EP1812738A1 - Soupape - Google Patents

Soupape

Info

Publication number
EP1812738A1
EP1812738A1 EP05801567A EP05801567A EP1812738A1 EP 1812738 A1 EP1812738 A1 EP 1812738A1 EP 05801567 A EP05801567 A EP 05801567A EP 05801567 A EP05801567 A EP 05801567A EP 1812738 A1 EP1812738 A1 EP 1812738A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
piston
control edge
valve according
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Withdrawn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
EP05801567A
Other languages
German (de)
English (en)
Inventor
Eric MÜLLER
Manfred Homm
Reinhard Stehr
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 Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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 LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP1812738A1 publication Critical patent/EP1812738A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0446—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces
    • F16K17/046—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with an obturating member having at least a component of their opening and closing motion not perpendicular to the closing faces the valve being of the gate valve type or the sliding valve type
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
    • 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

Definitions

  • the invention relates to a valve, in particular a pressure relief valve, with a piston with piston collars, which forms control edges with a piston bore / guide with inlet and outlet grooves.
  • valves are known.
  • the valve has for example a piston collar, which is acted upon on one side by a pilot pressure and on the other side of a pressure which prevails in a hydraulic main system. If the system pressure exceeds the pressure force of the pilot pressure by its pressure force, the piston collar begins to open, and a flow arises at the control edge which partially reduces the static pressures previously existing there in the closed state. This is also referred to as the action of a so-called flow force, which is physically generated by the now lacking static pressure force component. With increasing flow at the control edge further pressure force components in the opening direction are reduced by the flow, so that the Sys ⁇ temdruck must increase further to open the valve piston against the constant pilot pressure.
  • valve in particular pressure limiting valve, with a piston with piston collars, which forms with a piston bore / guide with inlet andesque ⁇ grooves control edges, wherein the valve has two control edges and a hydraulic resistance, which with one of the control edges is connected in series.
  • This has the advantage that increasing static pressure losses at the control edge in the case of flow, that is to say so-called flow forces, can be compensated for by an increasing dynamic pressure, which is generated by the resistance, on the valve piston.
  • a valve is preferred in which the hydraulic resistance is connected in series with the first control edge. Furthermore, a valve is preferred in which the hydraulic resistance of the first control edge is upstream or downstream in the flow direction.
  • An inventive valve is characterized in that the second control edge is switchable in the flow direction parallel to the first control edge. Also preferred is a valve in which the second control edge opens later in the direction of the opening movement than the first control edge.
  • An inventive valve is characterized in that the hydraulic resistance is designed as a diaphragm. This has the advantage that temperature influences on the hydraulic medium, which have the effect as viscosity changes of the medium, do not significantly influence the pressure drop occurring at the orifice.
  • Another valve is characterized in that the hydraulic resistance is designed as a throttle. As a result, temperature effects and thus the influence of viscosity for specific effects can be meaningfully exploited, if this is desired for the control strategy.
  • a valve is preferred which is designed as a slide valve. Also preferred is a valve which can be precontrolled by a pilot pressure. Also, a valve is preferred in which the piston collars have different sized Druckwirkflä ⁇ chen. This has the advantage that, for example, high system pressures can be regulated with a low pilot pressure.
  • FIG. 1 shows an embodiment of the pressure limiting valve according to the invention.
  • FIG. 2 shows the different effects of the static and dynamic pressure forces on the valve piston.
  • FIG. 3 shows the valve of FIG. 1 with both open control edges.
  • FIG. 4 shows a second embodiment of a pressure limiting valve according to the invention.
  • FIG. 5 shows an enlarged view of the control edge from FIG. 4 under the influence of flow forces.
  • Figure 6 shows the comparison of the pressure relief valve characteristics between a conventional pressure relief valve, the optimized pressure relief valve and an ideal pressure relief valve.
  • FIG. 1 shows an embodiment of the pressure limiting valve according to the invention.
  • a piston 3 with three piston collars 5, 7 and 9 ge leads.
  • the piston bore 1 is larger in diameter in the region 11 than in the region 13.
  • the piston collar 5 is larger in diameter than the piston collars 7 and 9.
  • a supply line 15 is divided within a valve housing not directly shown here in a first Zu ⁇ 17 and a second Inlet 19 in the form of circulation grooves on. If a system pressure prevails in the inlet 15, the system pressure at the piston collar 7 on the pressure-acting surface 21 and at the piston collar 9 on the pressure-acting surface 23 will cancel each other out in terms of force.
  • This opening force is acted upon by a pilot pressure, which acts via the feed 31 on the entire pressure-acting surface 29 of the larger piston collar 5, - A - compensated, so that a large pressure acting surface 29 with a low pilot pressure in the region of the supply 31 against a small differential area between the piston collar 27 and 25, acted upon by a higher system pressure, compensated.
  • Two outlet connections 33 and 35 of the valve reunite into a common outlet 37, wherein a hydraulic resistance 39, for example in the form of an orifice, is arranged behind the outlet 33.
  • This resistance 39 generates a back pressure in the area 33 when the control edge 41 of the piston collar 5 is opened and thereby flows through the resistor 39 in accordance with the throughflow.
  • the effects of this arrangement between the control edge 41 and the resistance 39 are shown in FIG described.
  • valve piston collar 5 is shown in Figure 1 in the closed state.
