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EP1409873B1 - 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 Download PDF

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Publication number
EP1409873B1
EP1409873B1 EP02758348A EP02758348A EP1409873B1 EP 1409873 B1 EP1409873 B1 EP 1409873B1 EP 02758348 A EP02758348 A EP 02758348A EP 02758348 A EP02758348 A EP 02758348A EP 1409873 B1 EP1409873 B1 EP 1409873B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve block
return spring
block according
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.)
Expired - Lifetime
Application number
EP02758348A
Other languages
German (de)
English (en)
Other versions
EP1409873A1 (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

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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

  • the invention relates to a valve block according to the preamble of claim 1.
  • a valve block of this kind is for example in the US-A-2 299 234 or in the DE 199 53 170 A1 described.
  • a power control valve and a control valve are provided, the latter being acted upon in response to the difference between the working pressure in a working line of the hydraulic pump and the pressure upstream of the power control valve in a power control line of an adjusting device for the hydraulic pump with control pressure.
  • the control valve can be acted upon by means of an actuator with a variable additional force. 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 as a function of the operating situation.
  • the invention has for its object to simplify the adjustment in a valve block according to the preamble of claim 1 and to improve safety.
  • the adjusting movement of the actuator is limited in its closing force increasing the direction of movement by a stop element in a position in which the closing force corresponds to its limited maximum value.
  • the embodiment 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 of the valve block.
  • the attachment can be prefabricated or preassembled not only in terms of the actuator, but also in terms of the stop element, so that it only requires an assembly of the attachment to the valve block to complete the valve according to the invention.
  • an adjusting disc in the form of a spring plate whose edge is tapered on both sides so far that the adjusting disc can be mounted in a radially enlarged base region of a blind hole of the attachment.
  • Another advantage of the embodiment of the invention is the fact that it can be combined with existing designs in a simple manner and integrate it.
  • valve block is part of a designated in its entirety by 2 adjusting device for adjusting and adjusting the flow rate of a hydrostatic machine, here a hydraulic pump 3.
  • the adjusting device 2 has an adjusting cylinder 4, which is hydraulically effective in the embodiment on one side and in per se known Way of a cylinder 4a and a displaceably mounted therein piston 4b and an associated piston rod 4c, which is connected to an adjuster shown 3a of the pump 3.
  • the hydrostatic machine can be formed instead of by a hydraulic pump 3 by a hydraulic motor adjustable throughput volume.
  • the valve block 1 at least four hydraulic connections, namely a working pressure port P, a pitch pressure port A, a tank port T and a control port X.
  • the hydraulic pump 3 is connected to a Drive shaft of a drive motor, not shown in drive connection, z. B. with an internal combustion engine. In functional operation, the hydraulic pump 3 sucks 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.
  • the valve block 1 may have only one valve 9.
  • two valves 9, 11 are provided, of which the valve 9 is a pressure regulating valve and the valve 11 is a flow control valve.
  • An input of the pressure regulating 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 delivery flow restrictor 8.
  • the valve piston 14 of the pressure control valve 9 can be acted upon by a connected to the working line branch 7a connecting line 13 with the working pressure and against the force of a return spring 15, the spring force by an actuator 16a of an adjustment 16 is selectively reduced and increased.
  • the flow control valve 11 is connected by a first connecting line 21 with the working line 7 upstream of the flow restrictor 8 and with the working line branch 7a and connected 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 and the adjusting cylinder 4 so that the flow restrictor 8 is flowed through by a constant flow rate.
  • the flow control valve 11 is acted upon by the connecting lines 21, 22 of the pressure drop across the delivery flow restrictor 8.
  • valve piston becomes 23 of the flow control valve 11 is moved against a return spring 24 from its first valve position d in the direction of its second valve position c.
  • control pressure in the control pressure chamber 4d of the adjusting cylinder 4 is regulated via the control pressure line 25.
  • the control pressure in the control pressure chamber 4d of the adjusting cylinder 4 is increased and the displacement volume of the hydraulic pump 3 is swiveled back in the direction of a smaller displacement volume.
  • the flow rate which is determined by the load connected to the working line 7, can be varied by changing the cross section of the preferably adjustable flow restrictor 8.
