessive overheating or pressure loss problem.
  • the performance parameters of the power steering pump with front high-pressure cooling cavity of the present invention are:

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US13/717,180 2011-12-29 2012-12-17 Power steering pump Abandoned US20130170959A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201110451942.8A CN102536802B (zh) 2011-12-29 2011-12-29 转向助力泵
CN201110451942.8 2011-12-29

Publications (1)

Publication Number Publication Date
US20130170959A1 true US20130170959A1 (en) 2013-07-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
US13/717,180 Abandoned US20130170959A1 (en) 2011-12-29 2012-12-17 Power steering pump

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US (1) US20130170959A1 (de)
CN (1) CN102536802B (de)
DE (1) DE202012104802U1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109237026A (zh) * 2018-11-08 2019-01-18 周琦人 空气压缩机轴端减压密封结构
US20190249674A1 (en) * 2018-01-31 2019-08-15 Gp Enterprises Co., Ltd Combined sump pump with a backup pump structure

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102979727B (zh) * 2012-12-11 2014-01-01 全兴精工集团有限公司 一种载重汽车用耐磨轻型转向叶片泵
CN102996437B (zh) * 2012-12-11 2014-01-29 全兴精工集团有限公司 一种重卡载货汽车转向油泵
CN103147979B (zh) * 2013-02-28 2016-03-16 奇瑞汽车股份有限公司 一种动力转向泵
CN109649485B (zh) * 2019-01-15 2024-04-09 烟台利通液压技术有限公司 一种车用电动液压助力转向泵总成
CN113565757B (zh) * 2021-07-01 2022-04-19 燕山大学 一种多级压排多输出泵
CN114135482B (zh) * 2021-11-29 2023-11-24 涌镇液压机械（上海）有限公司 无轴心摆线齿轮泵

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
UST927009I4 (en) * 1973-10-23 1974-10-01 Plgi i pq
US3977190A (en) * 1974-05-07 1976-08-31 Aisin Seiki Kabushiki Kaisha Pump speed detecting device
US4014630A (en) * 1974-06-03 1977-03-29 Trw Inc. Power steering pump
US4479764A (en) * 1983-03-09 1984-10-30 General Motors Corporation Demand responsive hydraulic pump
US4560329A (en) * 1983-10-20 1985-12-24 Mitsubishi Denki Kabushiki Kaisha Strainer device for rotary compressor
US5562758A (en) * 1995-02-24 1996-10-08 Awaji; Toshio Method of removing fine particle dust and apparatus therefor
US5567125A (en) * 1995-01-06 1996-10-22 Trw Inc. Pump assembly with tubular bypass liner with at least one projection
US20060073027A1 (en) * 2004-10-06 2006-04-06 Norikazu Ide Vane pump
US20070148029A1 (en) * 2005-12-26 2007-06-28 Hitachi, Ltd. Variable displacement vane pump

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57193791A (en) * 1981-05-25 1982-11-29 Jidosha Kiki Co Ltd Oil pump
CN101285471A (zh) * 2008-01-08 2008-10-15 郭羽 汽车转向助力泵
CN201763601U (zh) * 2010-07-21 2011-03-16 浙江恒隆万安泵业有限公司 一种新型卡车转向泵
CN201803621U (zh) * 2010-09-30 2011-04-20 濮阳市联众兴业化工有限公司 换热器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
UST927009I4 (en) * 1973-10-23 1974-10-01 Plgi i pq
US3977190A (en) * 1974-05-07 1976-08-31 Aisin Seiki Kabushiki Kaisha Pump speed detecting device
US4014630A (en) * 1974-06-03 1977-03-29 Trw Inc. Power steering pump
US4479764A (en) * 1983-03-09 1984-10-30 General Motors Corporation Demand responsive hydraulic pump
US4560329A (en) * 1983-10-20 1985-12-24 Mitsubishi Denki Kabushiki Kaisha Strainer device for rotary compressor
US5567125A (en) * 1995-01-06 1996-10-22 Trw Inc. Pump assembly with tubular bypass liner with at least one projection
US5562758A (en) * 1995-02-24 1996-10-08 Awaji; Toshio Method of removing fine particle dust and apparatus therefor
US20060073027A1 (en) * 2004-10-06 2006-04-06 Norikazu Ide Vane pump
US20070148029A1 (en) * 2005-12-26 2007-06-28 Hitachi, Ltd. Variable displacement vane pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190249674A1 (en) * 2018-01-31 2019-08-15 Gp Enterprises Co., Ltd Combined sump pump with a backup pump structure
CN109237026A (zh) * 2018-11-08 2019-01-18 周琦人 空气压缩机轴端减压密封结构

Also Published As

Publication number Publication date
CN102536802A (zh) 2012-07-04
CN102536802B (zh) 2014-02-12
DE202012104802U1 (de) 2013-01-23

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AS Assignment

Owner name: QUANXING MACHINING GROUP CO., LTD, CHINA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LIU, DONG;CHEN, JUN;WU, SHAOHUA;AND OTHERS;REEL/FRAME:029484/0195

Effective date: 20121129

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION