US20130019830A1 - Control valve having a curved spring band serving as a non-return valve - Google Patents

Control valve having a curved spring band serving as a non-return valve Download PDF

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Publication number
US20130019830A1
US20130019830A1 US13/637,397 US201113637397A US2013019830A1 US 20130019830 A1 US20130019830 A1 US 20130019830A1 US 201113637397 A US201113637397 A US 201113637397A US 2013019830 A1 US2013019830 A1 US 2013019830A1
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US
United States
Prior art keywords
spring band
valve
openings
control valve
groove
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
US13/637,397
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English (en)
Inventor
Jens Hoppe
Lars Buchmann
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HOPPE, JENS, BUCHMANN, LARS
Publication of US20130019830A1 publication Critical patent/US20130019830A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/14—Check valves with flexible valve members
    • F16K15/16—Check valves with flexible valve members with tongue-shaped laminae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves

Definitions

  • the invention relates to a control valve, in particular to a proportional valve for controlling a device for adjusting the rotational angle position of a camshaft with respect to a crankshaft of an internal combustion engine.
  • a control valve of this type has a valve housing which is of hollow-cylindrical design and is intended for receiving an axially displaceable control piston, the axial displacement of which causes a pressure medium connection to be connected to or disconnected from at least one working connection.
  • the outer circumferential side of the control piston has control edges which interact with valve housing openings arranged on the circumferential side.
  • Control valves of the abovementioned type are used, for example, for controlling a device for the rotational angle position of a camshaft with respect to a crankshaft of an internal combustion engine.
  • the camshaft serves to actuate the gas exchange valves, the opening or closing time of which is to be set depending on the current range of performance characteristics of the engine, in particular depending on the current rotational speed or load thereof, in order to optimize the engine efficiency.
  • the rotational angle position of the camshaft with respect to the crankshaft is adjusted via a device which is actuatable electrically, hydraulically or pneumatically.
  • the control valve provided in the present case is intended to be usable in particular for controlling such a hydraulically actuatable adjusting device.
  • EP 1 291 563 A2 discloses a control valve of the above-mentioned type having a non-return valve integrated in the valve housing.
  • the non-return valve consists of an annularly curved spring band which serves at the same time as a closing element and as a spring element.
  • the curved spring band is placed into an annular groove formed on the outer or inner circumferential side of the valve housing such that said spring band undergoes elastic deformation upon pressurization in the opening direction and opens up bores formed in the valve housing or in a sleeve surrounding the valve housing for the passage of an operating medium while said spring band resumes the original shape thereof and closes the bores upon pressurization in the closing direction.
  • the non-return valve serves to avoid the transmission of pressure pulsations which are operationally induced to arise in the camshaft adjuster and—without a non-return valve—could pass back via the working and pressure oil connections of the control valve into the pressure oil circuit. Since, as a rule, further components, in particular secondary components, such as chain adjusters, etc., are connected to the same pressurized oil circuit, back flow of the operating medium may result in damage to the further components. At the same time, the non-return valve serves to support pressure pulsations, thus increasing the torsional rigidity, i.e. the positional stability of the adjusting device.
  • control valve having a non-return valve in such a manner that a defined opening and closing of the non-return valve is ensured over the long term.
  • control valve is intended to be constructed in a simple manner and to be producible cost-effectively.
  • the valve housing which is of hollow-cylindrical design, of the proposed control valve has a plurality of openings which are arranged circumferentially in a radial plane and are closable via a non-return valve designed as a curved spring band.
  • the openings arranged in a radial plane are arranged at different angular distances from one another, and the shape and the rotational angle position of the curved spring band serving as the non-return valve are matched to said angular distances.
  • the different angular distances between the openings formed in the valve housing result in a non-rotationally-symmetrical arrangement of the openings and therefore in a non-rotationally-symmetrical design of the valve housing.
  • an arrangement of the openings at different angular distances from one another is also to be understood as meaning an arrangement in which only one angular distance is designed to be larger or smaller than the other angular distances.
  • one angular distance can be selected to be of a size such that a concentration of the openings occurs in a sector extending over a certain angular range while a further sector is optionally formed without openings.
  • the concentration of the openings on one side or in a certain sector region of the valve housing predetermines a preferred flow direction of the operating medium and therefore an orientation of the curved spring band, in which the spring band and the openings interact in an optimum manner. This has to apply in particular if—as provided—the shape and the rotational angle position of the curved spring band are furthermore matched to the asymmetrical arrangement of the openings. A high throughflow rate and a simultaneously small pressure drop can therefore be brought about even given a small opening stroke of the spring band.
  • the curved spring band serving as a non-return valve in order to match the shape of the spring band to the asymmetrical arrangement of the openings in the valve housing, provision is made, according to a preferred embodiment of the invention, for the curved spring band serving as a non-return valve to have an open oval shape. It is ensured by the open shape that the spring element can be sufficiently elastically deformed in order to produce an opening stroke.
  • the oval shape substantially predetermines an orientation of the spring band with respect to the openings formed in the valve housing. Furthermore, given an appropriate design of a spring band receptacle, the oval shape can be used for securing the rotational angle position of the spring band with respect to the valve housing, thus ensuring an optimum interaction of openings and spring band even over the long term.
  • the valve housing for receiving the curved spring band in the region of the openings has different wall thicknesses such that an at least partially encircling groove having a varying groove depth is formed on the outer or inner circumferential side of the valve housing.
