EP0405113A1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP0405113A1
EP0405113A1 EP19900109175 EP90109175A EP0405113A1 EP 0405113 A1 EP0405113 A1 EP 0405113A1 EP 19900109175 EP19900109175 EP 19900109175 EP 90109175 A EP90109175 A EP 90109175A EP 0405113 A1 EP0405113 A1 EP 0405113A1
Authority
EP
European Patent Office
Prior art keywords
control
slide
throttle
control device
collar
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
EP19900109175
Other languages
German (de)
English (en)
Inventor
Wolfgang Dipl.-Ing. Koetter
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 EP0405113A1 publication Critical patent/EP0405113A1/fr
Ceased 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

Definitions

  • the invention relates to a hydraulic control device for a fluid motor according to the preamble of the main claim.
  • Such a hydraulic control device is already known from DE-PS 29 30 390, which works with a directional control valve forming a first throttle device, the control slide of which controls a flow cross section proportional to the deflection of the slide and thus functions as a measuring orifice.
  • a pressure compensator is connected in series with the first throttle device as the second throttle device, which is acted upon by the load pressure and keeps the respective volume flow independent of the load pressure in a manner known per se.
  • a third throttle device which can be set independently from the outside and with which the volume flow can be individually limited to a maximum value while maintaining the load pressure-compensated control in end positions of the control slide, so that a single valve can be set to different, maximum volume flows.
  • the disadvantage is that such control devices with three separate throttle devices in series with each other build relatively complex and are therefore expensive.
  • the third throttle device with a rotatable, sleeve-forming slide sleeve requires a relatively large amount of installation space and is expensive. Above all, however, it is disadvantageous that this control device has a relatively small fine control range, since this is only effective over a partial stroke of the control slide and has a disadvantageous effect, in particular in the case of small volume flows.
  • the hydraulic control device with the characterizing features of the main claim has the advantage over the fact that it enables load pressure-independent control with an independent limitation of the maximum volume flow, manages with less effort and is more compact and cheaper. Furthermore, it has better fine control properties, since the fine control range extends over a larger part of the stroke.
  • FIG. 1 shows a longitudinal section through the hydraulic control device, partly in a simplified representation
  • FIGS. 2 and 3 each show partial sections according to II-II or III-III in FIG. 1
  • FIG. 4 shows a characteristic field, the individual characteristic curves of which show the course of the oil flow Q in Show dependence on the stroke S of the control spool.
  • FIG. 1 shows a hydraulic control device 10 for load pressure-compensated control of a fluid motor 11, the control device 10 essentially consisting of a hydraulic directional control valve 12 shown in longitudinal section and an upstream pressure compensator 13, which is shown in simplified form.
  • a hydraulic directional control valve 12 shown in longitudinal section and an upstream pressure compensator 13, which is shown in simplified form.
  • several such directional control valves 12 are flanged together and are arranged in a manner known per se, not shown in detail between a connection plate and an end plate, so that they form a control block which is supplied with pressure medium by a pressure medium source 14 via the connection plate.
  • the directional control valve 12 has a slide bore 16 in a housing 15, in which a longitudinally movable control slide 17 is tightly and slidably guided.
  • the slide bore 16 penetrates a number of chambers, of which a first throttle chamber 18 and an adjacent, second throttle chamber 19 are assigned to a first throttle device 21, approximately in the middle of the housing 15, which works as a measuring choke. Seen from the first measuring throttle chamber 18 towards the outside towards a first end face 22, the slide bore 16 penetrates in succession a first inlet chamber 23, a first motor chamber 24 and a first return chamber 25. In the opposite direction, the slide bore 16 penetrates one from the second measuring throttle chamber 19 second inlet chamber 26, a second motor chamber 27 and a second return chamber 28 before the slide bore 16 opens to a second end face 29 serving as the operating side.
  • the first measuring throttle chamber 18 is connected via a simplified inlet connection 31 and an inlet channel 32, into which the pressure compensator 13 is connected, to the outlet of the pressure medium source 14, which is designed here as a control pump.
  • the second measuring throttle chamber 19 is extended downwards and is penetrated by a longitudinal bore 33 which extends through the housing 15 and which extends essentially parallel to the slide bore 16. This multiple offset longitudinal bore 33 also penetrates the first (23) and second inlet chamber 26 and receives a first (34) and a second check valve 35.
  • These check valves 34, 35 each secure their associated inlet chambers 23, 26 and delimit a section 36 between them in the longitudinal bore 33, into which the second measuring throttle chamber 19 projects.
  • FIG. 1 shows a partial section according to II-II in FIG. 1
  • this section 36 there is also a pressure tapping point 37 which is assigned to a load pressure selection device 38 arranged in the housing 15 is.
  • This selection device 38 which is known per se, has a blind hole-like recess 41 which is open towards a first flange surface 39 and into which the pressure tap point 37 opens out and from which a control pressure channel 42 leads radially offset to a second flange surface 43 in the housing 15.
  • a seat valve body 44 Arranged in the blind hole-like recess 41 is a seat valve body 44 which selects the maximum load pressure from two supplied load pressure signals Y1 and Y2 and forwards it via the control pressure channel 42 as signal Y to a possibly adjacent block directional control valve or the connecting plate and further to a regulator of the pressure medium source 14 .
  • the two external return chambers 25 and 28 are connected to one another via a transverse channel 45 and additionally to a return channel 46.
  • the measuring throttle chambers 18, 19, in contrast to the other working chambers 24, 25, are not completely penetrated by the slide bore 16, but rather cut the slide bore 16 to the same extent.
  • Both throttle chambers 18, 19 are designed such that they extend approximately to the longitudinal axis of the slide bore 16.
  • a web 47 fixed to the housing remains between the measuring throttle chambers 18, 19 and extends in a plane perpendicular to the longitudinal axis of the slide bore 16.
  • this web 47 extends only over part of the circumference of the slide bore 16, in particular over half its circumference.
  • the slide bore 16 has a continuous circumferential surface in the area of both measuring throttle chambers 18, 19 and the web 47, which is approximately semicircular.
  • the control slide 17 has a control collar 48 which is located in the center relative to the working chamber through which pressure medium flows and which is assigned to both the first throttle device 21 and a third throttle device 49.
