EP0624732B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0624732B1
EP0624732B1 EP94103381A EP94103381A EP0624732B1 EP 0624732 B1 EP0624732 B1 EP 0624732B1 EP 94103381 A EP94103381 A EP 94103381A EP 94103381 A EP94103381 A EP 94103381A EP 0624732 B1 EP0624732 B1 EP 0624732B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
control device
bore
slide
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
EP94103381A
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German (de)
English (en)
Other versions
EP0624732A1 (fr
Inventor
Gottfried Dipl.-Ing. Olbrich
Claus-Peter Kristen
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0624732A1 publication Critical patent/EP0624732A1/fr
Application granted granted Critical
Publication of EP0624732B1 publication Critical patent/EP0624732B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • 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
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves

Definitions

  • the invention is based on a hydraulic control device according to the genus specified in the preamble of claim 1.
  • a hydraulic control device is known from DE 37 09 504 A1 known for the load pressure independent control of an engine, those with a pressure compensator upstream of the directional control valve and a assigned secondary pressure relief valve works. It points the pressure relief valve on a device with which the Trigger pressure is hydraulically adjustable.
  • a disadvantage of this control device is that to achieve different Pressure values via an additional, separate switching valve can be controlled, which means the construction costs is increased. It is also shown in simplified form in this Control device disadvantageous that the adjustable secondary pressure limitation only be effective in one of the two motor connections can.
  • the hydraulic control device with the characteristic In contrast, features of the main claim have the advantage that with an LS directional control valve with individual pressure compensator and central Secondary pressure relief valve for both motor connections different Pressure settings possible for both motor connections will.
  • the control device can be relatively simple and Realize cost-effective construction by using the spring preload or load of the secondary pressure relief valve depending on the Slider actuation direction can be influenced by hydraulic actuating means is. It can be selected by the location of the control pressure tap specify on which side of the cylinder the higher one Pressure value should apply. So that's about the geometry of the spool at the same time an assignment between slide actuation direction and the higher pressure value of the secondary pressure relief valve given.
  • Directional valves previously available can expediently be used in the hydraulic control device according to the invention continue to be used.
  • Figure 1 shows a first embodiment of the hydraulic Control device with directional valve and individual pressure compensator in the Longitudinal section and in a simplified representation
  • Figure 2 shows a cross section according to II-II in Figure 1
  • Figure 3 shows a section according to III-III in Figure 1
  • Figure 4 shows a part of a second embodiment with other means.
  • Figure 1 shows in longitudinal section and in a simplified representation a first hydraulic control device in LS technology, so for a load pressure-independent control, in which a directional control Directional control valve 11 and an individually assigned, connected in series Pressure compensator 12 parallel to one another in a common axis Housing 13 are arranged.
  • the directional valve 11 has one Control slide 15, which in a housing 13 penetrating Slider bore 16 is guided.
  • this slide bore 16 are seven chambers 17 to 23 are formed, five of which lie side by side Chambers 17 to 21 of the directional control of the pressure medium flow serve and the two adjacent chambers 22, 23 to a metering orifice 14, which in a manner known per se with the Pressure compensator 12 works together.
  • the return chambers 17, 21 are with a return line, not shown, and the motor chambers 18th and 20 each with a motor connection 24 or 25 in connection.
  • the Chamber 23 serves as the first upstream orifice chamber and the chamber 22 as a second, outlet-side orifice chamber, from the from a channel 26 with a check valve 27 to the inlet chamber 19 leads.
  • System pressure compensator opens upstream of the check valve 27 a tap hole 28 in the channel 26.
  • the Pressure tap a pressure signal through hole 29, with the help the maximum control pressure for several actuators in parallel
  • Directional control valves to a controller of a variable displacement pump or to the System pressure compensator is directed to a load pressure independent
  • the Indian Spool bore 16 guided spool 15 is in through annular grooves six piston sections 31 to 36 divided. On his first, out the one end face 37 of the housing 13 projecting piston section 31 attacks a double-acting return device 38, which holds the control slide 15 in the neutral position shown.