  • the spring band is preferably arranged in the interior of the valve housing.
  • a groove into which the spring band can be placed is furthermore formed preferably on the inner circumferential side in the region of the openings.
  • the groove depth of the groove varies such that the groove base firstly rises, then drops.
  • the groove depth may also peter out entirely such that the groove base corresponds to the inner wall of the valve housing. The groove is then not of encircling design.
  • the valve housing preferably has an oval shape in cross section in the region of the groove in a manner corresponding to the shape of the spring band such that the latter bears in an encircling manner against the groove base.
  • the corresponding oval shape of the spring band and groove brings about a securing of the rotational angle position of the spring band.
  • the formation of a groove for receiving the spring band furthermore has the advantage that, due to the form-fitting connection, the axial position of the spring band is also secured.
  • the curved spring band serving as the non-return valve may also, however, be inserted into a groove on the outer circumferential side of the valve housing or into a groove on the inner circumferential side of a receiving bore of a camshaft or of a cylinder head and interact in a corresponding manner with the openings of the valve housing and/or with openings of the receiving bore.
  • the spring band is preferably placed into a groove, the groove depth of which varies in order to achieve an oval groove shape in the cross section of the valve housing or in the receiving bore, said groove shape being matched to the oval shape of the spring band.
  • the width of the groove, which is provided for receiving the spring band, in the valve housing substantially corresponds to the width of the spring band.
  • the axial position of the spring band is fixed.
  • this may also mean that the groove width is optionally selected to be slightly larger in order to facilitate the insertion of the spring band.
  • the spring band serves at the same time as a closing element and as a spring element.
  • the spring band therefore combines the functions of closing element and spring element in one component.
  • the opening and closing characteristics of the non-return valve are adjustable via the spring strength of the curved spring band.
  • the spring strength is predetermined in particular by the hinge strength of the spring band.
  • the hinge strength may also be varied, for example, over the circumference of the curved spring band.
  • the pressure medium connection P is advantageously designed as an at least partially encircling groove arranged on the outer circumferential side of the valve housing.
  • the groove may be designed as an annular groove.
  • further annular grooves may be arranged on the outer circumferential side of the valve housing, said annular grooves forming further connections, for example the working connections A and B.
  • FIG. 1 shows a side view and a top view of a curved spring band of a control valve according to the invention
  • FIG. 2 shows a longitudinal section and a cross section through a valve housing of a control valve according to the invention
  • FIG. 3 shows a longitudinal section through the valve housing of FIG. 2 with the spring band inserted upon pressurization in the opening direction
  • FIG. 4 shows a longitudinal section through the valve housing of FIG. 2 with the spring band inserted upon pressurization in the closing direction.
  • FIGS. 1 and 2 show the essential elements of a control valve according to the invention, namely a spring band 3 usable as a non-return valve 4 , and a valve housing 1 , each in an individual illustration.
  • the spring band 3 is inserted into a groove 5 formed on the inner circumferential side of the valve housing 1 such that the spring band 3 bears against the groove base of the groove 5 under a certain radial prestress.
  • the spring band 3 usable as the non-return valve 4 is curved to form an oval shape such that the ends of the spring band 3 are spaced apart from each other. The distance between the ends or the opening of the oval shape ensures that the spring band 3 is elastically deformable within the groove 5 .
  • the width of the spring band 3 is constant and is matched to the width of the groove 5 .
  • an ovally shaped groove 5 is formed in a manner corresponding to the oval shape of the spring element 3 on the inner circumferential side of the valve housing 1 (see cross section of the valve housing) in the region of openings 2 which serve to hydraulically connect a pressure medium connection P, which is designed as an encircling groove 6 , to working connections A and B.
  • the openings 2 are arranged circumferentially at different angular distances from one another in such a manner that the groove 5 does not have any openings 2 over a certain angular range.
  • a main flow direction of the operating medium is therefore predetermined, said flow direction, together with the shape of the groove 5 , predetermining a certain orientation of the spring band 3 . This ensures optimum interaction of openings 2 and spring band 3 .
  • the groove 5 secures the installed position of the spring band 3 against axial displacement and against rotation.
  • the spring band 3 Upon pressurization of the spring band 3 in the opening direction (see FIG. 3 ) by operating medium being supplied via the pressure medium connection P, the spring band 3 is pressed radially inward, wherein said spring band undergoes elastic deformation and opens up the openings 2 . Even at a small opening stroke of the spring band 3 , a high throughflow rate can be obtained with little pressure drop, i.e. low losses, since the arrangement of the openings 2 is concentrated on the region about the pressure medium connection or the port P.
  • the operating medium passes via the opened-up openings 2 to further openings 7 which serve for the hydraulic connection to a working connection A or B, said working connections being designed as an annular groove corresponding to the pressure medium connection P.
  • the pressure ratios are such that the spring band 3 is acted upon in the closing direction by a pressure force which is greater than the prevailing operating pressure, for example due to pressure pulsations, the operating medium can flow back via the working connections A or B, and the spring band 3 is placed against the base of the groove 5 again and thereby closes the openings 2 formed in the groove 5 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Check Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Springs (AREA)
US13/637,397 2010-04-26 2011-04-05 Control valve having a curved spring band serving as a non-return valve Abandoned US20130019830A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010018200A DE102010018200A1 (de) 2010-04-26 2010-04-26 Steuerventil, insbesondere Proportionalventil
DE102010018200.1 2010-04-26
PCT/EP2011/055231 WO2011134750A1 (de) 2010-04-26 2011-04-05 Steuerventil mit einem als rückschlagventil dienenden gebogenen federbandes

