US20040247469A1 - Power-assisted steering pump - Google Patents

Power-assisted steering pump Download PDF

Info

Publication number
US20040247469A1
US20040247469A1 US10/489,566 US48956604A US2004247469A1 US 20040247469 A1 US20040247469 A1 US 20040247469A1 US 48956604 A US48956604 A US 48956604A US 2004247469 A1 US2004247469 A1 US 2004247469A1
Authority
US
United States
Prior art keywords
pump
throttle valve
recited
volumetric flow
valve
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
US10/489,566
Other languages
English (en)
Inventor
Axel Fassbender
Hans-Juergen Lauth
Doan Nguyen
Karl Prinzhorn
Dirk Webert
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to LUK FAHRZEUG-HYDRAULIK GMBH & CO. KG reassignment LUK FAHRZEUG-HYDRAULIK GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LAUTH, HANS-JUERGEN, PRINZHORN, KARL, VAN NGUYEN, DOAN, WEBERT, DIRK, FASSBENDER, AXEL
Publication of US20040247469A1 publication Critical patent/US20040247469A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F04C14/24—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/062—Details, component parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D6/00—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits
    • B62D6/02—Arrangements for automatically controlling steering depending on driving conditions sensed and responded to, e.g. control circuits responsive only to vehicle speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1201—Rotational speed of the axis

