EP0902194A1 - Soupape à maintien de charge - Google Patents

Soupape à maintien de charge Download PDF

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Publication number
EP0902194A1
EP0902194A1 EP98109115A EP98109115A EP0902194A1 EP 0902194 A1 EP0902194 A1 EP 0902194A1 EP 98109115 A EP98109115 A EP 98109115A EP 98109115 A EP98109115 A EP 98109115A EP 0902194 A1 EP0902194 A1 EP 0902194A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure relief
load
seat
pressure
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.)
Granted
Application number
EP98109115A
Other languages
German (de)
English (en)
Other versions
EP0902194B1 (fr
Inventor
Martin Ing. Heusser
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH 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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP0902194A1 publication Critical patent/EP0902194A1/fr
Application granted granted Critical
Publication of EP0902194B1 publication Critical patent/EP0902194B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/008—Throttling member profiles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2562—Dividing and recombining
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/778—Axes of ports co-axial

Definitions

  • the invention relates to a load holding valve according to the preamble of claim 1.
  • load holding valves are known from prior use, in which the Pressure relief valve closing member is relieved of the pressure to be limited. It there is an essentially linear relationship between the one to be limited Pressure and the pilot pressure to open the pressure relief valve. Indeed is a shock function or damping function by the pressure relief valve not given, so that separate valve components must be provided for this.
  • a 1992 from a brochure by Oil-Control, Nonantola, IT, Page CM3, known load holding valve has one with the pressure relief valve closing member one-piece control piston, the pressure surface slightly is smaller than the cross-sectional area of the valve seat.
  • the pressure to be limited acts on the differential surface in the opening direction of the pressure relief valve to achieve a shock function or damping function in the event of pressure surges.
  • the valve seat is for the check valve function in a sleeve that can be moved against spring force shaped. Because the same valve components for the non-return and pressure limiting functions cooperate, the pressure relief valve closing element is opened moved relative to the valve seat while in the one flow direction while being held Pressure relief valve closing element of the valve seat against spring force is shifted. Both valve functions performed with the same valve components affect each other. In the check valve is because of the small construction Cross-section high dynamic pressure to accept. Under unfavorable operating conditions no leakage can be achieved.
  • the invention has for its object a load holding valve of the aforementioned Art to create that inexpensively with compact dimensions with high reliability is producible and despite the integrated shock-damping function under load one sensitive control of the consumer enables.
  • the one-piece design of the closing member with the control piston is favorable in terms of production and assembly technology.
  • the low back pressure of the pressure relief valve externally surrounding, structurally separate check valve Losses.
  • the functions of the check valve and the pressure relief valve do not interfere with each other.
  • the shooting link is partially relieved, i.e. the one to be limited Pressure only acts on the closing element in the opening direction for the shock-damping function sufficient size, but not on the entire cross-sectional area of the valve seat. This results in a favorable low tax ratio, the allows a high pilot pressure and precise and sensitive control of the consumer enables what to do with varying pressures with the consumer movement and instability to be feared is appropriate.
  • the hydraulic system responds with the load holding valve stiff and low-vibration.
  • the partial relief of the closing member is structurally simple the annular shoulder that reaches between the housing chamber and the Pilot chamber is positioned so that in the stroke of the check valve, its closing member is guided on the pressure relief valve closing member.
  • the seat valve tightness important for the load holding function is simple reached.
  • the result is between the cylinder guide and the cylindrical approach a slide function, in which the Control channels gradually open or close a variable cross-section depending on the stroke, spread the change in the passage cross-section over a large stroke range and prevent the pressure relief valve closing member from oscillating or e.g. in the event of a pressure surge after an opening stroke, the valve seat suddenly hits and causes vibrations in the system.
  • the quantity control device Pressure fluid does not suddenly flow out, but after a predetermined one Characteristic curve, opens and closes the pressure relief valve damped in the event of a pressure surge. This results in a damping behavior that has so far only been possible with additional complex Action was possible.
  • the closing member of the check valve works with the sealing surface unaffected by intensive flow dynamics in the pressure relief valve together.
  • the check valve holds reliably when the pressure relief valve is opened its shut-off position.
  • the pressure relief valve cannot supply any pressure medium bypass.
  • the additional control channels are alternatively of longitudinal grooves formed in the closing member to make changes in the flow cross-section to a large Distribute the stroke range of the closing element.
  • a particularly simple manufacture of the additional control channels is claimed 8 by grinding arch slots into the cylindrical longitudinal section of the closing link possible.
  • the longitudinal grooves can have different clear widths have.
  • the functional reliability is increased according to claim 11, if for each flow direction a sieve element is provided.
  • a hydraulic consumer V e.g. a double-acting hydraulic cylinder or hydraulic motor
  • a directional control valve W connected to a pump P and a tank T.
  • On a work line 1 is connected to the lower side of the consumer, while the Lifting side is connected to the directional control valve W via a working line 2.
