EP1409873A1 - Bloc de distribution pour un dispositif de regulation, en particulier une machine hydrostatique - Google Patents

Bloc de distribution pour un dispositif de regulation, en particulier une machine hydrostatique

Info

Publication number
EP1409873A1
EP1409873A1 EP02758348A EP02758348A EP1409873A1 EP 1409873 A1 EP1409873 A1 EP 1409873A1 EP 02758348 A EP02758348 A EP 02758348A EP 02758348 A EP02758348 A EP 02758348A EP 1409873 A1 EP1409873 A1 EP 1409873A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve block
block according
return spring
actuator
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
EP02758348A
Other languages
German (de)
English (en)
Other versions
EP1409873B1 (fr
Inventor
Roland Belser
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1409873A1 publication Critical patent/EP1409873A1/fr
Application granted granted Critical
Publication of EP1409873B1 publication Critical patent/EP1409873B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • Valve block for a control device in particular for a hydrostatic machine
  • the invention relates to a valve block according to the preamble of claim 1.
  • a valve block of this type is described in DE 199 53 170 AI.
  • a power control valve and a control valve are provided, the latter being acted upon by control pressure in a power control line of an adjusting device for the hydraulic pump as a function of the difference between the working pressure in a working line of the hydraulic pump and the pressure flow up the power control valve.
  • a variable additional force can be applied to the control valve by means of an actuator. This makes it possible to adjust the maximum power limited by the control valve in connection with the power control valve and thus to reduce or increase the maximum power depending on the operating situation.
  • the invention is based, with one
  • Valve block according to the preamble of claim 1 to simplify the adjustment and improve safety.
  • the adjusting movement of the actuator in its direction of movement increasing the closing force is limited by a stop element in a position in which the closing force corresponds to its limited maximum value.
  • a stop element in a position in which the closing force corresponds to its limited maximum value.
  • the operator can set the hydrostatic machine at most only to a value, in particular a pressure value, which corresponds to a certain maximum permissible value, e.g. B. corresponds to the maximum permissible signal pressure or working or operating pressure.
  • the configuration according to the invention also simplifies the adjustment of the adjusting device. The operator need not pay particular attention to whether or when the setting corresponds to or exceeds a maximum permissible criterion.
  • the configuration according to the invention is suitable, inter alia, for a pressure control device and / or for a flow control device
  • the stop element and the actuator are arranged on an attachment part of the valve block.
  • the attachment can be prefabricated or preassembled not only with regard to the actuator, but also with regard to the stop element, so that it is only necessary to mount the attachment on the valve block in order to complete the valve according to the invention.
  • FIG. 1 shows a valve block according to the invention for a hydraulic control device with two valves
  • valve block 2 shows a basic hydraulic circuit diagram of the valve block
  • Fig. 4 shows a receiving body with the adjusting disc in axial section.
  • the valve block designated by 1 in FIGS. 1 and 2 is part of an adjusting device, designated in its entirety by 2, for adjusting and adjusting the throughput volume of a hydrostatic machine, here a hydraulic pump 3.
  • the adjusting device 2 has an adjusting cylinder 4, which in the exemplary embodiment is hydraulic on one side is effective and in a manner known per se consists of a cylinder 4a and a piston 4b slidably mounted therein and a piston rod 4c connected to it, which is connected to an adjusting element 3a of the pump 3, which is indicated in the drawing.
  • the hydrostatic machine can be formed by a throughput volume adjustable by a hydraulic motor instead of by a hydraulic pump 3.
  • the valve block 1 has at least four hydraulic connections, namely a working pressure connection P, a control pressure connection A, a tank connection T and a control connection X.
  • the hydraulic pump 3 is equipped with a Drive shaft of a drive motor, not shown, in drive connection, for. B. with an internal combustion engine. In functional operation, the hydraulic pump 3 draws in hydraulic fluid through a suction line 5 from a hydraulic fluid tank 6 and conveys the hydraulic fluid into a working line 7 in which an optionally adjustable delivery flow restrictor 8 is arranged.
  • valve block 1 can have only one valve 9.
  • valve 9 is a pressure control valve and valve 11 is a flow control valve.