  • Its sixth piston section protruding from the other end face 39 36 stands with an actuator, not shown in connection, with the help of the control slide 15 for directional control of the pressure medium flow to the motor connections 24 or 25 back or from them back into the return position in working positions can be moved, the size of the orifice plate 14 at the same time the pressure medium flow is adjustable.
  • the fifth piston section 35 which is in the region of the two orifice chambers 22, 23 forms the measuring orifice 14, has two control edges 42.
  • the pressure compensator 12 has a through hole 43 in the housing 13, which runs axially parallel to the slide bore 16 and which on the one side with a pressure relief valve 44 and on the other Side is closed with a plug 45.
  • this through hole 43 is a longitudinally movable control slide 46 of the pressure compensator 12 slidably guided.
  • an inlet chamber 47 and an adjacent flow chamber 48 Approximately at the orifice 14 of the directional valve 11 penetrates the through hole 43 an inlet chamber 47 and an adjacent flow chamber 48.
  • the inlet chamber 47 is via an inlet channel 49 with a pump connection 51 in connection.
  • a continuation channel 52 leads from the continuation chamber 48 to the first orifice chamber 23.
  • a connecting channel 53 an annular chamber 54 surrounding the through bore 43, which via a throttle connection 55 arranged in the control slide 46 constantly communicates with a control chamber 56 which controls the slide valve 46 encumbering standard spring 57.
  • the pressure in the Control chamber 56 which during the operation of the first control device 10 corresponds to the respective load pressure, thus works together with the Force of the control spring 57 on the left face of the control slide 46 and on the other hand is used for the function of the secondary pressure limitation limited by the pressure relief valve 44.
  • This pressure of Control chamber 56 acts on a spherical closing member 58 of the Pressure relief valve 44, which by a compression spring 59 an associated valve seat is pressed.
  • One the pressure relief valve 44 associated drain chamber 61 is via a drain line 62 with the first return chamber 17 of the directional valve 11 in Connection. As shown in FIG. 1 in connection with FIG. 3, is this drain line 62 by two perpendicular to each other Drain bores 63 formed in the housing 13 in one plane run, which between a formed by the slide 15, 46 Middle plane and an outer, first flange surface 64.
  • On a piston section located in the area of the forwarding chamber 48 65 of the control slide 46 is the volume flow through the Pressure balance 12 regulating control edge 66 is formed.
  • a hydraulic actuator 67 is mounted, thus is space-saving below the return device 38.
  • this Actuating unit 67 is a threaded sleeve 68 fixed to the housing Pressure chamber 69 formed.
  • a piston longitudinally movable bolt 71 slidably on the one hand from Pressure in the pressure chamber 69 is applied and with his other End supported on the closing member 58 of the pressure relief valve 44.
  • the Actuating unit 67 has an adjusting housing 72, in which an inclined Cross bore 73 the pressure chamber 69 with a in the housing 13 extending control longitudinal bore 74 connects.
  • This Longitudinal control bore 74 extends from the end face 37 and extends parallel to the through hole 43 and close to a second flange surface 75, as can be seen particularly clearly from FIG. 3. Furthermore, two are in the housing 13 starting from the bottom 76 control bores 77, 78 arranged parallel to one another, which run perpendicular to the control longitudinal bore 74 and the latter penetrate and in the areas on both sides of the inlet chamber 19 ends. Each end of the control bores 77, 78 is above each a blind hole 79 made by the flange surface 64 the slide bore 16 in connection. The blind holes 79 are arranged so that their connections in the housing Webs between the inlet chamber 19 and the first (18) or second Manufacture engine chamber 20.
  • the basic functions of the directional control of the Pressure medium flow to the two motor connections 24, 25 and the basic function of the orifice plate 14 in connection with the pressure compensator 12 provided for volume flow control as known per se as well as the basic function of a secondary pressure limitation through the pressure relief valve 44 in connection with the Individual pressure compensator 12.
  • control slide 15 in the directional control valve 11 based on Figure 1 deflected to the right in a working position is, with a pressure medium flow from the pump connection 51 via the inlet channel 49 by the control slide 46 with its control edge 66 controlled control throttle, the continuation channel 52, the partially open orifice 14, the channel 26, the check valve 27, the Inlet chamber 19 and the open left control edge 41 on the second Piston section 32 into the engine chamber 18 and on to the first Motor connection 24 flows.
  • the prevailing in the first motor connection 24 Load pressure also builds up in the downstream measuring throttle chamber 22 and acts via the connecting channel 53, the Annulus 54 and the throttle connection 55 in the control slide 46 also in the control chamber 56.
  • This load pressure acts in the control chamber 56 together with the force of the control spring 57 on one side of the Control slide 46, the other side of the pressure in the flow chamber 48 and thus acted upon by the pressure upstream of the orifice 14 becomes.
