WO2003042587A1 - Soupape a siege - Google Patents

Soupape a siege Download PDF

Info

Publication number
WO2003042587A1
WO2003042587A1 PCT/DE2002/003614 DE0203614W WO03042587A1 WO 2003042587 A1 WO2003042587 A1 WO 2003042587A1 DE 0203614 W DE0203614 W DE 0203614W WO 03042587 A1 WO03042587 A1 WO 03042587A1
Authority
WO
WIPO (PCT)
Prior art keywords
seat
valve
damping
closing
valve according
Prior art date
Application number
PCT/DE2002/003614
Other languages
German (de)
English (en)
Inventor
Götz-Dieter MACHAT
Sabine Lohe
Karl-Josef Meyer
Wilfried Stroka
Original Assignee
Bosch Rexroth Ag
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 Bosch Rexroth Ag filed Critical Bosch Rexroth Ag
Publication of WO2003042587A1 publication Critical patent/WO2003042587A1/fr

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
    • F16K17/0433—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 vibration preventing means

Definitions

  • the invention relates to a seat valve, in particular a pressure relief valve according to the preamble of claim 1.
  • a pressure relief valve in which a conical closing body is biased against a valve seat by a closing spring.
  • the system pressure is set using an adjusting screw, which can be used to adjust the preload of the compression spring and thus the pressure of the closing body on the valve seat. If a preset maximum pressure at the inlet connection is exceeded, the closing body is lifted from its valve seat against the force of the compression spring, so that a connection to an outlet connection, for example a tank connection, is established and the system pressure is limited to its preset value.
  • anlie- system pressure may cause axial movements of the closing body so that it performs high-frequency vibrations and ⁇ it strikes against the valve seat.
  • This undesirable "rattling" of the closing body leads on the one hand to considerable noise pollution, on the other hand the seat edge of the valve seat can be damaged.
  • a damping pin can be assigned to the closing body, which can either be designed in one piece or - as suggested in DE 198 04 752 AI - as a damping slide formed separately from the valve body with its own control edge.
  • the invention has for its object to provide a seat valve, in particular a pressure relief valve, in which the flow behavior is improved compared to conventional solutions.
  • a closing body of the seat valve is formed downstream of the valve seat with a damming body which at least partially covers outflow openings.
  • a peripheral edge of the bluff body acts as a control edge via which the diameter of the outflow openings can be opened or closed.
  • the damping pin is removed by grading the closing body. forms, which is practically designed as a stepped piston.
  • the bluff body is advantageously designed with an impact surface for the pressure medium.
  • the pressure medium builds up on the baffle surface of the bluff body, with the resulting dynamic pressure increasing the stroke.
  • the flow behavior can be further improved if the baffle is stepped back over a step, an outer peripheral edge of the step forming the control edge for opening / closing the outflow openings.
  • a spring plate for a spring plate for a spring plate
  • the geometry of the bluff body is chosen so that the spring plate is not directly impacted by the emerging liquid jet.
  • the radial guidance of the closing body takes place in an advantageous variant according to the invention through an outer section of the bluff body and / or an end section of the damping piston.
  • the valve seat is advantageously designed with a larger diameter than the damping bore receiving the damping piston ⁇ -so that it cannot control the valve seat when the valve is open.
  • the closing body is particularly simple if it has a valve cone that tapers towards an annular groove of the damping piston.
  • the inlet connection of the pressure limiting valve which is preferably designed as an axial connection, opens out in the region of this annular groove. It was shown that an optimal flow behavior can be set with a diameter ratio between valve seat and damping bore of 10: 9.
  • the overall length of the seat valve can be minimized if the spring plate with a cone is inserted in sections into an inner cone of the bluff body.
  • the contact area is preferably placed in the axial direction between the control edge of the bluff body and the valve seat, so that stable support between the guide sections on the outer circumference of the bluff body and on the damping piston is ensured.
  • FIG. 1 shows a section through an inventive device
  • Figure 2 is a detailed representation of a variant of the pressure relief valve from Figure 1 and Figure 3 shows another embodiment of a pressure relief valve.
  • the pressure relief valve 1 shown in longitudinal section in FIG. 1 is designed in a cartridge design and is screwed into a valve bore 2 of a housing or control block 4.