  • a load holding valve L is provided between line sections 2a and 2b.
  • the Load holding valve L includes a check valve R that is in the first flow direction to consumer V opens and in the second flow direction to the directional control valve W locks automatically.
  • a pressure relief valve is located parallel to the check valve R. D provided that hydraulically from the working line 1 via a pilot line 3rd is controllable in the second direction of flow to the speed of the consumer V under load depending on the adjustment of the directional control valve W. Taxes.
  • a load is held by the load holding valve L.
  • the load is too lift, the directional control valve is adjusted to its left switching position, so that the Consumer V is applied via the working line 2 and the open check valve R. becomes.
  • Displaced pressure medium flows via the other working line 1 to Tank T.
  • the directional control valve W is in its right switching position switched.
  • Pressure built up in working line 1 acts via the pilot line 3 on the pressure relief valve D, which is opened and pressure medium flows out leaves.
  • Indicated by the pilot line at the pressure relief valve D is a partially relieved pressure relief valve, which is the load pressure in the line section 2b acted upon in the opening direction.
  • a shock or Damping function achieved during pressure surges in consumer V. Opens in the event of a pressure surge the pressure relief valve D and allows pressure medium to flow out at least briefly, to reduce the pressure surge and dampen vibrations in the system.
  • Fig. 2 is a closing member 4 of the pressure relief valve D in the manner of a cattail formed and provided with a conical seat 5, to which a cylindrical Approach 6 connects, which has a cylindrical longitudinal section 7 an annular shoulder 8 continues.
  • a control piston 9 is formed on the shoulder 8, which is connected to the pilot line 3 in a Pilot chamber 10 and a seal 11 is slidable.
  • a seat insert 13 is positioned, which the closing member 4th supports and on an underside sealing surface 15 for a plate-shaped check valve closing member 16 ending flow passages 14 contains.
  • the check valve closing member 16 is e.g. on the cylindrical longitudinal section 7 of the closing member 4 out and loaded by a weak closing spring 17, which is a bell-shaped Screen 18 holds on the closing member 16.
  • the lower part of the housing chamber 12 is connected to the line section 2b.
  • the upper part of the housing chamber 12 forms the connection to the line section 2a with a screw-in insert 23.
  • a suitably adjustable spring 22 is accommodated in the screw-in insert 23, which loads the closing member 4 downwards and determines at what pressure the pressure relief valve D opens.
  • a circular valve seat 19 is formed in the seat insert 13 and is in contact with the seat surface 5 of the closing member 4 cooperates in the manner of a seat valve (in the shown Shut-off position leak-free tightness).
  • Adjacent to the valve seat 19 is a cylindrical one Guide section 20 shaped, the slide-like with the cylindrical approach 6 of the locking member 4 works together (e.g. sliding fit).
  • the seat insert 13 is slightly enlarged inside, so the longitudinal section 7 slides smoothly.
  • the closing member 4 contains a chamber 24 which is connected to the lower one via connections 25 Part of the housing chamber 12 is connected, and additionally molded control channels K adjacent to the seat 5, for example radial bores 21 with different Diameters.
  • the contours of the radial bores 21 may overlap each other in the axial direction. With increasing distance from the seat 5, the radial bores 21 have increasing diameters.
  • the guide section 20 forms with the extension 6 and the control channels K.
  • Quantity control device M which is relative to the stroke of the closing member 4 relative to the valve seat 19 takes effect to control the amount.
  • In the seat insert 13 is in A further screen disk 26 is provided in the upper part of the housing chamber 12.
  • Control channels K to effect to pressure medium in a controlled amount from the line section 2b let in the line section 2a.
  • the duty ratio of the load holding valve should be greater than 1: 2.5, expediently are around 1: 3.
  • a pressure surge rises above the area difference between the valve seat 19 and the Seal 11, the closing member 4 against the spring 22 from the valve seat 19. It is dismantled or steamed.
  • the control channels K also participate in this as soon as the seat surface 5 has lifted off the valve seat 19. After the pressure surge has been reduced, the closing element sets 4 on the valve seat 19.
  • Fig. 3 (function as in Fig. 2), the quantity control device M is different from that shown in FIG.
  • the closing member 4 in Fig. 3 is in one piece with the control piston 9.
  • the longitudinal grooves 27 can be ground in with a grinding wheel, the diameter of which curvature and their strength determine the clear width of the longitudinal grooves 27.
  • It can several longitudinal grooves 27 of identical size and width distributed over the circumference and length can be molded, or also different widths or different lengths Longitudinal grooves 27.
  • the longitudinal grooves 27 end in the same axial area. It would be conceivable, as with the radial bores 21, for the ends of the longitudinal grooves 27 to be different position far from the seat 5.
  • the load holding valve of FIGS. 2 and 3 could be used with a larger control pistons can be combined in the pilot chamber 10.
  • valve seat 19 The area difference between the valve seat 19 and the seal 11 or the contact surface of the control piston 9 is matched to the application, i.e. the force or preload of the spring 22 and the pressure conditions in the system, such that the shock and damping function for pressure surges of a certain extent is achieved with which the pressure relief valve is independent of the control piston 9 opens briefly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Check Valves (AREA)
  • Safety Valves (AREA)
EP98109115A 1997-09-15 1998-05-19 Soupape à maintien de charge Expired - Lifetime EP0902194B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29716577U DE29716577U1 (de) 1997-09-15 1997-09-15 Lasthalteventil
DE29716577U 1997-09-15