Publications (1)

Publication Number Publication Date
US20130019830A1 true US20130019830A1 (en) 2013-01-24

Family

ID=44140688

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/637,397 Abandoned US20130019830A1 (en) 2010-04-26 2011-04-05 Control valve having a curved spring band serving as a non-return valve

Country Status (5)

Country Link
US (1) US20130019830A1 (de)
EP (1) EP2564039B1 (de)
CN (1) CN102859128B (de)
DE (1) DE102010018200A1 (de)
WO (1) WO2011134750A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104454062A (zh) * 2014-12-01 2015-03-25 绵阳富临精工机械股份有限公司 一种用于机油控制阀的带限位机构的单向阀
EP3219941A1 (de) * 2016-03-14 2017-09-20 ECO Holding 1 GmbH Hydraulikventil für einen schwenkmotorversteller einer nockenwelle
US20180164979A1 (en) * 2014-09-06 2018-06-14 Airwatch Llc Collaboration for network-shared documents
US20180298791A1 (en) * 2017-04-13 2018-10-18 Schaeffler Technologies AG & Co. KG Pressure medium supply to valve train elements
US10358953B2 (en) * 2015-07-20 2019-07-23 Delphia Automotive Systems Luxembourg Sa Valve

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011087664B4 (de) * 2011-12-02 2014-03-20 Continental Automotive Gmbh Ventilanordnung
DE102015208453B3 (de) * 2015-05-07 2016-06-30 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Rückschlagventilen am Volumenspeicher
DE102017106987A1 (de) 2016-07-08 2018-01-11 ECO Holding 1 GmbH Rückschlagventil für ein Pleuel für eine Brennkraftmaschine mit variabler Verdichtung
EP3267012B1 (de) * 2016-07-08 2019-09-18 ECO Holding 1 GmbH Rückschlagventil für einen pleuel für eine brennkraftmaschine mit variabler verdichtung
JP6690633B2 (ja) * 2017-01-19 2020-04-28 株式会社デンソー バルブタイミング調整装置およびチェック弁