Definitions

  • the present invention is directed to a pump, in particular to a power-assisted steering pump, having a flow-control valve, the flow-control valve including, inter alia, a hydraulic resistance, such as a primary throttle valve, and a control piston, the primary throttle valve being optionally constituted of a control pin and an annular orifice.
  • Flow-control valves are also known, which, in response to increasing engine speed, i.e., increasing motor vehicle speed, reduce the volumetric flow to the steering system, in order to give the driver a more direct steering sensation at high speeds.
  • Flow-control valves of this kind have, for example, a control pin having a conical end, which is positioned in an annular orifice.
  • the primary throttle valve made up of this control pin and the annular orifice, closes more and more, thereby reducing the volumetric flow streaming to the steering system.
  • the primary throttle valve made up of this control pin and the annular orifice, closes more and more, thereby reducing the volumetric flow streaming to the steering system.
  • no other ways to influence the volumetric flow are possible, and the volumetric flow output to the steering system is influenced virtually only by the pump speed.
  • a pump in particular a power-assisted steering pump, having a flow-control valve, the flow-control valve including, inter alia, a hydraulic resistance, such as a primary throttle valve, and a control piston, the primary throttle valve being optionally constituted of a control pin and an annular orifice, an electrically adjustable bypass throttle valve being configured in parallel to the primary throttle valve.
  • the volumetric flow from the pump to the consumer is able, in addition, to be electrically influenced.
  • the same differential pressure acts on the bypass throttle valve as does on the primary throttle valve.
  • One embodiment of the pump in accordance with the present invention is distinguished in that, in response to increasing drive current, the bypass throttle valve reduces the delivery rate from the pump to the consumer. In one other preferred specific embodiment, in response to increasing drive current of the bypass throttle valve, the delivery rate from the pump to the consumer is increased.
  • One embodiment is also preferred where the electrically adjustable bypass throttle valve is adaptable to series-produced pumps, so that flexible installation positions of the bypass throttle valve are possible, regardless of where the primary throttle valve provided on the flow-control valve is located in the pump.
  • This has the particular benefit that, depending on the installation situation of an existing pump in a particular engine compartment, the installation location of the additional bypass throttle valve is adaptable to these engine compartment conditions, without adversely affecting the main throttle valve situated in the flow-control valve, and thus the functioning of the flow-control valve.
  • One embodiment of the pump in accordance with the present invention is distinguished in that the primary throttle valve of the series-produced pump ensures the basic delivery rate of the volumetric flow for the steering system, above all in the fail-safe case, i.e., when, for example, the electrical power supply fails, and in that the electrically adjustable bypass throttle valve is used for additionally varying the delivery rate to the consumer as a function of various parameters.
  • the parameters which are supposed to influence the electrically adjustable bypass throttle valve include parameters such as driving speed, engine speed, cornering behavior, braking characteristics, vehicle stability, steering angle, steering-wheel angular velocity, wheel speeds or wheel slip.
  • FIG. 1 shows a hydraulic circuit plan of a pump in accordance with the present invention.
  • FIG. 2 illustrates the operating range of a pump in accordance with the present invention.
  • FIG. 3 depicts one structural design of a pump in accordance with the present invention.
  • FIG. 4 shows another structural design.
  • FIG. 5 likewise shows another design.
  • FIG. 6 is a schematic diagram of a method for determining the solenoid-current driving of the bypass throttle valve.
  • FIG. 1 A pump system in accordance with the present invention is shown in FIG. 1 in the form of a hydraulic circuit diagram.
  • a pump unit 1 is driven via a drive shaft 3 of a driving mechanism (not shown in greater detail here), such as a belt pulley, by a combustion engine.
  • a driving mechanism such as a belt pulley
  • pump 1 delivers a volumetric flow into interconnection point 5 .
  • a connecting line 7 leads to a variable primary throttle valve 9 , illustrated by a throttle symbol and an arrow, a further connecting line 11 leads to a control piston of a control valve 13 , and a third connecting line 15 leads to an electrically adjustable bypass throttle valve 17 .
  • Connecting line 11 leads to an interconnection point 19 , from where a connecting line 21 leads to the control piston of control valve 13 , while a control line 23 acts on the left side of the control piston. Pressure P 1 prevailing at the pump output acts in control line 23 and is likewise active via interconnection point 5 in connecting lines 15 , 7 , 11 and 21 .
  • a volumetric flow may stream by way of connecting line 25 to interconnection point 27 , into which a connecting line 29 from electrically adjustable bypass throttle valve 17 also leads.
  • a connecting line 31 leads to a throttle valve 33 and continues via a connecting line 35 to an interconnection point 37 , where a control line 39 acts on the right side of the control piston.
  • a spring 41 acts on the right side of the control piston of control valve 13 .
  • a control line 43 continues to a pressure-limiting pilot valve 45 and via a line 47 to an interconnection point 49 into which outlet line 51 of control valve 13 flows.
  • an injector device 53 in which the oil flows streaming from the flow-control valve and pressure-limiting valve may entrain oil from a reservoir line 55 , the oil flowing off from flow-control valve 13 and/or from pressure-limiting pilot valve 45 flows again via pump suction line 57 into pump unit 1 .
  • a volumetric flow is increased via primary throttle valve 9 , to consumer 59 , such as to a power-assisted steering system.
  • pressure difference P 1 minus P 2 increases at the primary throttle valve.
  • pressure difference P 1 minus P 2 which, together with spring 41 , acts on the control piston of control valve 13 , becomes so great that pressure P 1 is able to displace control piston against pressure P 2 and adjust spring 41 to the right, enabling a volumetric flow to flow off over the control piston and be supplied, in turn, to suction side 57 of pump 1 .
  • control piston 13 is linked via a mechanical connection 61 to variable primary throttle valve 9 , in response to an increasing opening movement of piston 13 , variable primary throttle valve 9 continues to close, so that with increasing pump speed, a volumetric flow streaming toward the consumer is reduced.
  • the volumetric flow streaming toward consumer 59 is predetermined by the particular mechanical conditions of control valve 13 and of adjustable primary throttle valve 9 , and is not able to be changed further.
