WO2010072201A1 - Soupape pilote et machine hydraulique à commande par soupape - Google Patents

Soupape pilote et machine hydraulique à commande par soupape Download PDF

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Publication number
WO2010072201A1
WO2010072201A1 PCT/DE2009/001775 DE2009001775W WO2010072201A1 WO 2010072201 A1 WO2010072201 A1 WO 2010072201A1 DE 2009001775 W DE2009001775 W DE 2009001775W WO 2010072201 A1 WO2010072201 A1 WO 2010072201A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
armature
pilot
valve body
valve according
Prior art date
Application number
PCT/DE2009/001775
Other languages
German (de)
English (en)
Inventor
Jörg Weingart
Peter Schwaderer
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 WO2010072201A1 publication Critical patent/WO2010072201A1/fr

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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/54—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/024—Devices for relieving the pressure on the sealing faces for lift valves using an auxiliary valve on the main valve

Definitions

  • the invention relates to a pilot-operated valve according to the preamble of claim 1 and a valve-controlled hydraulic machine with such a valve.
  • valve-controlled hydraulic machines are known, for example, from EP 1 537 333 B1.
  • This document shows a hydraulic machine in axial or radial piston construction, which can be operated as a motor and as a pump, wherein the winning party Suction volume via the valve control is almost infinitely adjustable.
  • the hydraulic machine is designed as an axial piston machine, wherein a plurality of piston arranged in a cylinder is supported on a rotatably mounted swash plate.
  • Each of these pistons defined with the associated cylinder chamber a working space, which is connectable via a low-pressure side valve and a high-pressure side valve with a pressure medium inlet or a pressure medium drain.
  • the two valves are designed as electrically unlockable or lockable non-return valves, which can be controlled via the pump control and operated in the respective working space in "fill mode", "partial mode” or “idle mode”
  • the delivery or displacement volume can be infinitely varied from a maximum value to 0.
  • the hydraulic machine is operated via a control unit in accordance with a control algorithm in order to achieve a pulsation-free total displacement volume flow (pump) or total displacement volume flow (motor) This is often done according to a phase control, but it can also be performed after a Phasenabites- or phase cut control.
  • Hydraulic machines with variable via the valve control displacement / delivery volume is also called Digital Displacement Units (DDU).
  • DDU Digital Displacement Units
  • piston engines are advantageous, in particular in radial piston construction, since these make it possible to carry out the input and output separately for each displacer and thus to actively control it. It can make sense to switch between pump and motor operation. so that the control element for the low or high pressure connection can look different.
  • Such a control element is described for example in WO 2008/029073 A1.
  • This document shows a high-pressure side valve, which is designed with a pilot control.
  • This valve has a main stage with a valve body biased against a valve seat.
  • the valve body is penetrated by a pilot control hole, which is closed in a basic position by a pilot valve body, which is also the armature of an electromagnetic pilot actuator.
  • the pilot valve body When energizing this actuator, the pilot valve body performs a stroke and opens the pilot hole, so that the valve body is relieved in the closing direction and can be lifted by the pressure at the entrance of his valve seat.
  • the stroke of the valve body corresponds approximately to the stroke of the pilot valve body / armature.
  • a minimized in terms of space hydraulic machine requires a small valve in its overall dimensions with the largest possible and thus low-resistance flow cross-section.
  • a large flow cross-section requires a larger valve lift, which contradicts the requirement for high valve dynamics with the lowest possible electrical power consumption.
  • the requirements for the valve vary with different operating points of the hydraulic machine. For example, high flow rates result from high speeds, and demands for small switching times with low speeds are accompanied by long switch-on times for the solenoid coils.
  • the invention has for its object to provide a pilot operated valve and a hydraulic machine designed so that is suitable for a minimum space for large volume flows while still ensuring a high valve dynamics for controlling the hydraulic machine.
  • the pilot-operated valve is designed with a main stage and an electromagnetically actuated pilot control, the main stage having a valve body which is traversed by a pilot control flow path. This can be closed by means of a pilot valve body of a pilot actuator, wherein a stroke of an armature of this pilot actuator is directly or indirectly transferable to the pilot valve body.