  • the valve piston 14 is moved from the illustrated first valve position b to the second valve position a, in which the adjusting pressure chamber 4d extending portion of the control pressure line 25 is connected to the connecting line 12 and the working line branch 7a.
  • the loading of the control pressure chamber 4d is increased with the control pressure and adjusted the displacement volume to a value which results in a working pressure not exceeding the predetermined value.
  • the flow control valve 11 has a connection which is connected by a connecting line 26 to the tank 6 and in the valve position d corresponds to the connection for the control pressure line 25.
  • the control pressure line 25 is connected between the valves 9, 11 through a connecting line 27 with a first discharge throttle 28a to the tank 6.
  • control pressure line 25 or the control pressure chamber 4d is optionally connected by a second relief throttle 28b to the first relief throttle 28a and also connected thereto by the tank 6.
  • the flow control valve 11 and the pressure control valve 9 are each formed as a 3/2-way valve.
  • the flow control valve 11 has an adjusting device 31 with an adjusting member 31a, with which the spring force of the return spring 25 is selectively reduced or increased.
  • the adjusting members 16a, 31a are selectively reciprocable and mounted lockable in the respective setting position.
  • the direction of movement of the adjusting 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 adjusted by motor, z. B. by an electromagnet, in particular a proportional magnet.
  • the actuators 16a and 31a act in the embodiment axially on an abutment 32 of the associated return spring 15 and 24, wherein the abutment 32 is preferably formed by a support plate 19 in the sense of a spring plate, which in the following reference Fig. 1 is described, which shows a compact and therefore inter alia, for this reason advantageous embodiment of the valve block 1.
  • the transverse bores 52, 53 are each closed by a threaded plug 54 or 55.
  • the valve piston 23 has a first annular recess 56 which is connected via a connecting channel 58 to the working pressure port P.
  • the annular recess 56 is adjoined by an enlarged diameter portion 59, on which a first control edge 60 is formed.
  • the valve piston 23 has a second annular recess 61 which is connected via a connecting channel 62 to the tank port T.
  • the second annular recess 61 is adjoined by an enlarged diameter portion 92, on which a second control edge 63 is formed.
  • valve piston 23 of the flow control valve 25 in his in Fig. 2 shown rest position by the associated return spring 24 in Fig. 1 is shifted to the left, the second control edge 63 is opened and a connecting channel 64 is connected via the connecting channel 62 to the tank port T.
  • the annular recess 56 is connected via a formed in the valve piston 23 longitudinal bore 65 with a formed between a first pressure-engaging surface 66 and the stopper 55 first pressure chamber 67.
  • the pressure application surface 66 formed by the left end face of the valve piston 23 is acted upon by the working pressure.
  • the restoring force increase generated by the actuator 31a is introduced into the valve piston 23 via the support disk 19 and the return spring 24. Of the Valve piston 23 therefore adjusts itself so that the force exerted by the working pressure with the force applied by the return spring 24 counterforce is in equilibrium.
  • the valve piston 14 for the pressure control valve 9 is inserted into the second transverse bore 53.
  • the valve piston 14 has a first annular recess 77, which communicates via the connecting channel 58 with the working pressure port P.
  • the first annular recess 77 is adjoined by an enlarged diameter portion 78 on which a first control edge 79 is formed.
  • a second annular recess 80 is further formed, which is in communication with the connecting channel 64.
  • the second annular recess 80 is adjoined by an enlarged diameter portion 81 on which a second control edge 82 is formed.
  • the second valve piston 14 by the return spring 15 at its in Fig. 1 pressed left stop so that the second control edge 82 is open.
  • the return spring 15 abuts against a spring plate 83, which is held on the valve piston 14 in abutment.
  • the externally accessible actuator 16a In the screwed into the body 51 receiving body 84 is the externally accessible actuator 16a, with which the axial position of the support plate 19 and thus the bias of the second return spring 15 can be changed.
  • valve piston 14 is a blind bore designed as a longitudinal bore 87, which opens at a formed between the plug 54 and the valve piston 14 third pressure chamber 88, so that the third pressure chamber 88 is connected to the working pressure port P.
  • the working pressure acts on a first pressurization 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 return spring 15.
  • valve head 14 In the region of the connecting channel 62, the valve head 14 has a passage 93.
  • a longitudinal bore 94 extends to the control pressure port A.
  • a closure plug 96 In the penetration region between the connecting channel 64 and the longitudinal bore 94 is a closure 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. Further, the blind bore 97 via a second transverse bore 99, which forms the second relief throttle, connected to the control pressure port A.