Publications (2)

Publication Number Publication Date
EP0902194A1 true EP0902194A1 (fr) 1999-03-17
EP0902194B1 EP0902194B1 (fr) 2002-11-13

Family

ID=8046033

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98109115A Expired - Lifetime EP0902194B1 (fr) 1997-09-15 1998-05-19 Soupape à maintien de charge

Country Status (5)

Country Link
US (1) US5996466A (fr)
EP (1) EP0902194B1 (fr)
KR (1) KR100295425B1 (fr)
DE (2) DE29716577U1 (fr)
ES (1) ES2186046T3 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1063431A1 (fr) 1999-06-24 2000-12-27 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Soupape à maintien de charge
EP1344945A3 (fr) * 2002-03-14 2004-06-16 Howaldtswerke-Deutsche Werft Ag Combinaison de soupapes
CN105587701A (zh) * 2015-10-23 2016-05-18 上海立新液压有限公司 一种负载保持阀
DE102019218401B3 (de) * 2019-11-27 2021-04-01 Hawe Hydraulik Se Lasthalteventil, Lasthaltventilset und Verfahren zur Montage eines Lasthalteventils
DE102019218402A1 (de) * 2019-11-27 2021-05-27 Hawe Hydraulik Se Federdom für ein Hydraulikventil und Hydraulikventil mit einem solchen Federdom
CN112855640A (zh) * 2019-11-27 2021-05-28 哈威液压股份公司 阀锥、具有阀锥的负载保持阀及用于组装止回阀的方法
DE102022207208A1 (de) 2022-07-14 2024-01-25 Hawe Hydraulik Se Hydraulikventil

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2766525A1 (fr) * 1997-12-02 1999-01-29 Poclain Hydraulics Sa Circuit d'alimentation en fluide d'un recepteur equipe de moyens pour soumettre ce recepteur a une loi de pression
DE10261225B4 (de) * 2002-12-20 2006-11-16 Dorma Gmbh + Co. Kg Elektrohydraulischer Servotürantrieb zum Antrieb einer Tür, eines Fensters oder dergleichen
DE102004057375A1 (de) 2004-11-26 2006-06-08 Voith Turbo Gmbh & Co. Kg Kombinierte Entlastungs- und Schwallschutzvorrichtung für unter Druck setzbare Betriebsmittelbehälter in Betriebsmittelversorgungssystemen hydrodynamischer Maschinen
JP2006283785A (ja) * 2005-03-31 2006-10-19 Nabtesco Corp 油圧回路およびその弁装置
ITPR20090100A1 (it) * 2009-11-30 2011-06-01 Walvoil Spa Dispositivo di controllo del segnale di pressione di pilotaggio
DE102012011062A1 (de) * 2012-06-04 2013-12-05 Liebherr-France Sas Hydrauliksystem und Druckbegrenzungsventil
GB2524975A (en) * 2014-04-07 2015-10-14 Weatherford Uk Ltd Vent valve and method of use

