EP1674729A2 - Pompe - Google Patents

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Publication number
EP1674729A2
EP1674729A2 EP05027802A EP05027802A EP1674729A2 EP 1674729 A2 EP1674729 A2 EP 1674729A2 EP 05027802 A EP05027802 A EP 05027802A EP 05027802 A EP05027802 A EP 05027802A EP 1674729 A2 EP1674729 A2 EP 1674729A2
Authority
EP
European Patent Office
Prior art keywords
working oil
choke
pump
passage
flow rate
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.)
Withdrawn
Application number
EP05027802A
Other languages
German (de)
English (en)
Other versions
EP1674729A3 (fr
Inventor
Tomoyuki c/o Kayaba Industry Co. Ltd. Fujita
Masamichi c/o Kayaba Industry Co. Ltd. Sugihara
Yoshinobu c/o Kayaba Industry Co. Ltd. Yasue
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.)
KYB Corp
Original Assignee
Kayaba Industry 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 Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Publication of EP1674729A2 publication Critical patent/EP1674729A2/fr
Publication of EP1674729A3 publication Critical patent/EP1674729A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/50—Conditions before a throttle
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/52—Conditions after a throttle
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/70—Safety, emergency conditions or requirements
    • F04C2270/701—Cold start

Definitions

  • This invention relates to flow control of a fixed capacity pump used for example in the power steering of a vehicle.
  • JPH09-170569A published by the Japan Patent Office in 1997 discloses a flow control valve for a fixed capacity pump that can be used in the power steering of a vehicle.
  • the flow control valve supplies working oil discharged from the fixed capacity pump to an actuator via a variable orifice.
  • the flow control valve is provided with a spool that displaces in response to a pressure loss in the orifice and, according to its displaced position, causes a part of the discharged working oil to flow into a recirculation passage.
  • Working oil that is sucked by the pump is supplied from a reservoir via a suction passage.
  • the recirculation passage recirculates working oil into the suction passage.
  • the orifice has a feature whereby the flow characteristic is constant irrespective of the temperature of the working oil that passes therethrough. For example, when the viscosity of the working oil is high due to low temperature, the pressure loss in the working oil passing through the orifice does not become very large with respect to the flow rate. On the other hand, when the viscosity of the working oil increases, frictional resistance in the suction passage inevitably increases, and the suction resistance of the pump increases.
  • the working oil recirculated from the recirculation passage is under a pushing force originating in the discharge pressure of the pump, and therefore the suction resistance of the pump when it sucks the recirculated working oil is small.
  • the pump suctions working oil from the reservoir via the suction passage it suffers a large suction resistance.
  • the entire suction resistance of the pump therefore depends on the ratio of the flow rate of the recirculated working oil to the flow rate of the working oil supplied from the reservoir.
  • this invention provides a pump device for supplying working oil to an actuator, comprising a fixed capacity pump, a choke through which working oil discharged by the pump flows, and a flow control valve which recirculates a part of the working oil discharged by the pump to a suction side of the pump, according to a pressure loss generated by the choke.
  • FIG. 1 is a hydraulic circuit diagram of a pump device according to this invention.
  • FIG. 2 is a longitudinal sectional view of a vane pump as a component of the pump device.
  • FIG. 3 is a longitudinal sectional view of a flow control valve according to this invention.
  • FIG. 4 is a diagram showing a result of an experiment performed by the inventors to test the effect of the working oil temperature on the flow characteristics of an orifice and a choke.
  • a pump device comprises a fixed capacity pump P and a flow control valve F enclosed in a casing C shown by a single dotted line.
  • the fixed capacity pump P is connected to a motive power source such as an internal combustion engine and, when driven by the motive power source, sucks work oil through a suction passage 1 formed in the casing C.
  • the suction passage 1 is connected, via an external conduit Rp, to a reservoir R disposed outside the casing C.
  • the fixed capacity pump P discharges pressurized work oil to a discharge passage 2 that is also formed in the casing C.
  • the discharge passage 2 is connected to an actuator A located outside the casing C.
  • a choke 21 is disposed in the discharge passage 2.
  • a branch passage 2b branches off from the discharge passage 2 at a position upstream of the choke 21.
  • the branch passage 2b is connected to an inlet port 4 of the flow control valve F.