  • the control edge 41 of the Koibenbundes 5 has with the control edge 43 of a housing 45 ge a certain overlap and is thus closed.
  • an effective static pressure profile 47 results which effects a force in the opening direction of the piston by means of the system pressure. This opening force is kept in equilibrium by the pressure force of the pilot pressure on the piston surface 29, as described in FIG.
  • the function of the blanks 39 from FIG. 1 now comes into effect, as shown in FIG. 2c.
  • the resistance 39 generates a back pressure in the region 33 with increasing throughflow, which adds to the previous residual pressure profile 49 from FIG. 2b in the form of an additional pressure profile 53 and thus the opening pressure losses which occur in the flow according to FIG. 2b with respect to FIG. compensated.
  • the system pressure does not have to increase any further in order to allow the opening of the valve piston, since this is prevented by the additional back pressure of the aperture 39 is realized. Only when the opening of the control edges
  • FIG. 3 differs from FIG. 1 in that an opening is formed on the piston collar 7 between the control edge 55 of the piston collar 7 and the control edge 57 of the housing, which now permits a further volume flow via the inlet 19 parallel to the volume flow via the inlet 17 , All other functions also correspond to the functions as described in FIG. 1 and should not be mentioned again to avoid repetition.
  • the additional volume flow via the inlet 19 and the control edges 55, 57 into the outlet 35 does not flow through any resistance and thus does not generate any significant additional pressure increase, so that a low-resistance parallel volume flow to the volume flow mentioned in FIG.
  • FIG. 4 shows another embodiment of a pressure limiting valve according to the invention.
  • a constant on the outer diameter valve piston 60 is guided within a piston bore 62.
  • the piston 60 furthermore has a guide pin 64, which is guided in an inner axial piston bore 66.
  • the hydraulic medium passes under system pressure into the region 70 and via an opening 72 in the Kol ⁇ benbohrung 66 of the piston 60.
  • the hydraulic fluid From the piston bore 66 then the hydraulic fluid through a force acting as a resistance narrow bore 74 to a mounted in the piston STEU ⁇ 76 76, which cooperates with a control edge 78 of the housing, passed. From the control edge region 76 and 78, the fluid then enters the drainage region 80 and thus into the drain 82.
  • a second control edge 84 comes to the opening with respect to the control edge 78 of the housing and thus leaves a second volume flow from the region 70 into the region 80, while the Steu ⁇ erkanten Scheme 76 of the piston is now fully open and thereby no change takes place at the control edge region 76 and the flow through the resistor 74.
  • a first control edge opening 76 this time with an upstream resistor 74, and parallel to this in a further ⁇ Stammsbewe ⁇ supply a second control edge region 84 is used, which leads to the same effects as in the valve construction in Figure 1.
  • the pilot pressure in the region 86 on the large valve piston surface 88, which corresponds to the entire diameter of the valve piston 60 and Kol ⁇ 62 ben Adjust is compensated by the system pressure within the inner piston bore 66 on the surface 90, which here the opening force for the valve piston - testifies.
  • the same pressure acting on the surface 92 of the guide pin 64 is effective in Ventil ⁇ housing and has no influence on the opening force of the piston 60th
  • the effect of the flow force that is to say the static pressure force loss when flowing through at the control edges 76 of the piston and 78 of the housing, is shown enlarged in FIG.
  • the control edge 76 of the piston 60 has opened relative to the control edge 78 of the housing 94, so that the hydraulic fluid flows from the piston bore 66 of the piston 60 through the resistor 74 in the control edge region 76 and 78.
  • these control edges were still closed, the pressures on the control edge surfaces 96 and 98 compensated Siert and thus generated no additional piston force.
  • FIG. 6 shows the corresponding characteristic curves of a conventional pressure-limiting valve, the optimized pressure-limiting valve and the theoretical characteristic of an ideal pressure-limiting valve.
  • the characteristic 114 should always remain the same pressure with increasing volumetric flow, ie not rise above the volumetric flow rate, which, however, corresponds to the previous explanations by static pressure losses in the form of Flow forces is not possible. Therefore, in a conventional pressure relief valve according to the characteristic curve 116, the previously described flow forces and thus the characteristic curve 116 increase above the volume flow.
  • the volume flow through the resistor 39 or 74 in the form of a diaphragm characteristic 118 now comes into effect.
  • the system pressure 112 correspondingly increases at the resistor 39 from FIG. 1 or 74 from FIG. 5, which leads to a dynamic pressure which reduces the flow force influence and thus drops the characteristic curve in the region 120 again.
  • the second control edge is used, so that in the pressure limiting valve according to the invention was used, so that now results in the pressure relief valve according to the invention, a further course of the characteristic curve 124 approximately parallel to the characteristic curve 116 of a conventional pressure relief valve.
  • the course of the characteristic curve 124 of the pressure limiting valve according to the invention at the set pressure level remains far below the characteristic curve of a conventional pressure limiting valve, namely the characteristic curve 116.
  • a Druckbegren ⁇ relief valve is shown, the operating pressure is less changed by the flow than in a conventional pressure relief valve.
  • the first control edge 41, 76 thus opens until the operating pressure of the valve in the region of the back pressure of the diaphragm 39 or the diaphragm 74 is.
  • the system pressure, ie the inlet pressure drops completely at the aperture 39, 74, and the first control edge 41, 76 is completely open.
  • the error of the valve is minimal. That is, the operating pressure of the open valve corresponds to the operating pressure of the closed valve shown in Figure 2a, and in spite of Vo ⁇ lumenstroms that passes the pressure relief valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding Valves (AREA)
  • Safety Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Details Of Valves (AREA)
  • Control Of Fluid Pressure (AREA)

