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WO2002038993A1 - Soupape de pression preselective - Google Patents

Soupape de pression preselective Download PDF

Info

Publication number
WO2002038993A1
WO2002038993A1 PCT/DE2001/003383 DE0103383W WO0238993A1 WO 2002038993 A1 WO2002038993 A1 WO 2002038993A1 DE 0103383 W DE0103383 W DE 0103383W WO 0238993 A1 WO0238993 A1 WO 0238993A1
Authority
WO
WIPO (PCT)
Prior art keywords
pilot
pressure
pilot valve
pressure valve
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.)
Ceased
Application number
PCT/DE2001/003383
Other languages
German (de)
English (en)
Inventor
Karl Krug-Kussius
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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
Priority claimed from DE10120643A external-priority patent/DE10120643B4/de
Application filed by Mannesmann Rexroth AG, Bosch Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of WO2002038993A1 publication Critical patent/WO2002038993A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16K17/10—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 auxiliary valve for fluid operation of the main valve
    • F16K17/105—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 auxiliary valve for fluid operation of the main valve using choking or throttling means to control the fluid operation of the main valve
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4008—Control of circuit pressure
    • F16H61/4026—Control of low 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4157—Control of braking, e.g. preventing pump over-speeding when motor acts as a pump
    • 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

Definitions

  • the invention relates to a pressure feed valve according to the preamble of claim 1.
  • Such a pilot-operated pressure valve is used, for example, as a working valve in hydrostatic drives, for example undercarriage and slewing gear drives, and for protecting linear consumers, for example cylinders in an open or closed hydraulic circuit.
  • these pressure valves are used, for example, to open a connection from the high-pressure side to the low-pressure side when a predetermined system pressure is exceeded. Pressure medium is then guided past a hydraulic motor of the rotary / chassis drive from the high pressure branch into the low pressure branch, so that pressure peaks in the high pressure circuit can be avoided.
  • WO 99/08029 AI discloses a pilot-controlled pressure relief valve, in which a valve body of a main stage is assigned an attenuator, via which the valve body is opened far below its opening point, which is predetermined by the pilot stage, so that high accelerations of the driver occur when pressure peaks occur - / slewing drive resulting pressure peaks can be damped by briefly opening the valve body of the main stage below the response point of the pilot stage.
  • a pilot-controlled pressure feed valve with a suction function in which a pilot control stage has a booster piston the effect of which the pilot stage can be controlled below the set maximum pressure, so that pressure fluctuations at the inlet connection can be damped.
  • the object of the invention is to create a pilot-operated pressure valve in which the risk of damage is reduced even at high pressure surge loads.
  • the pilot stage of the pressure valve is associated with a damping member interacting with the pilot valve body, via which the pressure peaks occurring at high pressure surge loads are damped in the pilot stage, so that an abrupt placement of the pilot valve body on the associated pilot valve seat can be largely prevented.
  • the main advantage of the invention thus lies in the damped behavior of the main and pilot stages when vibrations occur on the pump and tank side out of phase.
  • the damping member is a piston which is guided in a pilot valve bore in the form of a blind hole, an end face of the piston with the bottom of the pilot valve bore delimiting a damping space into which control oil flows in or out of the piston depending on the axial displacement of the piston can flow out.
  • the cologne together with the pilot valve bore upstream of the pilot valve seat forms an annular nozzle through which the control oil flows when the pilot stage is open. Due to the pressure drop across this nozzle, the piston is subjected to a force acting in the direction of the pilot valve body during the opening movement of the pilot valve body, so that the piston can quickly follow the opening movement of the pilot valve body.
  • the control oil present in the rear damping chamber must first be displaced so that the closing movement of the pilot valve body is damped. This variant allows the pilot stage to be opened quickly while the return movement is damped, so that damage to the valve seat is prevented by the half-wave damping.
  • the cologne is of a particularly simple construction if it has, at an end section remote from the pilot valve seat, a guide collar which delimits the damping space and which, via a radially recessed central section, merges into a nozzle collar on the valve seat side and limits the nozzle.
  • the pilot stage preferably has at least one connecting bore in its housing, which opens on the one hand in the pilot valve bore and on the other hand in a spring chamber of the main stage.
  • the pilot valve-side mouth section lies in the area of the central, radially recessed section of the little cup, so that the control oil can flow on the one hand in the direction of the nozzle and on the other hand in the direction of the damping chamber.
  • the setting behavior of the pilot part is particularly good when a ball is used as the pilot valve body.
  • a pressure chamber downstream of the pilot valve can be pressurized with the pressure in the low-pressure area of the system or with a pilot pressure.
  • the pressure valve is preferably designed with a suction function, so that pressure medium can be drawn from the low pressure part into the high pressure part.
  • the valve body of the main stage is preferably designed as a valve slide in that a nozzle bore is formed.
  • the response behavior of the valve arrangement can be further improved if the valve spool is designed with a surface difference.
  • the valve according to the invention can be designed with a sliding seat.
  • FIG. 1 shows a section through a pilot-operated pressure relief valve according to the invention
  • Figure 2 is an enlarged view of a pilot part of the pressure relief valve of Figure 1 and
  • FIG. 3 shows a characteristic curve of the pressure relief valve from FIG. 1.
  • FIG. 1 shows a longitudinal section through a pilot-operated pressure relief valve 1, also called a pressure feed valve.
  • the pressure relief valve 1 has a main stage 2 and a pilot stage 4, which are formed in a cartridge-shaped housing 6.