  • the present invention utilizes electrically adjustable bypass throttle valve 17 , which, in response to increasing drive current on a solenoid 63 , is able to continuously push up the piston of the bypass throttle valve against a spring force 65 , and thus render possible an additional volumetric flow into nodal point 27 and thus to consumer 59 .
  • a volumetric-flow characteristics map is feasible independently of the particular mechanical conditions of the control piston of control valve 13 and of primary throttle valve 9 .
  • FIG. 2 illustrates the bandwidth of such a volumetric-flow characteristics map.
  • the regulated delivery rate to consumer 59 in l/min, here between 0 and 10 l/min, is plotted over the pump speed in rpm, here from 0 to 6000 revolutions.
  • a delivery-rate operating-range band 100 is discernible, which, at about 600 rpm, exhibits an average volumetric flow of 4.5 l/min. In response to an increasing speed of up to 6,000 rpm, it falls to an average volumetric flow of 2 l/min.
  • This volumetric-flow band corresponds, for example, to the volumetric flow which is adjusted by the control piston of control valve 13 and variable primary throttle valve 9 , the intention being for the bandwidth to include all additional tolerances in the system.
  • operating-range band 101 in FIG. 2 With, at approximately 1,000 rpm, 8 l/min are realizable, which, at 6,000 rpm, are reduced by variable primary throttle valve 9 to about 6.5 l/min.
  • the continuously variable primary throttle valve 17 makes all characteristic curves between characteristic curves 100 and 101 feasible.
  • a high volumetric flow may be provided, which is lowered at a high driving speed, in order to produce a more direct sensation of the steering-wheel forces at the steering wheel.
  • a delivery-rate characteristic curve for the steering system may be adjusted in the same manner in accordance with other vehicle parameters, as well, such as cornering speed, braking characteristics, wheel slip, etc. It is equally possible for the high volumetric flow initially required for parking to be lowered by the variable primary throttle valve relatively quickly to a minimal volumetric flow, thereby adding to energy savings.
  • variable primary throttle valve 9 ensures the basic pump delivery rate.
  • various speed-dependent characteristic curves of the basic delivery rate may be realized by the control pin, which is mechanically linked to the control piston of control valve 13 .
  • the pump delivery rate may be varied, in addition, by electrically adjustable bypass throttle valve 17 , which is connected in parallel to primary throttle valve 9 and is acted upon by same differential pressure P 1 minus P 2 .
  • bypass throttle valve 17 may reduce or increase the delivery rate of pump 1 to consumer 59 . Therefore, with regard to the fail-safe performance of a pump device of this kind, it is also beneficial that mechanical primary throttle valve 9 continues to function should the electrical power supply fail. This is not so readily feasible when a purely electrically adjustable primary throttle valve is used.
  • FIG. 3 depicts the structural adaptation of a variable primary throttle of this kind to a series-produced pump housing.
  • Electrically operable bypass throttle valve 201 is mounted via a fitting 203 on a cover 205 of a series-produced power-assisted steering pump.
  • Cover 205 seals a pump housing 207 , in which the flow-control valve, present till now, and the variable primary throttle valve (which are not visible here) are located in a valve housing 209 .
  • the volumetric inflow to the consumer is provided by a port 211 at the pump, and the return flow from the consumer and the reservoir by port 213 .
  • the position of electrical valve 201 may be varied in a number of ways, without altering the other structural conditions of the pump or even of the vehicle.
  • FIG. 4 illustrates how such an electrical bypass throttle valve is adapted to another type of series-produced pump.
  • electrical bypass throttle valve 201 is mounted on pump housing 207 above flow-control valve housing 209 , resulting in a vertical attachment in conformance with the installation conditions of this pump.
  • the pressure connection to consumer 211 and the suction connection of pump 213 are configured in other positions, so that an available place for positioning the bypass throttle valve may be found in a different way, in conformance with these conditions and the space requirements in the vehicle.
  • FIG. 5 shows the same pump type as in FIG. 4, including an axial attachment of electrical bypass throttle valve 201 .
  • the space behind the pump may be used for adapting solenoid valve 201 , when no space is available in the areas around valve housing 209 , at suction side 213 or at pressure-outlet side 211 .
  • solenoid valve 201 when no space is available in the areas around valve housing 209 , at suction side 213 or at pressure-outlet side 211 .
  • FIG. 6 shows a schematic diagram of a method for determining the solenoid-current driving of bypass throttle valve 201 .
  • an electronic computer device determines the solenoid current on the basis of a plurality of input variables, and a solenoid current is output accordingly.
  • Input variables used for the algorithm for determining the solenoid current include driving speed 301 , steering-wheel angular velocity 303 , engine speed 305 of the combustion engine, and steering angle 307 .
  • Steering-wheel angular velocity 303 is generated by a functional unit as a first input variable for a characteristics map 309 .
  • Vehicle speed 301 is used as a second input variable for characteristics map 309 .
  • a valve-opening value is mapped in characteristics map 309 as a function of vehicle speed 301 and steering-wheel angular velocity 303 .
  • Characteristics map 309 is used, in turn, as first input variable for a second characteristics map 311 , which processes engine speed 305 as a second input variable.
  • a valve-opening value is mapped as a function of characteristics map 309 and of combustion-engine speed 305 .
  • Second characteristics map 311 is used, in turn, as first input variable for a functional unit 315 , for which a characteristic curve 313 is used as second input variable.
  • Characteristic curve 313 is generated from steering-angle signal 307 and constitutes a valve-opening value as a function of steering angle 307 .
  • the output variable of functional unit 315 is the input variable for a functional unit 317 in which the solenoid-current characteristic curve is generated for solenoid current 319 of bypass throttle valve 201 as a function of the valve-opening value. Solenoid current 319 is then made available to the solenoid of bypass throttle valve 201 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Transportation (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Power Steering Mechanism (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Magnetically Actuated Valves (AREA)
  • Rotary Pumps (AREA)
US10/489,566 2001-09-13 2002-09-11 Power-assisted steering pump Abandoned US20040247469A1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10145224 2001-09-13
DE10145224.1 2001-09-13
DE10157145 2001-11-22
DE10157145.3 2001-11-22
PCT/DE2002/003362 WO2003023227A1 (de) 2001-09-13 2002-09-11 Lenkhilpumpe