  • the adjusting devices 16, 31 are respectively arranged on receiving bodies 72, 84 which are add-on parts, in particular screw-in parts, of the main body 51.
  • the receiving bodies 72, 84 each have an axial through hole with two through-hole portions 101, 102.
  • the main body 51 facing through-hole portion 101 is respectively the recording of the associated return spring 15 and 24.
  • the main body 51 facing away from the through hole portion 102 serves each receiving the associated actuator 16a, and 31a.
  • the actuators 16a, 31a are each formed by a spindle drive
  • the adjusting screw 103 is screwed into the formed as a threaded bore hole section 102 and is axially adjustable by turning.
  • the respective adjusting screw 103 is from the outside to a rotary control element, not shown, for.
  • As a slot or a hexagon for a screwdriver accessible and lockable by a screwed lock nut 105 which abuts the receiving body 72 and 84 in the embodiment.
  • the end portion of the adjusting screw 103 projecting beyond the lock nut 105 is covered by a cap 106 screwed on, which is provided for the purpose of mechanical protection and / or sealing.
  • the cap 106 has at its threaded hole edge on a preferably radial end face, with which it rests against a preferably radial end face of the lock nut 105.
  • radial end faces are preferably also provided.
  • the abutting faces can each be sealed by a ring seal, z.
  • Example, by an O-ring 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 and 84, respectively.
  • the sealing ring 107 is axially elastically compressed in the screwed state, whereby the seal is achieved.
  • an adjustability-ensuring clearance 104 for the associated adjusting screw 103 is provided for the associated adjusting screw 103.
  • 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 which are respectively screwed into a corresponding threaded bore in the main body 51 with a screw sleeve 72a or 84a surrounding the inner through-hole portion 101 and, if appropriate, rest against the base body 51 with the shoulder surface of a compacted head.
  • a ring seal preferably a special sealing ring 109 may be provided in the edge region of the screw-in hole.
  • the support plate 19 and its surrounding area ir the receiving body 84 is particularly formed, as will be explained below.
  • the support disk 19 is located in an axial adjustment range in the transition region between the hole sections 101, 102.
  • the adjustment range for the support disk 19 is limited by a stop 112, which is located in is an axial position in which the pressure control valve 9 sets or limits a pressure, here the control pressure, which corresponds to the maximum allowable pressure.
  • the stopper 112 is formed by a step surface 114 facing away from the base 51 at the inner through-hole portion 101, wherein the step surface 114 defines a hole extension 115, which is located between the through-hole portions 101, 102.
  • the support disk 19 In order to mount the support disk 19, it is tapered on both sides to a dimension e, preferably flattened, which is smaller than the cross-sectional size of the inner through-hole portion 101. Consequently, the support disk 19 can be in a rotated relative to the stop 112 by 90 ° position move the through-hole portion 101 into the hole extension 115.
  • the latter is so large in terms of their axial and radial dimensions that the support plate 19 can be pivoted in the hole extension 115 in its operating position in which it is parallel to the stop 112.
  • the hole enlargement 115 has, at least in its axial region facing the stop 112, a preferably conical, inner circumferential surface 113 that converges toward the stop 112. By this convergent inner circumferential surface 113, the support plate 19 is centered when moving in the direction of the stop 112 when it should have taken an eccentric position when pivoting.
  • the support disk 19 is shown in several pivot intermediate positions.
  • the stop 112 and the stop member by a spring ring which is inserted into an annular groove in the inner circumferential surface of the inner through-hole portion 101.
  • the support plate 19 For mounting the support plate 19, whose size is adapted in this case with play on the cross-sectional size of the hole portion 101, the support plate 19 is first to be inserted into the through-hole portion 101 and then to mount the spring ring 116 which projects beyond the inner circumferential surface of the through-hole portion 101 and thus as Stop 112 can serve.
  • the support disk 19 may be round.
  • an electromagnet or an electric motor in particular a stepping motor, can be used, which z. B. via a threaded spindle, the bias of the return spring 15 and 24 and thus the force exerted on the valve piston 14 and 23 additional force changed.
  • the support plate 19 of the flow control valve 11 and its surroundings in the receiving body 72 may be formed as described above with reference to the pressure control valve 9.
  • the above-described stop limit for the maximum value of the restoring or closing force of the return spring can thus be realized in a corresponding embodiment also in the flow control valve 11 or another valve.