  • the housing 6 has an axial connection P, which is connected, for example, to the high-pressure side of a chassis drive.
  • An outlet port T formed by a radial bore star is connected to the low pressure side of the system.
  • the housing 6 is penetrated by an axial bore 8, in which a piston 10 is axially displaceably guided.
  • This main stage 2 is designed with a sliding seat, the piston 10 being prestressed against an annular shoulder 14 of the axial bore 8 via a compression spring 12.
  • the piston 10 of the main stage 2 is designed with an area difference, so that the pressure force equivalent effective in the opening direction is greater than the pressure force equivalent effective in the closing direction.
  • a hub-shaped projection 16 is formed on the bottom surface of the piston 10 and is penetrated by a bore forming a nozzle 18. This connects the part of the axial bore 8 on the inlet connection side to an interior 22 of the piston 10 delimited by the piston skirt 20.
  • the compression spring 12 engages an annular shoulder in the interior of the piston jacket 20 so that the latter is biased into its closed position in which the radial bores 24 of the outlet connection 10 are closed.
  • the axial bore 8 is widened in steps, so that an annular space is formed for receiving a suction ring 26, which is slidably guided between the outer periphery of the piston skirt 20 and a peripheral wall 28 of the radially expanded part of the axial bore 8.
  • the axial movement of the suction ring 26 is limited on the one hand by the radial shoulder widening the axial bore 8 and on the other hand by a stop collar 30.
  • the space formed by the annular space between the piston skirt 20 and the inner circumferential wall of the radially widened part of the axial bore is connected via a throttle space 33 to a parallel bore 32 of the housing 6, via which the pressure in the outlet connection can be tapped off.
  • a reducing piece 34 is screwed into the end section of the radially widened part 28 of the axial bore 8, via which a pilot valve housing is prestressed against a peripheral edge formed by an annular space 38 of the housing 6.
  • the annular space 38 is connected via a housing channel 40 to the low-pressure side, for example the outlet connection T.
  • the pilot valve housing and the components of the pilot stage 4 accommodated therein are shown enlarged in FIG.
  • the pilot valve housing has a base body 42 which is supported on the circumferential edge of the annular space 38 and from which a shoulder 44 extends toward the piston 10 in the center.
  • a pilot valve bore 46 designed as a blind hole is formed, which opens via a pilot valve seat 48 into a valve chamber 50, in which a pilot valve body 52 is arranged.
  • This is biased against the cylindrical valve seat 48 via a spring plate 54 and a control spring 56 acting thereon.
  • a radially projecting collar 55 of the spring plate 54 is guided in a recess 57 of the base body. This has a hexagonal cross section, so that on the one hand an exact guidance of the spring plate is guaranteed and on the other hand a large flow cross section to and from the spring chamber is available for the control spring 56.
  • the pilot valve body 52 is designed with a spherical active surface, with a ball specifically being centered and supported in a recess 58 in the spring plate 54.
  • the valve chamber 50 of the base body 42 is connected to the annular chamber 38 via relief channels 39 running in the radial direction.
  • control spring 56 is supported on a set screw 60 mounted in the reducer 34.
  • the bias of the control spring 56 can be adjusted by axially displacing the adjusting screw 60. This is fixed on the reducer 34 using a lock nut.
  • a part protruding from the reducer 34 is shown in FIG Set screw 60 covered by a safety cap 62.
  • the extension 44 is penetrated by a plurality of radially extending connecting bores 64, via which a spring chamber 66 for the compression spring 12, delimited by the radially expanded part of the axial bore 28, is delimited with the interior of the pilot valve bore 46.
  • a Kölbchen 68 is guided axially.
  • a guide collar 70 is formed on the left-hand end section of the piston 68 in FIG. 2, which forms an annular throttle gap 72 with the peripheral wall of the pilot valve bore 46.
  • a damping space 74 is delimited by the end face of the guide collar 70 and the bottom of the pilot valve bore 46.
  • a radially recessed central section 76 is formed on the small piston 68, which merges into a nozzle collar 78 at the end section on the right in FIG. 2, which forms an annular nozzle 80 with the peripheral wall of the pilot valve bore 46.
  • a centering cone 82 is formed in the end face of the nozzle collar 78 and can be brought into abutment with the pilot valve body 52.
  • control oil enters the pilot valve bore 46 from the spring chamber 66 through the connecting bores 64 in the region of the central section 76, so that the rear damping chamber 74 and the annular gap are filled with control oil between the piston 68 and the peripheral wall up to the valve seat 48, so that the compressive forces acting on the piston 68 in the axial direction are balanced.
  • the pressure at the inlet port P increases due to the connection via the nozzle bore 18, the pressure in the spring chamber 66 also increases, so that this pressure is also present at the valve seat 48.
  • Figure 3 shows a stat. and dyn. Pressure / flow characteristic (p / Q) of a pressure feed valve 1 according to the invention. Accordingly, the volume flow between the input port P and the output port T increases very quickly when the maximum value to be limited p m a ⁇ is reached due to the dynamically rapid opening movement of the pilot valve body. When the pressure at the inlet port P drops, the volume flow is hydraulically slowed back due to the damping effect of the piston 68, the piston 10 supported by the compression spring 12, so that the closing movement is damped.
  • the inner and outer play of the feed ring is selected so that the leakage of the valve arrangement can be reduced. This is further supported by the fact that the piston 10 is designed with an area difference. Further details on the structure of the main stage can be found in a parallel application P 2000 MA7468 by the applicant.
  • a spherical pilot valve body 52 has, in addition to the good setting behavior, the further advantage that any inclined positions of the control spring 56 can be compensated for, so that a central bearing on the valve seat 48 is ensured.
  • the pilot valve body 52 is acted upon by the pressure in the low-pressure branch via the connecting channel 40.
  • a solution is indicated in broken lines in FIG. 1, in which the pressure effective in the closing direction can also be set by a control pressure which is reported via a control line 84 into the annular space 38 and thus into the valve space 50 (external control line).