  • the control collar 48 has a first control edge 51, which is formed by a plurality of fine control recesses 52 distributed uniformly over the circumference, all of which have a basically identical shape and begin with their inner, closed ends together on a plane perpendicular to the Longitudinal axis of the control slide 17 extends. All of these fine control recesses 52 are open towards the first measuring throttle chamber 18 and are assigned to a first direction of movement when the control slide 17 - with reference to FIG. 1 - is deflected to the right.
  • second fine control recesses 53 are provided, which together form a second control edge 54.
  • the inner ends of the second fine control recesses 53 also lie on a plane that runs perpendicular to the longitudinal axis of the control slide 17 and are opened in a corresponding manner towards the second measuring throttle chamber 37.
  • These two control edges 51 and 54 form parts of the first throttle device 21 and thus take over the function of the orifice plate in the load pressure-compensated control of a volume flow to the engine 11 with the aid of the pressure compensator 13.
  • the control collar 48 is also part of the third throttle device 49, which is an independent adjustable limitation of the maximum volume flow.
  • control collar 48 has a third control edge 55, which is formed by a plane which extends obliquely to the longitudinal axis of the control slide 17 and thereby cuts the first fine control recesses 52 to different degrees.
  • This oblique, third control edge 55 facing the first measuring throttle chamber 18 is the assigned a direction of movement of the control slide 17, while a correspondingly arranged, fourth, oblique control edge 56 is provided for the other direction of movement of the control slide 17.
  • the third and fourth control edges 55, 56 thus form parts of the third throttle device 49 and give the control collar 48 in the longitudinal section according to FIG. 1 an approximately V-shaped appearance.
  • control collar 48 lies with its narrowest point, seen in the longitudinal direction, in the lateral surface in the central region of the semicircular web 47, while the longitudinal point of the broad surface of the control collar 48 lies on the inner wall of the slide bore 16 is present.
  • a first piston section 58 is formed on the control slide 17 between the first measuring throttle chamber 18 and the first motor chamber 24 and monitors the associated connection between the inlet chamber 23 and the motor chamber 24 with an inlet-side control edge 59.
  • An outer, second piston section 61 has a second, drain-side control edge 62, which monitors the connection from the first motor chamber 24 to the first return chamber 25.
  • an outer, fourth piston section 65 correspondingly has a control edge 66 on the outlet side.
  • a device 67 known per se is mounted coaxially to the control slide 17, which has a double-acting return device for the control slide 17, a mechanical latching device for certain working positions and a hydraulic one Has unlocking device. Furthermore, it can have a hydraulic final release, not explained in more detail, which taps the pressure in the second measuring throttle chamber 19 via an opening 68.
  • control slide 17 has an annular groove 69 in the area of the first piston section 58, with the aid of which, in the central position of the control slide 17 shown, the first inlet chamber 23 via a relief bore 71 to the transverse channel 45 and further to the return channel 46 is relieved.
  • the control slide 17 is formed and arranged in the housing 15 so that it can also perform a rotary movement about its longitudinal axis in addition to its longitudinal movement.
  • the control slide 17 On its fourth piston section 65 protruding from the housing 15 on the operating side 29, the control slide 17 therefore has a rotating device 72, by means of which it is coupled to an articulation part 73.
  • the articulation part 73 thus always remains in its position, regardless of the rotational position of the control collar 48.
  • the mode of operation of the control device 10 according to FIG. 1 is explained as follows, the function of which is only discussed to the extent necessary to understand the invention.
  • the basic function of an LS control, in which the volume flow should also be adjustable when the control slide is fully deflected, is assumed to be known per se.
  • the first measuring throttle chamber 18 and thus the inlet channel 32 connected to the variable displacement pump 14 are hydraulically blocked.
  • the motor chambers 24, 27 are hydraulically blocked by their associated control edges 59, 62 and 64, 66, respectively 42 is relieved via the selection device 38 known per se, the pressure tapping point 37 and the first check valve 34 to the first inlet chamber 23 and thus via the annular groove 69 and the relief bore 71 to the return channel 46. Accordingly, the control pump 14 works against a low back pressure.
  • control collar 48 opens a control cross-section from the first (18) to the second measuring throttle chamber 19 depending on its deflection. Simultaneously with the deflection of the control slide 17, the relief bore 71 becomes controlled so that the control pump 14 goes up in pressure. Proportional to the opening cross-section of the control collar 48 serving as a measuring throttle, a pressure medium flow finally flows from the control pump 14 via the pressure compensator 13 working as a second throttle device, the control collar 48 functioning as the first throttle device, via the first check valve 34 and the now open inlet-side control edge 59 into the first motor chamber 24 and on to the motor 11.
  • control device 10 is now to be limited to a smaller volume flow in the end position of the control slide 17, the control slide 17 is rotated 180 ° to its longitudinal axis with the aid of the rotating device 72, while the articulation part 73 maintains its position. In this way, the control collar 48 now lies with its widest point in the lowest point of the semicircular web 47.
  • the directional valve 12 is set to the smallest volume flow with the aid of the third throttle device 49, as shown in FIG Characteristic curve 75 is illustrated. As can be seen from FIG. 1 in connection with FIG. 4, all of the first fine control recesses 52 have the same opening start.
  • the tax facility device 10 can be limited to any volume flow between the characteristic curves 74 and 75, for example by turning the control slide 17 from its drawn position by 90 ° to set the characteristic curve 76.
  • the characteristic curves 74 to 76 make it clear that the fine control is adapted to the volume flow in a particularly advantageous manner and thus extends over the major part of the stroke s of the control slide 17.
  • the dashed curves 77 show the conditions in the previously known valve, where the fine controllability is only limited to partial strokes, which has a disadvantageous effect, in particular when the volume flow is set to be small.
  • control device 10 can also be modified such that the second throttle device is connected downstream or is in the bypass instead of the upstream pressure compensator. It is also possible to design the third throttle device so that it is only effective in one direction of movement of the control slide 17. Likewise, the shapes of the fine control recesses 52, 53 and the shape of the third and fourth control edges can be varied within limits.