  • the discharge passage 2 downstream of the choke 21 communicates with the actuator A and the discharge passage 2 upstream of the choke 21 communicates with the inlet port 4 of the flow control valve F via the branch passage 2b.
  • the flow control valve F comprises a spool 5, a control pressure chamber 6 and a spring chamber 7.
  • the control pressure chamber 6 and the spiring chamber 7 are separated by the spool 5.
  • the control pressure chamber 6 communicates with the branch passage 2b via the inlet port 4.
  • the spring chamber 7 communicates with the discharge passage 2 downstream of the choke 21 via a pilot passage 9.
  • a spring 8 is enclosed in the spring chamber 7.
  • the flow control valve F comprises a recirculation port 10.
  • the recirculation port 10 communicates with the control pressure chamber 6 according to displacement of the spool 5 toward the right hand side of the figure.
  • the recirculation port 10 communicates with the suction passage 1 via a recirculation passage 11 formed within the casing C.
  • the working oil pressure in the control pressure chamber 6 acts on the spool 5 as a thrust force from the left hand side of the figure.
  • the working oil pressure in the spring chamber 7 and the pressure of the spring 8 act on the spool 5 as a thrust force from the right hand side of the figure. Accordingly, the spool 5 displaces to a position where these two forces balance.
  • the opening of the recirculation port 10 depends on the balanced position of the spool 5.
  • the spool 5 displaces towards an opening increase direction of the recirculation port 10, i.e., towards the right hand side in the figure.
  • the spool 5 displaces towards an opening decrease direction of the recirculation port 10, i.e., towards the left hand side in the figure.
  • the recirculation passage 11 as the opening of the recirculation port 10 increases, the recirculation flow rate increases, and as the opening of the recirculation port 10 decreases, the recirculation flow rate decreases.
  • the flow rate Q4 of the oil that is sucked by the pump P from the reservoir R outside the casing C is represented by the following relation (3).
  • the casing C comprises a body 12 and a cover 14 that closes a bore 13 formed in the body 12.
  • the cam ring 16 accommodates a rotor 17 which is fixed to a rotation shaft 20.
  • the rotor 17 comprises plural vane grooves 18 formed in radial directions at equal angular intervals. In each vane groove 18, a vane 19 is accommodated so as to be free to protrude radially therefrom.
  • vanes 19 protrude from the vane grooves 18 as a result of centrifugal force and their protruding tips contact the inner circumference of the cam ring 16.
  • oil chambers are formed between adjacent vanes 19.
  • the rotation shaft 20 penetrates through the body 12 and connects to the motive power source such as an internal combustion engine outside the casing C.
  • the vanes that are in contact with the inner circumference of the cam ring 16 move forward and backward, and accordingly the oil chambers formed by the vanes and the inner circumference of the cam ring 16 expand and shrink.
  • the expansion and shrinkage of oil chambers take place simultaneously. More precisely, some oil chambers expand while others shrink.
  • the suction passage 1 is formed in the cover 14.
  • the suction passage 1 communicates with the expanding oil chambers and the discharge passage 2 communicates with the shrinking oil chambers through one or both of two side faces of the cam ring 16.
  • Each of the oil chambers sucks working oil from the suction passage 1 when it expands, or in other words, when it is in a suction stroke.
  • the suction passage 1 shrinks, or in other words when it is in a discharge stroke, it pressurizes the sucked working oil and discharges it to the discharge passage 2.
  • the branch passage 2b branches off from the discharge passage 2 as the discharge passage 2 extends toward the choke 21.
  • the branch passage 2b communicates with the control pressure chamber 6 via the inlet port 4.
  • this configuration in the circuit diagram has been drawn for the purpose of explanation.
  • the real construction is somewhat different as shown in FIG. 3.
  • the branch passage 2b shown in FIG. 1 is imaginary and in reality the discharge passage 2 directly communicates with the control pressure chamber 6 as shown in FIG. 3.
  • the working oil in the control pressure chamber 6 is separated into two oil streams by the spool 5, i.e., a stream to the actuator A via the choke 21, and a stream to the suction passage 1 via the recirculation port 10.
  • the branch passage 2b and the inlet port 4 are therefore not shown in FIG. 2 and FIG. 3.
  • This invention provides the choke 21 instead of an orifice in the discharge passage 2. Pressure loss caused by an orifice is not affected by the temperature of the working oil, or the viscosity thereof.