Abstract

L'invention concerne une soupape, en particulier une soupape de limitation de pression, comportant un piston (3) à embases (5, 7, 9), lequel piston forme des arêtes de commande (4) avec un alésage/guide de piston (1), pourvu de rainures d'entrée (17, 19) et de sortie.
EP05801567A 2004-11-09 2005-10-15 Soupape Withdrawn EP1812738A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004053983 2004-11-09
PCT/DE2005/001844 WO2006050684A1 (fr) 2004-11-09 2005-10-15 Soupape

Publications (1)

Publication Number Publication Date
EP1812738A1 true EP1812738A1 (fr) 2007-08-01

Family

ID=35659032

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05801567A Withdrawn EP1812738A1 (fr) 2004-11-09 2005-10-15 Soupape

Country Status (5)

Country Link
US (1) US7559336B2 (fr)
EP (1) EP1812738A1 (fr)
JP (1) JP4935678B2 (fr)
DE (1) DE112005002523A5 (fr)
WO (1) WO2006050684A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101517232A (zh) * 2006-09-14 2009-08-26 卢克摩擦片和离合器两合公司 用于将液压流体供应到消耗器的液压系统
DE102008058693A1 (de) * 2007-12-07 2009-06-10 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydrauliksystem mit einem Druckminderventil
FI123735B (fi) * 2011-01-14 2013-10-15 Parker Hannifin Mfg Finland Oy Painekompensoinnilla varustettu suuntaventtiili
DE102015211599A1 (de) 2015-06-23 2016-12-29 Zf Friedrichshafen Ag Ventil
CN111059322B (zh) * 2019-12-25 2020-11-17 华中科技大学 一种带有气浮式滑动副的气动伺服阀

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1168077A (fr) * 1955-12-09 1958-12-04 Gen Motors Corp Dispositif hydraulique de commande pour mécanisme de transmission à vitesse variable
US3381698A (en) * 1964-03-16 1968-05-07 Sanders Associates Inc Adjustable pressure gain control servo valve system
JPS4944695Y1 (fr) * 1970-10-29 1974-12-06
JPS4934620A (fr) * 1972-08-03 1974-03-30
JPS536815Y2 (fr) * 1973-08-24 1978-02-21
JPS5722994B2 (fr) * 1973-08-24 1982-05-15
US3872883A (en) * 1973-09-17 1975-03-25 Caterpillar Tractor Co Spool-type relief valve
US3979908A (en) * 1975-09-29 1976-09-14 The Cessna Aircraft Company Priority flow valve
DE2711861A1 (de) * 1977-03-18 1978-09-21 Elmeg Anordnung zur reduzierung der stroemungskraefte in ventilen
DE2827128A1 (de) * 1978-06-21 1980-01-03 Zahnradfabrik Friedrichshafen Kompaktes, vorgesteuertes druckbegrenzungsventil
US4254687A (en) * 1979-10-24 1981-03-10 The Cessna Aircraft Company Flow control valve
DE3308146A1 (de) * 1983-03-08 1984-09-20 Robert Bosch Gmbh, 7000 Stuttgart Entlastungsventil
JP2553345B2 (ja) * 1987-03-24 1996-11-13 株式会社ユニシアジェックス 圧力制御弁
JPH01156379U (fr) * 1988-04-20 1989-10-27
DE19740711A1 (de) * 1997-09-16 1999-03-18 Linde Ag Vorgesteuertes Druckbegrenzungsventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006050684A1 *

Also Published As

Publication number Publication date
WO2006050684A1 (fr) 2006-05-18
US7559336B2 (en) 2009-07-14
DE112005002523A5 (de) 2007-07-12
JP4935678B2 (ja) 2012-05-23
JP2008519222A (ja) 2008-06-05
US20070272889A1 (en) 2007-11-29

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