  • a further main-stage armature is provided in addition to the pilot valve body associated with the armature, which comes after a partial stroke of the valve body in electromagnetic operative engagement to move this in a Endhub Schl and / or to keep there.
  • the valve body of the main stage has a valve disk which is biased against a valve seat and in which the pilot valve body is guided at least in sections and biased against a pilot seat of Vorêtströmungs- path.
  • This bias can be done for example via a tension spring which is supported on the valve disk.
  • a tension spring which is supported on the valve disk.
  • a guide bush on which the tension spring is supported.
  • a shift spring is provided which biases the pilot valve body against the pilot valve seat.
  • the armature of the pilot actuator is penetrated by a guide rod of the pilot valve body, which carries at its end portion a spring plate on which the aforementioned shift spring is supported, which also biases main stage armature in the direction of its basic position.
  • the main-stage armature is then preferably attached to the valve body or integrally formed therewith.
  • valve body may be designed, for example, with a rear hub projection on which the precursor armature is placed.
  • a projection extending toward the other armature can be formed on an armature, which protrusion dips into a corresponding recess of the other armature in the abovementioned end stroke range, so that the magnetic force on the armature is increased at a comparatively small stroke.
  • an anticlip plate or a paramagnetic coating can be provided between them, so that the closing time of the valve is minimized.
  • a guide bush in the direction of the pilot control armature protrude from the valve body and thus act as Antiklebeplättchen.
  • the guide bushing must be made of paramagnetic material.
  • Figure 1 shows a longitudinal section through an inventive pilot-operated valve, which can be used as a high-pressure side valve of a valve-controlled hydraulic machine;
  • Figure 2 shows the pilot operated valve of Figure 1 with open pilot control
  • FIG. 3 shows the valve from FIG. 1 with the main stage open.
  • Figure 1 shows a longitudinal section through a valve, which can be used for example as a fast-switching electrically unlockable high pressure valve of a DDU of the type described above.
  • a high pressure valve 1 is used to control the high pressure side inlet and outlet of the DDU.
  • the high pressure valve operates as a conventional spring-loaded check valve. During engine operation, it must be actively opened against the pending high pressure to release the pressure medium inflow to the displacement chamber.
  • the illustrated high pressure valve 1 is designed as a cartridge valve, which can be screwed into a receiving bore of the DDU or the hydrostatic displacer unit.
  • the radial port A with a high-pressure channel and the axial port B with a displacement of the hydraulic machine is in fluid communication.
  • the high-pressure valve 1 is designed as a pilot-operated valve and has a main stage 2, which is assigned to a pilot control 4.
  • the main stage 2 has a seat bushing 6, on which the radial port A formed by a radial bore star and the axial port B are executed.
  • a valve seat 10 is formed by a radial shoulder, against which in the illustrated basic position of the high pressure valve 1, a valve body 12 is biased.
  • This consists essentially of a valve plate 14, which is designed with a seat seat 16 at the end, the sealing in the basic position the valve seat 10 is applied.
  • the valve disk 14 has a downwardly extending in Figure 1, from the axial bore 8 out projection 18 which is penetrated by a pilot hole 20, which widens in Figure 1 upwards to a pilot valve seat 22. against this, a pilot valve body 24 is biased, the structure will be explained in more detail below.
  • valve disk 14 is stepped back on its side facing away from the valve seat 10 via a radial shoulder, so that the valve disk 14 merges into a rear hub projection 26 of the valve body 12.
  • the pilot control bore 20 is extended in the radially expanded region of the valve disk 14 and the hub projection 26 in the radial direction to a guide bore 28, in the back of a guide bushing 30 is inserted.
  • This may be made of paramagnetic material and protrude axially slightly beyond the back face of hub boss 26 to serve as anti-stick pads.
  • a main-stage armature 32 is placed on the outer circumference of the hub projection 26.
  • the material of the main stage anchor 32 is designed for optimal magnetic flux, while the spring plate 14 is designed in view of an optimized sealing effect and wear resistance.
  • the attachment of the main stage anchor 32 on the hub projection 26 can be done in any way, for example, by shrinking, welding, screwing or otherwise.