  • An input of the pressure control valve 9 is connected by a connecting line 12 to a working line branch 7a, which branches off from the working line 7 upstream of the flow restrictor 8.
  • the valve piston 14 of the pressure regulating valve 9 can be acted upon by the working pressure through a connecting line 13 connected to the working line branch 7a, namely against the force of a return spring 15, the spring force of which can be optionally reduced and increased by an actuator 16a of an adjusting device 16.
  • the flow control valve 11 is connected by a first connecting line 21 to the working line 7 upstream of the flow restrictor 8 or to the working line branch 7a and by a second connecting line 22 to the working line 7 downstream of the flow restrictor 8.
  • the displacement volume of the hydraulic pump 3 is adjusted by the adjusting device 2 or the adjusting cylinder 4 in such a way that a constant flow rate flows through the flow restrictor 8.
  • the delivery flow control valve 11 is acted upon by the connecting lines 21, 22 from the pressure drop at the delivery flow restrictor 8. If the pressure drop at the delivery flow restrictor 8 increases in accordance with the delivery flow flowing through the delivery flow restrictor 8, the valve piston becomes 23 of the flow control valve 11 against a return spring
  • the signal pressure in the signal pressure chamber 4d of the adjusting cylinder 4 is regulated via the signal pressure line 25.
  • the signal pressure in the signal pressure chamber 4d of the adjusting cylinder 4 is increased and the displacement volume of the hydraulic pump 3 is pivoted back in the direction of a smaller displacement volume. This in turn reduces the delivery flow flowing through the delivery flow restrictor 8 and thus the pressure drop at the delivery flow restrictor 8, so that an equilibrium state is established at the delivery flow control valve 11.
  • the flow rate which is determined by the consumer connected to the working line 7, can be varied by changing the cross section of the preferably adjustable flow rate throttle 8.
  • the valve piston 14 is shifted from the illustrated first valve position b to the second valve position a, in which the section of the signal pressure line 25 extending to the signal pressure chamber 4d is connected to the connecting line 12 and to the working line branch 7a.
  • the flow control valve 11 has a connection which is connected to the tank 6 by a connecting line 26 and corresponds in the valve position d to the connection for the control pressure line 25.
  • the control pressure line 25 is connected between the valves 9, 11 by a connecting line 27 with a first relief throttle 28a with the tank 6. Downstream of the pressure control valve 9, the actuating pressure line 25 or the actuating pressure chamber 4d is optionally connected to the first relief throttle 28a by a second relief throttle 28b and likewise connected to the tank 6 by this.
  • the flow control valve 11 and the pressure control valve 9 are each designed as a 3/2 way valve.
  • the flow control valve 11 also has an adjusting device 31 with an adjusting member 31a, with which the spring force of the return spring 25 can be either reduced or increased.
  • the one-piece members 16a, 31a can optionally be moved back and forth and can be locked in the respective setting position.
  • the direction of movement of the one-piece members 16a, 31a is preferably directed in the longitudinal direction of the associated valve piston 14 or 23.
  • the actuators 16a and 31a are manually adjustable. However, they can also be adjustable by motor, e.g. B. by an electromagnet, in particular a proportional magnet.
  • the actuators 16a and 31a act axially on an abutment 32 of the associated return spring 15 or 24, the abutment 32 preferably being formed by a support disk 19 in the sense of a spring plate, which is described below with reference to FIG shows compact and therefore, among other things, advantageous embodiment of the valve block 1.
  • the cross bores 52, 53 are each closed by a threaded plug 54 or 55.
  • the valve piston 23 of the flow control valve 11 is axially movable.
  • the valve piston 23 has a first annular recess 56 which is connected to the working pressure port P via a connecting channel 58.
  • the annular recess 56 is adjoined by a region 59 with a larger diameter, on which a first control edge 60 is formed.
  • the valve piston 23 has a second annular recess 61 which is connected to the tank connection T via a connecting channel 62.
  • the second annular recess 61 is adjoined by a region 92 with a larger diameter, on which a second control edge 63 is formed.
  • the second control edge 63 is open and a connecting channel 64 is connected to the tank connection T via the connecting channel 62.