Publications (1)

Publication Number Publication Date
US20040247469A1 true US20040247469A1 (en) 2004-12-09

Family

ID=26010127

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/489,566 Abandoned US20040247469A1 (en) 2001-09-13 2002-09-11 Power-assisted steering pump

Country Status (9)

Country Link
US (1) US20040247469A1 (enExample)
EP (1) EP1427942B1 (enExample)
JP (1) JP2005502001A (enExample)
AT (1) ATE364137T1 (enExample)
DE (3) DE10294124D2 (enExample)
ES (1) ES2286288T3 (enExample)
FR (1) FR2829534B1 (enExample)
IT (1) ITMI20021945A1 (enExample)
WO (1) WO2003023227A1 (enExample)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040179950A1 (en) * 2003-03-11 2004-09-16 Denso Corporation Fuel supply pump capable of lubricating cam bearings
US20040197216A1 (en) * 2003-04-03 2004-10-07 Denso Corporation Fuel supply pump
EP3155265A4 (en) * 2014-06-13 2018-02-07 Clark Equipment Company Air compressor discharge system

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10311444A1 (de) * 2003-03-15 2004-09-23 Daimlerchrysler Ag Verfahren zum Betreiben einer Servolenkeinrichtung und Vorrichtung zur Durchführung des Verfahrens
JP2005112280A (ja) * 2003-10-10 2005-04-28 Kayaba Ind Co Ltd パワーステアリング装置
US7302798B2 (en) 2004-07-07 2007-12-04 Toyoda Koki Kabushiki Kaisha Hydraulic system, reservoir and pump suction enhancer for motor vehicle
DE102007036502A1 (de) * 2007-08-01 2009-02-05 Thyssenkrupp Presta Ag Druckleitung zur fluidischen Verbindung einer Pumpe zu einem hydraulischen Stellaggregat in einem Kraftfahrzeug

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4691797A (en) * 1986-07-10 1987-09-08 Trw Inc. Fluid flow control apparatus for a power steering system
US5111660A (en) * 1991-03-11 1992-05-12 Ford Motor Company Parallel flow electronically variable orifice for variable assist power steering system