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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)
EP19900109175 1989-06-30 1990-05-16 Dispositif de commande hydraulique Ceased EP0405113A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3921445 1989-06-30
DE19893921445 DE3921445A1 (de) 1989-06-30 1989-06-30 Hydraulische steuereinrichtung

Publications (1)

Publication Number Publication Date
EP0405113A1 true EP0405113A1 (fr) 1991-01-02

Family

ID=6383956

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900109175 Ceased EP0405113A1 (fr) 1989-06-30 1990-05-16 Dispositif de commande hydraulique

Country Status (2)

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EP (1) EP0405113A1 (fr)
DE (1) DE3921445A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014121088A1 (fr) * 2013-01-31 2014-08-07 Parker-Hannifin Corporation Vanne de commande de direction ayant des encoches de mesure sur le tiroir pour limiter le flux dans la position d'extrémité ouverte

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2033429A1 (de) * 1969-07-07 1971-01-21 Eaton YaIe & Towne Ine , Cleve land, Ohio (V St A ) Wegeventil
EP0224936A2 (fr) * 1985-12-06 1987-06-10 Karl-Thomas Dipl.-Ing. Rhody Soupape directionnelle à commande proportionnelle avec balance de pression séparée
DE3629849A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil
DE3629850A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2033429A1 (de) * 1969-07-07 1971-01-21 Eaton YaIe & Towne Ine , Cleve land, Ohio (V St A ) Wegeventil
EP0224936A2 (fr) * 1985-12-06 1987-06-10 Karl-Thomas Dipl.-Ing. Rhody Soupape directionnelle à commande proportionnelle avec balance de pression séparée
DE3629849A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil
DE3629850A1 (de) * 1986-09-02 1988-03-03 Bosch Gmbh Robert Hydraulisches wegeventil

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014121088A1 (fr) * 2013-01-31 2014-08-07 Parker-Hannifin Corporation Vanne de commande de direction ayant des encoches de mesure sur le tiroir pour limiter le flux dans la position d'extrémité ouverte
KR20150114533A (ko) * 2013-01-31 2015-10-12 파커-한니핀 코포레이션 개방 단부 위치에서 감소된 흐름을 위한 스풀 상의 계측 노치를 갖는 방향 제어 밸브
US9689500B2 (en) 2013-01-31 2017-06-27 Parker-Hannifin Corporation Pressure limited flow spool

Also Published As

Publication number Publication date
DE3921445A1 (de) 1991-01-03

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