  • a system pressure of the hydraulic system is present at an input port P on the front. This system pressure is limited by the pressure relief valve 1 to a maximum value. If the maximum value is exceeded, the pressure relief valve opens 1, so that pressure medium can flow out to a radial outlet connection T.
  • the pressure relief valve 1 has a valve sleeve 6, which is screwed into the control block 4 ' with an external thread.
  • the valve sleeve 6 has an axial bore 8 in the form of a blind bore, which is connected to the outlet port T via a radial bore star 10 which forms outflow openings and to the inlet port P via inclined bores 12 which form inlet openings.
  • the axial bore 8 is stepped back at its right end section in FIG. 1 via a radial shoulder 14, the region with a reduced diameter forming a damping bore 16.
  • the ' mouth region of the damping bore 16 in the radial shoulder 14 is designed as a valve seat 18 against which a closing body 20 is biased. This takes place via a closing spring 22, the pretension of which can be changed by means of a tension screw 24.
  • This is guided in the expanded part of the axial bore 8 and is in threaded engagement with a threaded bush 26 screwed into the axial bore 8.
  • the closing spring 22 engages on a spring plate 44 which, in the exemplary embodiment shown, is formed in one piece with a bluff body 36. In the exemplary embodiments according to FIGS. 2 and 3, the spring plate 44 is formed separately from the bluff body 36. This will be discussed in more detail below.
  • a hexagon socket 28 is formed on an end section of the tensioning screw 24 projecting axially from the threaded bushing 26, on which a tool for adjusting the tensioning screw 24 can be attached.
  • the set axial position of the clamping screw 24 is fixed by means of a lock nut 30. Further details of the pressure relief valve 1 are explained with reference to FIG. 2.
  • the closing body 20 is designed as a step-shaped cone, the end section on the right in FIG. 2 forming a damping piston 32 which is followed by a closing cone 34 on the left.
  • An outflow cross section 40 for the outflowing pressure medium is defined by the radial shoulder 14 of the axial bore 8 and an opposing impact surface 38 of the bluff body 36.
  • the end face is stepped back in the outer circumferential area by a circumferential step 40 in the radial direction.
  • This circumferential step 40 opens towards the outflow openings of the radial bore star 10.
  • the bluff body 36 covers the outflow openings of the radial bore star 10 in sections with its outer circumference.
  • the closing body 20 is guided with the outer circumferential surface 52 of the bluff body 36 in the radially widened part of the axial bore 8. so that the outer peripheral edge forms a control edge 53, via which the radial bore star 10 is opened when the closing body 20 is lifted off the valve seat 18.
  • the pressure medium flow is thus - as mentioned in the introduction to the description - determined by two control resistors connected in series (valve seat control resistor and bluff body control resistor), which can be adjusted in the same direction.
  • the spring plate 44 is located on a rear end face 42 of the closing body 20 via a centering ball 46 supported.
  • the closing spring 22 acts on this for pretensioning the closing body 20.
  • the damping piston 32 has a circumferential annular groove 48, in which the closing cone 34 ends. In the area of this annular groove 48, the oblique bores 12 of the input port P.
  • the damping piston 32 is guided with a certain play in the damping bore 16, so that pressure medium can flow from the annular groove 48 into a rear-side damping space 50 or can flow out of it.
  • pressure medium can flow from the annular groove 48 along the outer circumference of the damping piston 32 into the damping space 50.
  • the geometry of the damping piston 32 is chosen so that this opening stroke of the closing body 20 is not hindered.
  • Vibrations occur. Instead of the radial play, flow channels formed by flats running in the axial direction can also be provided on the outer circumference of the damping piston 32.
  • the closing body 20 In addition to the outer circumferential surface 52 guided in the axial bore 6, the closing body 20 also extends over circumferential regions of the damping pin 32 in the damping bore 16.
  • the inlet port P is sealed off from the outlet port T by means of seals 52 which are arranged on the outer circumference of the valve sleeve.
  • the diameter of the damping bore 16 is smaller than that
  • Diameter of the valve seat 18 executed so that the damping piston 32 the valve seat when the valve is open
  • valve seat 18 and also the inflow cross section to the valve seat 18 cannot close. This is possible with the prior art mentioned at the outset, since the damping bore has the same diameter as the valve seat. Correspondingly, the diameter of the damping piston 32 is of course also smaller than the diameter of the closing cone 34 resting on the valve seat 18.
  • the valve seat / damping bore diameter ratio is in the range 10: 9.