  • the annular recess 56 is connected via a longitudinal bore 65 formed in the valve piston 23 to a first pressure chamber 67 formed between a first pressure application surface 66 and the sealing plug 55.
  • the control pressure supplied to a second pressure chamber 68 via the supply flow control connection X acts on a second pressurizing surface 69, which forms the right end face of the valve piston 23.
  • the return spring 24 also acts on this end face of the valve piston 23 via a spring plate 70.
  • the restoring force increase generated by the actuator 31a is introduced into the valve piston 23 via the support disk 19 and the restoring spring 24.
  • the Valve piston 23 is therefore adjusted so that the actuating force exerted by the working pressure is in equilibrium with the counterforce exerted by the return spring 24.
  • the valve piston 14 for the pressure regulating valve 9 is inserted into the second transverse bore 53.
  • the valve piston 14 has a first annular recess 77 which is connected to the working pressure connection P via the connecting channel 58.
  • the first annular recess 77 is adjoined by an area 78 with an enlarged diameter, on which a first control edge 79 is formed.
  • a second annular recess 80 is also formed on the valve piston 14 and is connected to the connecting channel 64.
  • a region 81 with an enlarged diameter adjoins the second annular recess 80, on which a second control edge 82 is formed.
  • the second valve piston 14 In the rest position shown, the second valve piston 14 is pressed by the return spring 15 against its left stop in FIG. 1, so that the second control edge 82 is opened.
  • the return spring 15 rests on a spring plate 83 which is held in contact with the valve piston 14.
  • the receiving body 84 screwed into the base body 51 is the externally accessible actuator 16a, with which the axial position of the support disk 19 and thus the pretension of the second return spring 15 can be changed.
  • valve piston 14 there is a longitudinal bore 87 in the form of a blind bore, which opens out at a third pressure chamber 88 formed between the sealing plug 54 and the valve piston 14, so that the third pressure chamber 88 is connected to the working pressure connection P.
  • the working pressure acts on a first pressurizing surface 89 of the valve piston 14.
  • the equilibrium position of the valve piston 14 is therefore determined by the difference between the force generated by the working pressure and the restoring force of the restoring spring 15.
  • the valve piston 14 has a bushing 93.
  • a longitudinal bore 94 extends from the fourth pressure chamber 90 to the signal pressure connection A.
  • a sealing plug 96 in which a blind bore 97 is formed.
  • the blind bore 97 is connected to the tank connection T via a first transverse bore 98, which forms the first relief throttle.
  • the blind bore 97 is connected to the actuating pressure port A via a second transverse bore 99, which forms the second relief throttle.
  • the adjusting devices 16, 31 are each arranged on receiving bodies 72, 84, which are add-on parts, in particular screw-in parts, of the base body 51.
  • the receiving bodies 72, 84 each have an axial through hole with two through hole sections 101, 102.
  • the through-hole section 101 facing the base body 51 serves in each case to receive the associated return spring 15 or 24.
  • the through-hole section 102 facing away from the base body 51 in each case serves to receive the associated actuator 16a or 31a.
  • the actuators 16a, 31a are each formed by a spindle drive, the adjusting screw 103 of which is screwed into the through-hole section 102 in the form of a threaded bore and is axially adjustable by turning.
  • the respective adjusting screw 103 is on the outside of a rotary handle element, not shown, for. B. a slot or a hexagon for a screwdriver, accessible and lockable by a screwed lock nut 105, which rests on the receiving body 72 and 84 in the embodiment.
  • the end section of the adjusting screw 103 which projects beyond the lock nut 105 is covered by a screwed-on cap 106 which is provided for the purpose of mechanical protection and / or sealing.
  • the cap 106 has on its threaded hole edge a preferably radial end face with which it bears on a preferably radial end face of the lock nut 105. Radial end faces are preferably also provided between the lock nut 105 and the receiving body 72 or 84.
  • the abutting end faces can each be sealed by an annular seal, e.g. B. by an O-ring made of elastic material, which is arranged in an annular groove, which is arranged in the associated end face of the cap 106 or the lock nut 105 or the receiving body 72 or 84.
  • the sealing ring 107 is axially elastically compressed in the screwed state, whereby the seal is achieved.
  • a support plate 19 is arranged, on which the return spring 15 and 24 is supported.