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US1860163A (en) * 1930-04-21 1932-05-24 Binks Mfg Co Valve assembly for air-compressing cylinders
US3882891A (en) * 1974-06-19 1975-05-13 Abex Corp Check valve
US6318979B1 (en) * 1999-04-22 2001-11-20 Robert Bosch Gmbh Piston pump
US20030070713A1 (en) * 2001-09-05 2003-04-17 Hydraulik-Ring Gmbh Check valve and valve arrangement comprising such a check valve
US20060225791A1 (en) * 2005-03-18 2006-10-12 Hydraulik-Ring Gmbh Valve with check valve
US7240768B2 (en) * 2002-10-24 2007-07-10 Barnes Group Inc. Flapper finger valve
US20080271689A1 (en) * 2005-06-22 2008-11-06 Schaeffler Kg Control Valve for a Device for Variably Adjusting the Valve Timing for Gas Exchange Valves in an Internal Combustion Engine
US20120152195A1 (en) * 2010-12-20 2012-06-21 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster
US8225818B1 (en) * 2011-03-22 2012-07-24 Incova Technologies, Inc. Hydraulic valve arrangement with an annular check valve element
US8316889B2 (en) * 2006-05-13 2012-11-27 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster
US8505582B2 (en) * 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve

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DE3829698A1 (de) * 1987-09-05 1989-03-16 Zahnradfabrik Friedrichshafen Kolbenpumpe, insbesondere radialkolbenpumpe
US7000580B1 (en) * 2004-09-28 2006-02-21 Borgwarner Inc. Control valves with integrated check valves
GB0616966D0 (en) * 2006-08-29 2006-10-04 Delphi Tech Inc Oil control valve
GB0618648D0 (en) * 2006-09-22 2006-11-01 Delphi Tech Inc Oil control valve

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1860163A (en) * 1930-04-21 1932-05-24 Binks Mfg Co Valve assembly for air-compressing cylinders
US3882891A (en) * 1974-06-19 1975-05-13 Abex Corp Check valve
US6318979B1 (en) * 1999-04-22 2001-11-20 Robert Bosch Gmbh Piston pump
US20030070713A1 (en) * 2001-09-05 2003-04-17 Hydraulik-Ring Gmbh Check valve and valve arrangement comprising such a check valve
US6899126B2 (en) * 2001-09-05 2005-05-31 Hydraulik-Ring Gmbh Check valve and valve arrangement comprising such a check valve
US7240768B2 (en) * 2002-10-24 2007-07-10 Barnes Group Inc. Flapper finger valve
US20060225791A1 (en) * 2005-03-18 2006-10-12 Hydraulik-Ring Gmbh Valve with check valve
US20080271689A1 (en) * 2005-06-22 2008-11-06 Schaeffler Kg Control Valve for a Device for Variably Adjusting the Valve Timing for Gas Exchange Valves in an Internal Combustion Engine
US8316889B2 (en) * 2006-05-13 2012-11-27 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster
US8505582B2 (en) * 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US20120152195A1 (en) * 2010-12-20 2012-06-21 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster
US8225818B1 (en) * 2011-03-22 2012-07-24 Incova Technologies, Inc. Hydraulic valve arrangement with an annular check valve element

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180164979A1 (en) * 2014-09-06 2018-06-14 Airwatch Llc Collaboration for network-shared documents
CN104454062A (zh) * 2014-12-01 2015-03-25 绵阳富临精工机械股份有限公司 一种用于机油控制阀的带限位机构的单向阀
US10358953B2 (en) * 2015-07-20 2019-07-23 Delphia Automotive Systems Luxembourg Sa Valve
EP3219941A1 (de) * 2016-03-14 2017-09-20 ECO Holding 1 GmbH Hydraulikventil für einen schwenkmotorversteller einer nockenwelle
US10605127B2 (en) 2016-03-14 2020-03-31 ECO Holding 1 GmbH Hydraulic valve for a cam phaser
US20180298791A1 (en) * 2017-04-13 2018-10-18 Schaeffler Technologies AG & Co. KG Pressure medium supply to valve train elements
US10774695B2 (en) * 2017-04-13 2020-09-15 Schaeffler Technologies AG & Co. KG Pressure medium supply to valve train elements

Also Published As

Publication number Publication date
EP2564039B1 (de) 2017-08-02
CN102859128B (zh) 2015-07-15
DE102010018200A1 (de) 2011-10-27
WO2011134750A1 (de) 2011-11-03
EP2564039A1 (de) 2013-03-06
CN102859128A (zh) 2013-01-02

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Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HOPPE, JENS;BUCHMANN, LARS;SIGNING DATES FROM 20120916 TO 20120917;REEL/FRAME:029028/0328

STCB Information on status: application discontinuation

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