  • Measuring orifice 14 and control orifice 46, 66 are working on known way together to a load pressure independent control of the engine.
  • the downstream of the orifice 14th acting load pressure is also tapped via the tap hole 28 and forwarded to a system pressure compensator, not shown, at which, in a manner known per se, a maximum load pressure of the system can take effect.
  • the one in the first motor connection 24 and thus also effective load pressure in the control chamber 56 becomes additional for a secondary pressure limitation from the pressure relief valve 44 limited, that with the control slide 46 in the manner of a pilot-operated Pressure relief valve works together.
  • the second has the control slide 15 deflected to the right Piston section 32 with its left control edge 41 from the Blind hole 79 formed pressure signal tap controlled, see above that the prevailing in the first engine chamber 18 load pressure this pressure signal tap 79, the control bore 77, the control longitudinal bore 74 and the transverse bore 73 can act in the pressure chamber 69 and there loaded the bolt 71 working as a piston.
  • the locking link 58 of the pressure relief valve 44 is now not only by the Force of the compression spring 59 loaded, but also by the force of the pressurized bolt 71.
  • the response pressure of the Pressure relief valve 44 so increased that the function of the secondary pressure relief valve for the side of the first motor connection 24 is blocked.
  • the function of the secondary pressure limitation can So with the indicated flow direction to the first motor connection 24 do not take effect.
  • control slide 15 of the control device 10 based on Figure 1 from its neutral position to the left Deflected working position, so is pressure medium in a corresponding manner from the pump connection 51 via the control slide 46 and the metering orifice 14 controlled to the second motor connection 25.
  • control bore 78 by not shown Plug blocked inside, so that despite the control by the second piston section 32 no pressure signal is tapped.
  • the another control bore 77 is overridden by the second piston section 32, so that there is no pressure unit 69 in the actuating unit 67 Can build pressure.
  • the control bore 78 is here only to explain the light Configurability of the first control device shown and could in the case of the present function, they are also completely eliminated. To take effect of the pressure tap can be avoided instead of a sealing plug the associated blind hole 79 can also be omitted.
  • the present control device 10 can thus be used in particular Use loading cranes to realize occurring applications where the function of the secondary pressure relief valve 44 only for a single motor connection (25) should take effect while this function is simultaneously is blocked for the other motor connection 24.
  • the influence the common load pressure tap via the connecting channel 53 in a way that this is upstream from the distribution point of the volume flow to the motor connections 24, 25 can be done on this Be compensated for relatively easily.
  • the choice of the position of the pressure signal tapping point can dictate on which engine side 24, 25 the pressure relief valve 44 should be blocked. It can be used to determine the geometry of the Control spool or the directional valve 11 at the same time an assignment between slide actuation direction and secondary pressure relief valve function produce. The control device 10 can do this be changed that the pressure signal tap only on the Control bore 78 takes place so that when the pressure medium is supplied to the second motor connection 25, the secondary pressure relief valve 44 is blocked, while its function is effective at the motor connection 24 is.
  • Figure 4 shows a longitudinal section through part of a second Control device 90, which is different from the first control device 10 according to FIG. 1 primarily by another actuating unit 91, with the different high pressure values for the secondary pressure limiting function at the two motor connections 24, 25 are achievable; otherwise for the same components as in Figure 1 uses the same reference numerals.
  • actuating unit 91 there is an actuating piston in the threaded sleeve 68 92 slidably guided, the stroke of which with the aid of a stop ring 93 is adjustable.
  • the actuating piston 92 is also in the pressure Pressure chamber 69 can be acted upon and acts on a spring plate 94 which the compression spring 59 is supported.
  • pressurizing the Actuating piston 92 is thus in a through the stop ring 93rd limited dimensions the bias of the compression spring 59 and thus the response pressure of the pressure relief valve 44 increased.
  • the mode of operation of the second control device 90 corresponds in FIG essentially analogous to that of the first control device 10.
  • the pressure medium flow flows from the pump connection 51 to the first motor connection 24, a pressure signal is tapped via the control bore 77 and the actuating piston 92 acts on the actuating unit 91.
  • the bias of the compression spring 59 is increased accordingly and the Secondary pressure relief valve function is at a higher pressure value set.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (10)