  • FIG. 4 shows an experimental result obtained by the inventors with respect to the effect of the temperature of working oil on the flow characteristics of an orifice and a choke.
  • the orifice and choke have a same diameter D and the flow path length L of the choke is set at 1.33 times of the diameter D.
  • the flow rate of the choke is highly affected by the temperature or the viscosity of the working oil and the differential pressure between the upstream and downstream sides of the choke significantly increases in a low temperature state at an identical flow rate.
  • a differential pressure between the upstream and downstream sides of an orifice is explained as a differential pressure of an orifice
  • a differential pressure between the upstream and downstream sides of a choke is explained as a differential pressure of a choke.
  • the discharge flow rate Q1 of the fixed capacity pump P is obtained as a product of a unit discharge volume and a rotation speed of the pump P.
  • the rotation speed of the fixed capacity pump P depends on the rotation speed of the motive power source such as an internal combustion engine.
  • the discharge flow rate Q1 of the fixed capacity pump P increases accordingly, even in a low temperature state. If the differential pressure of the orifice were large in this situation, the recirculation flow rate Q3 via the recirculation port 10 would increase, so the suction flow rate of the fixed capacity pump P would not suffer a shortage.
  • the differential pressure of the orifice is small even in a low temperature state, and so the flow rate Q2 of working oil supplied to the actuator A increases and the recirculation flow rate Q3 decreases relatively.
  • the suction resistance by the pump P is small, because the recirculated working oil is under the influence of a pushing force originating from the discharge pressure of the fixed capacity pump P.
  • the suction resistance of the fresh working oil supplied from the reservoir R is larger than the suction resistance of the recirculated working oil.
  • the suction flow rate of the fixed capacity pump P may not match the discharge flow rate thereof due to an excessively large suction resistance. This situation generates a negative pressure in the pump P which causes cavitation and generates noise.
  • This invention focuses attention on the temperature characteristics of an orifice and choke as shown in FIG. 4, and by the use of the choke 21 that generates a large differential pressure under low temperature, achieves a relative increase in the recirculation flow rate Q3 with respect to the flow rate Q4 of the working oil supplied from the reservoir R in a low temperature state.
  • the choke As follows. Both the choke and orifice generate pressure loss due to restriction of the flow area.
  • the choke denotes a narrow flow area with a long flow path length L
  • the orifice denotes a narrow flow area that has a short flow path length L .
  • the choke indicates a narrow flow path in which the pressure loss decreases as the working oil temperature increases and takes a constant value when the working oil temperature is above a predetermined temperature.
  • the fixed capacity pump P does not suffer from a shortage of work oil for suction, while the flow rate Q4 of the working oil sucked through the conduit Rp remains small.
  • the flow rate Q3 represents the flow rate of the working oil that recirculates through the recirculation passage 11 formed internally in the casing C, and so the pressure loss due to recirculation is small.
  • the flow characteristic of the choke is no longer affected by the viscosity of the oil.
  • the choke 21 functions in the same way as an orifice.
  • the suction resistance due to friction in the conduit Rp does not become very large.
  • the fixed capacity pump P can therefore suck an adequate amount of working oil without suffering a large suction resistance, and the working oil is supplied to the actuator A at a constant flow rate defined depending on the flow diameter D and flow path length L of the choke 21.
  • the fixed capacity pump does not suffer from an insufficient suction flow rate, and therefore cavitation or generation of noise is prevented from occurring even when the rotation speed of the motive power source increases in a low temperature state.
  • this invention is applied to a pump device wherein the fixed capacity pump P is connected to the reservoir R via the conduit Rp, but this invention may also be applied to a pump device wherein the fixed capacity pump is directly connected to the reservoir, not via a conduit.
  • the opening of the choke 21 is not limited to a circular shape.
  • the shape of the opening is polygonal, the diameter D of a circular opening that has the same cross-sectional area should be used to determine the flow path length L of the choke 21.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
EP05027802A 2004-12-22 2005-12-19 Pompe Withdrawn EP1674729A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004370463A JP2006177230A (ja) 2004-12-22 2004-12-22 ポンプ装置