Landscapes

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

Abstract

L'invention concerne une soupape d'injection à pression, caractérisée en ce qu'à un corps de soupape de présélection (52) est associé un dispositif d'amortissement (68) par l'intermédiaire duquel au moins le mouvement de fermeture du corps de soupape de présélection est amorti.
PCT/DE2001/003383 2000-11-10 2001-09-05 Soupape de pression preselective Ceased WO2002038993A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10055813.5 2000-11-10
DE10055813 2000-11-10
DE10120643A DE10120643B4 (de) 2000-11-10 2001-04-27 Vorgesteuertes Druckventil
DE10120643.7 2001-04-27

Publications (1)

Publication Number Publication Date
WO2002038993A1 true WO2002038993A1 (fr) 2002-05-16

Family

ID=26007622

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2001/003383 Ceased WO2002038993A1 (fr) 2000-11-10 2001-09-05 Soupape de pression preselective

Country Status (1)

Country Link
WO (1) WO2002038993A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013083234A1 (fr) * 2011-12-10 2013-06-13 Robert Bosch Gmbh Système d'entraînement hydrostatique

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0638746A1 (fr) * 1993-08-02 1995-02-15 Hydrolux S.A.R.L. Etage piloté pour une soupape limitant la pression
WO1997032136A1 (fr) * 1996-02-28 1997-09-04 Beringer-Hydraulik Ag Soupape de frein a maintien de charge
WO1999008029A1 (fr) 1997-08-06 1999-02-18 Mannesmann Rexroth Ag Soupape de limitation de pression pilotee
EP0908653A1 (fr) 1997-10-07 1999-04-14 Mannesmann Rexroth AG Soupape pilote de limitation de pression

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0638746A1 (fr) * 1993-08-02 1995-02-15 Hydrolux S.A.R.L. Etage piloté pour une soupape limitant la pression
WO1997032136A1 (fr) * 1996-02-28 1997-09-04 Beringer-Hydraulik Ag Soupape de frein a maintien de charge
WO1999008029A1 (fr) 1997-08-06 1999-02-18 Mannesmann Rexroth Ag Soupape de limitation de pression pilotee
EP0908653A1 (fr) 1997-10-07 1999-04-14 Mannesmann Rexroth AG Soupape pilote de limitation de pression

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013083234A1 (fr) * 2011-12-10 2013-06-13 Robert Bosch Gmbh Système d'entraînement hydrostatique

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