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5818586A (ja) * 1981-07-27 1983-02-03 Jidosha Kiki Co Ltd 流量制御弁

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4691797A (en) * 1986-07-10 1987-09-08 Trw Inc. Fluid flow control apparatus for a power steering system
US5111660A (en) * 1991-03-11 1992-05-12 Ford Motor Company Parallel flow electronically variable orifice for variable assist power steering system

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040179950A1 (en) * 2003-03-11 2004-09-16 Denso Corporation Fuel supply pump capable of lubricating cam bearings
US7314351B2 (en) * 2003-03-11 2008-01-01 Denso Corporation Fuel supply pump capable of lubricating cam bearings
US20040197216A1 (en) * 2003-04-03 2004-10-07 Denso Corporation Fuel supply pump
US7377753B2 (en) * 2003-04-03 2008-05-27 Denso Corporation Fuel supply pump
EP3155265A4 (en) * 2014-06-13 2018-02-07 Clark Equipment Company Air compressor discharge system
US10378536B2 (en) 2014-06-13 2019-08-13 Clark Equipment Company Air compressor discharge system

Also Published As

Publication number Publication date
DE10294124D2 (de) 2004-07-29
ES2286288T3 (es) 2007-12-01
FR2829534A1 (fr) 2003-03-14
EP1427942A1 (de) 2004-06-16
ITMI20021945A1 (it) 2003-03-14
DE50210285D1 (de) 2007-07-19
DE10242040A1 (de) 2003-04-03
FR2829534B1 (fr) 2006-02-03
JP2005502001A (ja) 2005-01-20
EP1427942B1 (de) 2007-06-06
WO2003023227A1 (de) 2003-03-20
ATE364137T1 (de) 2007-06-15

Similar Documents

Publication Publication Date Title
US4798050A (en) Control system for hydraulic tandem pump in motor vehicle
US7100723B2 (en) Multiple pressure mode operation for hydraulic hybrid vehicle powertrain
EP1350930B2 (en) Variable displacement pump and control therefor
JP2503246B2 (ja) 油圧サスペションの油圧供給装置
US7841442B2 (en) Hydrostatic transmission
US20080184703A1 (en) Method for regulating a hydrostatic drive system
AU2021311138B2 (en) Hydraulic retarding control system
US4300650A (en) Multilevel power assisted steering
US6920753B2 (en) Magneto-electrohydraulic power steering system
US5124922A (en) System and method for controlling engine output to suppress slips on wheels applicable to automotive vehicle
US20040247469A1 (en) Power-assisted steering pump
US7022044B2 (en) Drive train for powering a mobile vehicle
JP2006022813A (ja) 自動二輪車の出力制御方法及び装置
KR101229173B1 (ko) 공급펌프
CN101022986B (zh) 转向助力系统
US20090159360A1 (en) Energy efficient power steering pump control system
JPH10510231A (ja) 自動車のための油圧式装置
US20190270480A1 (en) Apparatus and method for turning steerable vehicle wheels
JPH0781593A (ja) 動力舵取装置
US6003880A (en) Vehicle active tilt control system with pressure-controlled pump
EP0752361A1 (en) Flow control device
US20040003614A1 (en) Motor vehicle with an air-conditioning system
EP0802106A1 (en) Flow rate controller in power steering apparatus
JP3623105B2 (ja) 作業車の走行変速装置
CN2643028Y (zh) 汽车转向油泵

Legal Events

Date Code Title Description
AS Assignment

Owner name: LUK FAHRZEUG-HYDRAULIK GMBH & CO. KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:FASSBENDER, AXEL;LAUTH, HANS-JUERGEN;VAN NGUYEN, DOAN;AND OTHERS;REEL/FRAME:015305/0912;SIGNING DATES FROM 20040402 TO 20040419

STCB Information on status: application discontinuation

Free format text: ABANDONED -- AFTER EXAMINER'S ANSWER OR BOARD OF APPEALS DECISION