  • the receiving bodies 72 and 84 are formed by screw-in parts, each of which is screwed into a corresponding threaded bore in the base body 51 with a screw sleeve 72a or 84a surrounding the inner through-hole section 101 and, if appropriate, bear against the base body 51 with the shoulder surface of a compressed head.
  • an annular seal can preferably be provided with a special sealing ring 109 in the edge region of the screw hole.
  • the support disk 19 and its surrounding area are specially formed in the receiving body 84, as will be explained below.
  • the support disk 19 is located in an axial adjustment area in the transition area between the hole sections 101, 102.
  • the adjustment area for the support disk 19 is limited by a stop 112, which is shown in FIG an axial position in which the pressure control valve 9 sets or limits a pressure, here the signal pressure which corresponds to the maximum permissible pressure.
  • the stop 112 is formed by a step surface 114 facing away from the base body 51 on the inner through-hole section 101, the step surface 114 delimiting a hole widening 115 which is located between the through-hole sections 101, 102.
  • the support disk 19 is tapered on both sides to a dimension e, preferably flattened, which is smaller than the cross-sectional size of the inner through-hole section 101. Consequently, the support disk 19 can be passed through in a position rotated by 90 ° with respect to the stop 112 move the through hole portion 101 into the hole extension 115.
  • the latter is designed so large with respect to its axial and radial dimensions that the support disk 19 can be pivoted into its operating position in the hole extension 115, in which it is located parallel to the stop 112.
  • the hole widening 115 has, at least in its axial region facing the stop 112, a preferably conical inner surface 113 that converges towards the stop 112. By means of this convergent inner lateral surface 113, the support disk 19 is centered when moving in the direction of the stop 112 if it should have assumed an eccentric position during pivoting.
  • the support plate 19 is shown in several intermediate pivot positions.
  • the stop 112 or the stop element by a spring ring which is inserted into an annular groove in the inner lateral surface of the inner through-hole section 101.
  • the support plate 19 To assemble the support plate 19, the size of which in this case is adapted to the cross-sectional size of the hole section 101 with play, the support plate 19 must first be inserted into the through-hole section 101 and then the spring ring 116 must be fitted, which projects beyond the inner circumferential surface of the through-hole section 101 and thus as Stop 112 can serve.
  • the support disc 19 can be round.
  • an electromagnet or an electric motor in particular a stepper motor, can be used for motorized adjustment of the actuator 16a or 31a, which, for. B. via a threaded spindle, the bias of the return spring 15 or 24 and thus the additional force exerted on the valve piston 14 or 23 changed.
  • the support disk 19 of the flow control valve 11 and its surroundings can also be formed in the receiving body 72 as described above with reference to the pressure control valve 9.
  • the abovementioned limit stop for the maximum value of the restoring or closing force of the restoring spring can thus also be implemented in a corresponding embodiment in the case of the flow control valve 11 or another valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un bloc de distribution (1) destiné à un dispositif de régulation, comprenant une soupape (9). Dans sa position d'ouverture, le piston (14) de la soupape est actionné par une pression de régulation et, dans sa position de fermeture, par un ressort de rappel (18). Selon cette invention, la force de serrage du ressort de rappel (15) peut être réduite ou augmentée par un élément de réglage (16a), pouvant être déplacé en direction d'une position augmentant la force de serrage et d'une position réduisant cette dernière. L'objectif de cette invention est de simplifier ce déplacement ou réglage et d'améliorer la sécurité. A cet effet, le mouvement de déplacement de cet élément de réglage (16a) dans le sens de déplacement augmentant la force de serrage du ressort de rappel (15) est limité par un élément de butée (112) dans un position où la force de serrage du ressort de rappel (15) atteint sa valeur maximale limite.
EP02758348A 2001-07-26 2002-07-16 Bloc de distribution pour un dispositif de regulation, en particulier une machine hydrostatique Expired - Lifetime EP1409873B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10136416 2001-07-26
DE10136416A DE10136416A1 (de) 2001-07-26 2001-07-26 Ventilblock für eine Regelvorrichtung, insbesondere für eine hydrostatische Maschine
PCT/EP2002/007909 WO2003014570A1 (fr) 2001-07-26 2002-07-16 Bloc de distribution pour un dispositif de regulation, en particulier une machine hydrostatique