  • the closing body 20 When the system pressure set via the clamping screw 24 is exceeded, the closing body 20 lifts off the valve seat 18, so that pressure medium flows in via the oblique bores 12 and flows out via the control edge of the valve seat 18.
  • the outflow cross section downstream of the valve seat is determined at least in the initial region of the opening movement of the closing cone 20 by the axial position of the control edge 53.
  • the pressure medium impinging on the baffle surface 38 and the annular end face of the step 40 creates a dynamic pressure which increases the stroke.
  • the pressure loss-volume flow characteristic (pQ characteristic) of the pressure relief valve can be significantly improved compared to the solution described at the beginning. At high pressures above 100 bar, the volume flow is increased by almost 100% with the same pressure loss.
  • stage 40 which determines the outflow cross-section, contributes to improving the flow behavior.
  • FIG. 3 shows a variant of the exemplary embodiment shown in FIG. 2, the two constructions differing in principle only in the configuration of the spring plate 44 of the valve sleeve 6 and the bluff body 36.
  • the facing end faces of the bluff body 36 and the spring plate 44 are designed as radial surfaces that are at a short distance from each other.
  • the outside diameter of the bluff body 36 guided in the axial bore 8 is larger than the maximum outside diameter of the spring plate 44, so that pressure medium is not directly applied to it.
  • an inner cone 56 tapering toward the valve seat 18 is formed in the rear end face 42 of the bluff body 36, on the depression of which the centering ball 46 is supported.
  • the adjacent end face of the spring plate 44 is accordingly designed as a cone 58 immersed in the inner cone 56, the cone angle of which is, however, chosen to be somewhat smaller than the cone angle of the inner cone 56.
  • the outer diameter of the bluff body 36 is selected to be larger than the maximum outer diameter of the spring plate 44, so that it is practically covered by the bluff body in the outflow direction.
  • the contact area of the centering ball 46 on the inner cone 56 lies in the axial direction in the area between the radial planes spanned by the control edge 53 and the valve seat 18. Since this support of the spring plate 44 lies in a region between the radial support points of the dam body 36 (outer circumferential surface 52, valve seat 18, damping piston 32), and the spring plate 44 is not directly subjected to flow forces, the flow behavior, with reduced hysteresis, can be one good linearity of the pQ characteristic with extremely low control deviation and with significantly reduced flow noise can be significantly improved.
  • the tightness of the valve can also be improved by the exact radial guidance of the bluff body. In the variant shown in FIG.
  • valve sleeve 6 is also made in two parts with a spring sleeve 60 and a seat sleeve 62 inserted therein. This has essentially the same geometry as the partial region of the valve sleeve 6 shown in FIG. 2, so that further explanations are unnecessary.
  • This two-part design of the valve sleeve 6 simplifies the manufacture and functional check of the seat valve, since the components relevant for the flow behavior (radial bore star 10, oblique bores 12, valve seat 18, damping bore 16) are arranged in the seat sleeve 62. This can be made of a different material than the spring sleeve 60, so that the valve seat 18 can be designed with the desired properties.
  • the step 40 has a greater radial and axial extension than the step 40 of the exemplary embodiment shown in FIG. 2, so that the outer annular end face of the step 50 has a larger area than in the previously described exemplary embodiment.
  • the impact surface 38 is correspondingly reduced in the variant shown in FIG. 3.
  • Both the baffle surface 48 and the ring end face of the step 40 act as stowage surfaces, which bring about the aforementioned lifting reinforcement when the closing body is lifted off.
  • control resistors are connected in series. These control resistors are, on the one hand, the variable valve seat control resistor and the outflow cross section of the radial bore star 10, which is determined by the control edge 53. It has been shown that particularly good flow behavior can be achieved with this novel arrangement.
  • a seat valve in particular a pressure relief valve, in which a valve body is provided downstream of a valve seat with a bluff body which has a control edge on a peripheral surface, via which the outflow openings of the seat valve can be opened or closed.
  • valve bore control block
  • valve sleeve axial bore
  • radial bore star oblique bore
  • radial shoulder damping bore
  • valve seat closing body
  • closing spring clamping screw
  • threaded bush hexagon socket
  • counter nut damping piston
  • closing cone bluff body
  • baffle circumferential step, rear end face, spring plate, centering ball, ring groove, damping chamber, outer sleeve, inner sleeve, cone, and outer ring