  1. Dispositif hydraulique de commande avec un distributeur (11), approprié pour la commande d'un moteur, pour effectuer des commandes indépendamment de la pression de charge, distributeur dont le tiroir de commande (15), qui fonctionne comme un orifice de mesure, bloque dans une position neutre au moins une conduite conduisant au moteur, et relie alternativement, dans deux positions de travail, la conduite à une arrivée ou à un retour, et peut être actionné par un manomètre à piston (12) monté en amont du distributeur (11) et mis en série avec son orifice de mesure, manomètre à piston (12) dont l'organe de réglage peut être actionné par un ressort à l'encontre d'une pression différentielle provenant de la pression en amont de l'orifice de mesure et de la pression de charge, la pression de charge agissant dans une chambre de commande (56) qui est en liaison avec le côté se trouvant en aval de l'orifice de mesure et avec un point de prélèvement de la pression de charge, et la chambre de commande étant contrôlée par une soupape de limitation de pression (44) pour limiter, à l'aide du manomètre à piston (12), la pression en aval du distributeur à une valeur prédéterminée et, dans le cas de ce distributeur (11), le point de prélèvement de la pression de charge se trouvant en amont du point de distribution de l'écoulement du fluide sous pression vers les deux raccordements de moteur (24, 25),
    caractérisé par
    des moyens de réglage (67, 91), réglables hydrauliquement, pour modifier la pression de réponse de la soupape de limitation de pression (44), et
    au moins un canal de commande (73, 74, 77, 79) mène à une chambre sous pression (69) de ces moyens de réglage (67, 91), canal de commande (73, 74, 77, 79) dont on peut commander la liaison avec un raccordement de moteur (24), directement par le tiroir de commande (15) du distributeur (11).
  2. Dispositif de commande selon la revendication 1,
    caractérisé en ce que
    le canal de commande (73, 74, 77, 79) débouche dans une section de l'alésage de tiroir (16) qui est surrégulée par une section de piston (32) du tiroir de commande (15).
  3. Dispositif de commande selon la revendication 2,
    caractérisé en ce que
    la section de l'alésage de tiroir (16) se trouve entre une chambre d'arrivée (19) montée en aval de l'orifice de mesure (14), et une chambre de moteur adjacente (18, 20).
  4. Dispositif de commande selon l'une ou plusieurs des revendications 1 à 3,
    caractérisé en ce que
    les moyens de réglage (67 ; 91) présentent un piston (71, 92) qui peut être sollicité par la pression régnant dans la chambre sous pression (69), piston avec lequel l'organe d'obturation (58) de la soupape de limitation de pression (44) peut être sollicité en plus de l'action du ressort de compression (59).
  5. Dispositif de commande selon l'une ou plusieurs des revendications 1 à 3,
    caractérisé en ce que
    les moyens de réglage (91) présentent un piston (92) qui peut être sollicité par la pression régnant dans la chambre sous pression (69), et qui peut être déplacé contre une butée (93) solidaire du boítier, piston avec lequel on peut régler la précontrainte du ressort (59) dans la soupape de limitation de pression (44).
  6. Dispositif de commande selon l'une ou plusieurs des revendications 1 à 5,
    caractérisé en ce que
    la pression dans la chambre sous pression (69), quand l'alésage de commande (77, 78) est en position recouverte, se détend d'elle-même en passant à travers le tiroir de commande (15) et à travers la fente de guidage du piston (71, 92), vers le réservoir.
  7. Dispositif de commande selon l'une des revendications 1 à 6,
    caractérisé en ce que
    le canal de commande (73, 74, 77, 79) présente au moins deux alésages de commande (77, 74) qui s'étendent perpendiculairement l'un à l'autre, qui se croisent, et qui partent d'une face inférieure (76) et d'une face frontale (37) du boítier (13), et
    l'alésage de commande (77), qui part de la face inférieure (76), est en liaison avec l'alésage de tiroir (16) par l'intermédiaire d'un alésage de commande (79) pratiqué à partir d'une surface de bridage (64) et ayant la forme d'un trou borgne.
  8. Dispositif de commande selon l'une des revendications 1 à 7,
    caractérisé en ce que
    les moyens de réglage (67, 91) sont disposés essentiellement dans un boítier de réglage (72) qui est monté sur une face frontale (37) du boítier de distributeur (13), sur lequel est disposé aussi le dispositif de retour (38) pour le tiroir de commande (15).
  9. Dispositif de commande selon l'une des revendications 1 à 8,
    caractérisé en ce que
    le manomètre à piston (12), la soupape de limitation de pression (44) et l'unité de réglage (67, 91) sont disposés de façon coaxiale dans le boítier (13).
  10. Dispositif de commande selon l'une ou plusieurs des revendications 1 à 9,
    caractérisé en ce que
    dans la zone de prélèvement de pression de charge (53), on prévoit pour le manomètre à piston individuel (12), entre l'orifice de mesure (14) et la chambre d'arrivée (19), un alésage de prélèvement (28) pour un manomètre à piston de système.
EP94103381A 1993-04-15 1994-03-07 Dispositif de commande hydraulique Expired - Lifetime EP0624732B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4312257A DE4312257A1 (de) 1993-04-15 1993-04-15 Hydraulische Steuereinrichtung
DE4312257 1993-04-15