Publications (2)

Publication Number Publication Date
EP1674729A2 true EP1674729A2 (fr) 2006-06-28
EP1674729A3 EP1674729A3 (fr) 2012-10-17

Family

ID=36096147

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05027802A Withdrawn EP1674729A3 (fr) 2004-12-22 2005-12-19 Pompe

Country Status (4)

Country Link
US (1) US20060222519A1 (fr)
EP (1) EP1674729A3 (fr)
JP (1) JP2006177230A (fr)
CN (1) CN1793651A (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2042737A3 (fr) * 2007-09-28 2013-12-04 Parker-Hannifin Corporation Système de récupération de pression

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2543365C2 (ru) * 2009-06-03 2015-02-27 Итон Корпорейшн Гидравлическое устройство с магнитными фиксирующими клапанами
JP5544904B2 (ja) * 2010-01-29 2014-07-09 株式会社ジェイテクト 流量制御装置
JP6393560B2 (ja) * 2014-08-29 2018-09-19 Ｋｙｂ株式会社 ポンプ装置
KR20160150161A (ko) * 2015-06-18 2016-12-29 현대자동차주식회사 전동식 오일펌프 소음 저감 방법

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2887060A (en) * 1953-06-22 1959-05-19 American Brake Shoe Co Variable volume pumping mechanism
US3632232A (en) * 1969-04-01 1972-01-04 Toyoda Machine Works Ltd Rotary pump
EP0045928A1 (fr) * 1980-08-11 1982-02-17 Vickers Incorporated Transmission de puissance
EP0505033A1 (fr) * 1991-03-11 1992-09-23 Ford Motor Company Limited Contrôle du débit sensible â la viscosité pour pompe hydraulique
JP2001073963A (ja) * 1999-08-31 2001-03-21 Kayaba Ind Co Ltd ベーンポンプの焼き付き防止構造

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58113892U (ja) * 1982-01-29 1983-08-03 三菱自動車工業株式会社 パワ−ステアリング用のオイルポンプ装置
JPH01178783A (ja) * 1987-12-29 1989-07-14 Nippon Denso Co Ltd 油圧アクチュエータ制御システム
JP3729525B2 (ja) * 1994-12-16 2005-12-21 ジヤトコ株式会社 可変容量型オイルポンプのライン圧制御装置
US5860797A (en) * 1995-04-04 1999-01-19 Aisin Seiki Kabushiki Kaisha Flow rate control device for a pump
JP3732884B2 (ja) * 1996-04-22 2006-01-11 株式会社ルネサステクノロジ 内部電源電圧発生回路、内部電圧発生回路および半導体装置
DE19652420A1 (de) * 1996-12-09 1998-06-10 Luk Fahrzeug Hydraulik Stromregelanordnung für eine hydraulische Fördereinrichtung
US5973356A (en) * 1997-07-08 1999-10-26 Micron Technology, Inc. Ultra high density flash memory
JP2000161246A (ja) * 1998-06-23 2000-06-13 Bosch Braking Systems Co Ltd オイルポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2887060A (en) * 1953-06-22 1959-05-19 American Brake Shoe Co Variable volume pumping mechanism
US3632232A (en) * 1969-04-01 1972-01-04 Toyoda Machine Works Ltd Rotary pump
EP0045928A1 (fr) * 1980-08-11 1982-02-17 Vickers Incorporated Transmission de puissance
EP0505033A1 (fr) * 1991-03-11 1992-09-23 Ford Motor Company Limited Contrôle du débit sensible â la viscosité pour pompe hydraulique
JP2001073963A (ja) * 1999-08-31 2001-03-21 Kayaba Ind Co Ltd ベーンポンプの焼き付き防止構造

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2042737A3 (fr) * 2007-09-28 2013-12-04 Parker-Hannifin Corporation Système de récupération de pression

Also Published As

Publication number Publication date
EP1674729A3 (fr) 2012-10-17
CN1793651A (zh) 2006-06-28
US20060222519A1 (en) 2006-10-05
JP2006177230A (ja) 2006-07-06

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