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  • 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.

Claims (11)

  1. Bloc de distribution (1) pour dispositif de régulation, notamment pour machine hydrostatique, le bloc de distribution comportant un distributeur (9) dont le piston (14) est soumis à une pression de régulation pour l'amener en position d'ouverture et à un ressort de rappel (18) pour l'amener en position de fermeture,
    la force de fermeture exercée par le ressort de rappel (15) pouvant être réduite ou augmentée par un actionneur (16a), qui peut être déplacé dans une position augmentant la force de fermeture et dans une position réduisant la force de fermeture,
    caractérisé en ce que le déplacement de l'actionneur (16a) dans le sens de déplacement augmentant la force de fermeture du ressort de rappel (15) est limité par un élément de butée (112) dans une position dans laquelle la force de fermeture exercée par le ressort de rappel (15) atteint sa valeur maximale limitée.
  2. Bloc de distribution selon la revendication 1, caractérisé en ce que l'élément de butée (112) est formé par une surface en gradin (114), opposée au piston du distributeur (14), dans un orifice (101) de réception des ressorts de rappel (15).
  3. Bloc de distribution selon la revendication 2, caractérisé en ce que le ressort de rappel (15) s'appuie contre un disque d'appui (19), contre lequel agit l'actionneur (16a), et coopère avec l'élément de butée (112).
  4. Bloc de distribution selon la revendication 3, caractérisé en ce que la surface en gradin (114) limite une partie élargie (115) de l'orifice, dans laquelle est disposé le disque d'appui (19) conformé pour être plus grand que l'orifice de réception (101).
  5. Bloc de distribution selon la revendication 3 ou 4, caractérisé en ce que, du côté du disque d'appui (19) qui est opposé au piston du distributeur (14), l'actionneur (16a) est disposé de façon à être mobile axialement dans une portion d'orifice (102), de préférence coaxiale,
  6. Bloc de distribution selon la revendication 5, caractérisé en ce que, sur des côtés opposés, le disque d'appui (19) est rétréci à une largeur (e) inférieure à la section de l'orifice de réception (101), et en ce que la partie élargie (115) de l'orifice a une dimension telle que le disque d'appui (19) est apte à pivoter dans la partie élargie (115) de l'orifice.
  7. Bloc de distribution selon la revendication 5 ou 6, caractérisé en ce que l'actionneur (16a) est formé par une commande par vis qui comporte une vis de réglage (103), qui est vissée dans la portion d'orifice extérieure (102).
  8. Bloc de distribution selon l'une des revendications précédentes, caractérisé en ce que l'élément de butée (112) et l'actionneur (16a) sont disposés dans une partie rapportée (84) du bloc de distribution (1).
  9. Bloc de distribution selon la revendication 8, caractérisé en ce que la partie rapportée (84) est fixée au bloc de distribution (1) par vissage.
  10. Bloc de distribution selon l'une des revendications précédentes, caractérisé en ce que le distributeur est un distributeur de régulation de pression (9), par exemple un distributeur de limitation de pression ou un distributeur de régulation de débit (11).
  11. Bloc de distribution selon la revendication 10, caractérisé en ce que le distributeur de régulation de pression (9) ou le distributeur de régulation de débit (11) est disposé dans une conduite de pression de commande (24) qui s'étend en direction d'un piston de commande (4) qui est destiné à régler le volume de déplacement de la machine hydrostatique.
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 EP1409873A1 (fr) 2004-04-21
EP1409873B1 true 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)

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DE102018216831A1 (de) * 2018-10-01 2020-04-02 Robert Bosch Gmbh Regelvorrichtung für Pumpendruck und -volumenstrom mit konzentrischen Steuerschiebern
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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Publication number Priority date Publication date Assignee Title
DE102018216831A1 (de) * 2018-10-01 2020-04-02 Robert Bosch Gmbh Regelvorrichtung für Pumpendruck und -volumenstrom mit konzentrischen Steuerschiebern
US11353120B2 (en) 2018-10-01 2022-06-07 Robert Bosch Gmbh Regulating device for pump pressure and pump volumetric flow rate, having concentric control slide valves
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
US11512784B2 (en) 2020-07-16 2022-11-29 Robert Bosch Gmbh Control valve having a radial recess in the region of the first and the second orifice

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WO2003014570A1 (fr) 2003-02-20
DE10136416A1 (de) 2003-02-13
DE50213456D1 (de) 2009-05-28
US7044442B2 (en) 2006-05-16
EP1409873A1 (fr) 2004-04-21
US20050029484A1 (en) 2005-02-10

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