Publications (2)

Publication Number Publication Date
EP0624732A1 EP0624732A1 (fr) 1994-11-17
EP0624732B1 true EP0624732B1 (fr) 1998-01-21

Family

ID=6485496

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94103381A Expired - Lifetime EP0624732B1 (fr) 1993-04-15 1994-03-07 Dispositif de commande hydraulique

Country Status (2)

Country Link
EP (1) EP0624732B1 (fr)
DE (2) DE4312257A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1499807A1 (fr) * 2002-04-26 2005-01-26 Bosch Rexroth AG Ensemble distributeur ls
WO2011115647A1 (fr) * 2010-03-17 2011-09-22 Parker Hannifin Corporation Soupape à commande hydraulique comprenant un limiteur de pression
CN103328870B (zh) * 2011-02-01 2016-01-27 罗伯特·博世有限公司 压力加载的构件的壳体
US9810334B2 (en) 2013-01-31 2017-11-07 Parker-Hannifin Corporation Pressure limited flow priority boost

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3690051C1 (de) * 1985-02-23 1997-09-18 Barmag Barmer Maschf Proportionalventil mit einem einstellbaren Drosselventil zwischen Pumpe und Last sowie einer Druckwaage
DE3709504C2 (de) * 1987-03-23 1995-02-02 Rexroth Mannesmann Gmbh Ventileinrichtung
DE3915652C2 (de) * 1989-05-12 1996-10-24 Bosch Gmbh Robert Hydraulische Steuereinrichtung

Also Published As

Publication number Publication date
DE4312257A1 (de) 1994-10-20
DE59405062D1 (de) 1998-02-26
EP0624732A1 (fr) 1994-11-17

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