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2559029A1 (de) * 1975-12-29 1977-07-07 Heilmeier & Weinlein Bremsventil
FR2362290A1 (fr) 1976-08-16 1978-03-17 Caterpillar Tractor Co Soupape de retenue de charge et de derivation
FR2388186A1 (fr) 1977-04-21 1978-11-17 Rexnord Inc Soupape pilote de blocage a fonctionnement hydraulique
EP0045206A1 (fr) 1980-07-29 1982-02-03 Fluid Controls, Inc. Soupape de réglage
GB2205385A (en) 1987-05-15 1988-12-07 Oil Control Spa Improvements in a load holding and control valve, in particular for hydraulic circuits with either open or closed centre directional control valve

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1765627A (en) * 1927-05-11 1930-06-24 French Oil Mill Machinery Hydraulic press and the like
US4223693A (en) * 1978-07-27 1980-09-23 Modular Controls Corporation Counterbalance valve
EP0197467B1 (fr) * 1985-04-11 1992-01-29 Beringer-Hydraulik AG Soupape de descente freinée et maintenu sans fuites.
US5133434A (en) * 1989-06-15 1992-07-28 Atsugi Unisia Corporation Variable damping force shock absorber with feature of independent adjustment of damping characteristics for bounding a rebounding strokes

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2559029A1 (de) * 1975-12-29 1977-07-07 Heilmeier & Weinlein Bremsventil
DE2559029C2 (de) 1975-12-29 1985-10-31 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München Bremsventil
FR2362290A1 (fr) 1976-08-16 1978-03-17 Caterpillar Tractor Co Soupape de retenue de charge et de derivation
FR2388186A1 (fr) 1977-04-21 1978-11-17 Rexnord Inc Soupape pilote de blocage a fonctionnement hydraulique
EP0045206A1 (fr) 1980-07-29 1982-02-03 Fluid Controls, Inc. Soupape de réglage
GB2205385A (en) 1987-05-15 1988-12-07 Oil Control Spa Improvements in a load holding and control valve, in particular for hydraulic circuits with either open or closed centre directional control valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"prospekt der fa. oil-control, nonantola, it", 1992, pages: CM3

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1063431A1 (fr) 1999-06-24 2000-12-27 HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG Soupape à maintien de charge
EP1344945A3 (fr) * 2002-03-14 2004-06-16 Howaldtswerke-Deutsche Werft Ag Combinaison de soupapes
CN105587701A (zh) * 2015-10-23 2016-05-18 上海立新液压有限公司 一种负载保持阀
DE102019218401B3 (de) * 2019-11-27 2021-04-01 Hawe Hydraulik Se Lasthalteventil, Lasthaltventilset und Verfahren zur Montage eines Lasthalteventils
DE102019218402A1 (de) * 2019-11-27 2021-05-27 Hawe Hydraulik Se Federdom für ein Hydraulikventil und Hydraulikventil mit einem solchen Federdom
CN112855640A (zh) * 2019-11-27 2021-05-28 哈威液压股份公司 阀锥、具有阀锥的负载保持阀及用于组装止回阀的方法
CN112855638A (zh) * 2019-11-27 2021-05-28 哈威液压股份公司 用于液压阀的弹簧罩及具有这种弹簧罩的液压阀
DE102019218402B4 (de) 2019-11-27 2022-09-22 Hawe Hydraulik Se Federdom für ein Hydraulikventil und Hydraulikventil mit einem solchen Federdom
CN112855640B (zh) * 2019-11-27 2023-04-18 哈威液压股份公司 阀锥、具有阀锥的负载保持阀及用于组装止回阀的方法
CN112855638B (zh) * 2019-11-27 2023-09-15 哈威液压股份公司 用于液压阀的弹簧罩及具有这种弹簧罩的液压阀
DE102022207208A1 (de) 2022-07-14 2024-01-25 Hawe Hydraulik Se Hydraulikventil

Also Published As

Publication number Publication date
DE59806260D1 (de) 2002-12-19
US5996466A (en) 1999-12-07
KR100295425B1 (ko) 2001-07-12
EP0902194B1 (fr) 2002-11-13
DE29716577U1 (de) 1997-11-13
KR19990029263A (ko) 1999-04-26
ES2186046T3 (es) 2003-05-01

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