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Details Of Valves (AREA)

Abstract

La présente invention concerne une soupape à siège, notamment une soupape de limitation de pression (1). Selon cette invention, un corps de soupape est pourvu, en aval d'un siège de soupape, d'un corps de retenue (36) qui présente, sur une surface périphérique, une rampe de distribution (53) permettant d'ouvrir ou de fermer des orifices d'écoulement (10) de la soupape à siège.
PCT/DE2002/003614 2001-11-13 2002-09-25 Soupape a siege WO2003042587A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2001155629 DE10155629A1 (de) 2001-11-13 2001-11-13 Sitzventil
DE10155629.2 2001-11-13

Publications (1)

Publication Number Publication Date
WO2003042587A1 true WO2003042587A1 (fr) 2003-05-22

Family

ID=7705538

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/003614 WO2003042587A1 (fr) 2001-11-13 2002-09-25 Soupape a siege

Country Status (2)

Country Link
DE (1) DE10155629A1 (fr)
WO (1) WO2003042587A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9273702B2 (en) 2011-10-21 2016-03-01 Sun Hydraulics Corporation Dynamically adjusting counterbalance valve
US9850919B2 (en) 2014-09-16 2017-12-26 Sun Hydraulics Corporation Counterbalance valve with dual or triple pilot ratio
CN108413085A (zh) * 2018-05-22 2018-08-17 重庆邮电大学 一种减压单向阀

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008045419A1 (de) * 2008-09-02 2010-03-04 Marco Systemanalyse Und Entwicklung Gmbh Druckbegrenzungsventil
EP3073162A1 (fr) * 2015-03-21 2016-09-28 HS Wroclaw Sp. z o.o. Soupape avec amortisseur
EP3348884B1 (fr) * 2017-01-13 2019-11-27 Hamilton Sundstrand Corporation Soupape d'amortissement hydraulique
EP3825591A1 (fr) * 2019-11-22 2021-05-26 Hamilton Sundstrand Corporation Soupape d'amortissement hydraulique

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1398893A (fr) * 1964-04-02 1965-05-14 Dispositif limiteur de pression hydraulique
US5381823A (en) * 1994-02-14 1995-01-17 Sun Hydraulics Hydraulic pressure control valve
EP0908653A1 (fr) * 1997-10-07 1999-04-14 Mannesmann Rexroth AG Soupape pilote de limitation de pression
DE19804752A1 (de) 1998-02-06 1999-08-12 Mannesmann Rexroth Ag Sitzventil
WO2001069112A1 (fr) * 2000-03-17 2001-09-20 Robert Bosch Gmbh Dispositif de regulation de pression

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7922427U1 (de) * 1979-08-06 1979-10-31 Herion-Werke Kg, 7012 Fellbach Ueberdruckventil
DE29713295U1 (de) * 1997-07-25 1997-10-16 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Sicherheitsventil für die Hochdruckhydraulik

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1398893A (fr) * 1964-04-02 1965-05-14 Dispositif limiteur de pression hydraulique
US5381823A (en) * 1994-02-14 1995-01-17 Sun Hydraulics Hydraulic pressure control valve
EP0908653A1 (fr) * 1997-10-07 1999-04-14 Mannesmann Rexroth AG Soupape pilote de limitation de pression
DE19804752A1 (de) 1998-02-06 1999-08-12 Mannesmann Rexroth Ag Sitzventil
WO2001069112A1 (fr) * 2000-03-17 2001-09-20 Robert Bosch Gmbh Dispositif de regulation de pression

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9273702B2 (en) 2011-10-21 2016-03-01 Sun Hydraulics Corporation Dynamically adjusting counterbalance valve
US9850919B2 (en) 2014-09-16 2017-12-26 Sun Hydraulics Corporation Counterbalance valve with dual or triple pilot ratio
CN108413085A (zh) * 2018-05-22 2018-08-17 重庆邮电大学 一种减压单向阀
CN108413085B (zh) * 2018-05-22 2020-02-07 重庆邮电大学 一种减压单向阀

Also Published As

Publication number Publication date
DE10155629A1 (de) 2003-05-22

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