Publications (2)

Publication Number Publication Date
EP1409873A1 true EP1409873A1 (fr) 2004-04-21
EP1409873B1 EP1409873B1 (fr) 2009-04-15

Family

ID=7693164

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02758348A Expired - Lifetime EP1409873B1 (fr) 2001-07-26 2002-07-16 Bloc de distribution pour un dispositif de regulation, en particulier une machine hydrostatique

Country Status (4)

Country Link
US (1) US7044442B2 (fr)
EP (1) EP1409873B1 (fr)
DE (2) DE10136416A1 (fr)
WO (1) WO2003014570A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020208933A1 (de) 2020-07-16 2022-01-20 Robert Bosch Gesellschaft mit beschränkter Haftung Regelventil mit radialer Ausnehmung im Bereich der ersten und der zweiten Blende

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DE10136416A1 (de) 2001-07-26 2003-02-13 Brueninghaus Hydromatik Gmbh Ventilblock für eine Regelvorrichtung, insbesondere für eine hydrostatische Maschine
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DE102008038455A1 (de) 2007-08-20 2009-02-26 Robert Bosch Gmbh Axialkolbenmaschine in Schrägscheibenbauweise mit einer Stellvorrichtung
DE102009037733B4 (de) 2009-08-17 2021-12-09 Robert Bosch Gmbh Regelventilanordnung und Verstellpumpe
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DE102010006196A1 (de) * 2010-01-29 2011-08-04 Robert Bosch GmbH, 70469 Hydraulisches Vorsteuergerät
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DE102012218903B4 (de) * 2012-10-17 2023-02-16 Robert Bosch Gmbh Hydraulische Ventilanordnung und hydraulische Maschinenanordnung mit einer derartigen Ventilanordnung
RU2573429C1 (ru) * 2014-11-11 2016-01-20 Открытое акционерное общество "Конструкторское бюро химавтоматики" Блок клапанов
US9657561B1 (en) 2016-01-06 2017-05-23 Isodrill, Inc. Downhole power conversion and management using a dynamically variable displacement pump
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DE102017112700A1 (de) * 2017-06-08 2018-12-13 Schwäbische Hüttenwerke Automotive GmbH Steuerventil
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DE102018216831A1 (de) * 2018-10-01 2020-04-02 Robert Bosch Gmbh Regelvorrichtung für Pumpendruck und -volumenstrom mit konzentrischen Steuerschiebern
DE102019132269A1 (de) * 2018-12-03 2020-06-04 Komatsu Germany Gmbh Werkzeug zum Einstellen von Hochdruck-Hydraulikkreisläufen an Hydraulikbaggern
DE102022205536A1 (de) 2022-05-31 2023-11-30 Robert Bosch Gesellschaft mit beschränkter Haftung Ventilbaugruppe mit L-förmigem Hauptkörper, welcher eine Spülventilanordnung und eine Notlenkventilanordnung umfasst

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DE102020208933A1 (de) 2020-07-16 2022-01-20 Robert Bosch Gesellschaft mit beschränkter Haftung Regelventil mit radialer Ausnehmung im Bereich der ersten und der zweiten Blende

Also Published As

Publication number Publication date
EP1409873B1 (fr) 2009-04-15
US20050029484A1 (en) 2005-02-10
DE50213456D1 (de) 2009-05-28
US7044442B2 (en) 2006-05-16
WO2003014570A1 (fr) 2003-02-20
DE10136416A1 (de) 2003-02-13

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