  • the main stage anchor 32 is plate-shaped with a in FIG. 1, which projects axially upwards in the circumferential direction.
  • valve body 12 in the seat sleeve 6 takes place along the outer circumferential surfaces of the main stage anchor 32 and the spring plate 14 - these sections are slidably guided along an inner guide 36 of the seat bushing 6.
  • the seat bushing 6 is inserted into a valve sleeve 38 which is screwed into the receiving bore of the hydraulic machine mentioned above.
  • a guide collar 40 which is guided axially displaceably in the guide bore 28.
  • the pilot valve body 24 is downgraded in the radial direction to a guide rod 42, which is guided over the guide bush 30.
  • a tensioning spring 44 engages the ring-shaped surface of the guide collar 40 at the top in FIG. 1, which in turn is supported on the adjacent annular end face of the guide bush 30, so that the pilot valve body 24 is preloaded in a sealing manner against the pilot valve seat 22 with its conical tip.
  • the guide rod 42 extends upward beyond the guide bushing 30 and passes through an armature 46 of the pilot control 4.
  • armature 46 On the out of this armature 46 extending end portion of the guide rod 42 is a bush-shaped, stepped spring plate 48 is placed on the a switching spring 50 attacks.
  • An annular end face 52 of the spring plate 48 which lies at the bottom in FIG. 1, bears against a stop surface 54 of the armature 46 so that it is flush with the adjacent end face of the seat bush by the bias of the switching spring 50 with a radially projecting stop lug 56 on the outer circumference of the armature 46 6 patch washer 58 is biased.
  • the armature 46 is embodied on its end face facing the main-stage armature 32 with an annular recess 57 whose geometry is adapted to the dimension of the projecting peripheral edge 34 of the main-stage armature 32.
  • a bobbin 62 In a receiving bore 60 of the valve sleeve 38, a bobbin 62, consisting of a coil carrier and a winding, is used, which can be energized by means of an electrical connection 64 to actuate the armature 46.
  • the bobbin 62 is supported at the top on a pole ring 66 and at the bottom by a further, konifizi establishen and non-magnetizable cone ring 68.
  • the function of this conical ring 68 is to seal the high pressure area to the coil and further to the valve environment. Furthermore, the magnetic flux runs around the cone ring 68, so that the field line profile according to FIG. 3 is established.
  • the axial securing in the opposite direction is effected by a front plate 74, which is connected via a fastening screw 76 with the axial pole piece 70 and is supported in the axial direction on the adjacent annular end face of the pole ring 66. This is in turn supported by a support shoulder 80 on a shoulder 78 of the valve sleeve 68, so that the entire pilot control is clamped in the valve sleeve 38.
  • the pole piece 70 is designed with a blind hole 82, at the end face of the switching spring 50 is supported and dip into the illustrated in the basic position of the spring plate 48 and the end portion of the guide rod 42 sections.
  • the above-described high pressure valve 1 operates as a check valve, which can be opened by the pressure in the displacement chamber (port B) against the force of the switching spring 50.
  • the higher pressure is applied to the radial port A, so that the high-pressure valve 1 must be opened against this high pressure.
  • FIGS. 2 and 3 are selected somewhat differently than in the illustration according to FIG. 1, but this is of no significance for the above explanations. From this other intersection, it is clear that the two armatures 46, 32 are each pressure-balanced by axially extending relief bores 86, 88.
  • a pilot control flow path between the two ports A, B is opened.
  • This precontrol flow path is indicated by dashed lines in the illustration according to FIG. 1 and is identified by the reference numeral 82.
  • bores are provided in the peripheral wall of the hub projection 26 and in the guide collar 40, which allow a control oil flow from port B through the open pilot valve seat, through the guide collar 40 and radially through the hub projection 26 to the port A.
  • valve disk 14 does not lift off its valve seat 10 immediately after opening the above-described pilot flow path, but only when the pressure level between the high pressure side and the low pressure side (displacement) is almost balanced, and thus in the closing direction due to the pressure difference across the valve Valve plate 14 effective force is smaller than the force acting in the opening direction of the tension spring 44th
  • the magnetic circuit is split, where due to the not shown, running through the main stage armature 34 part of the magnetic circuit already has an opening force on the main stage armature 34 acts.
  • the axial length of the pilot air gap 74 is less than the opening stroke H of the valve disk 14. That the guide rod 42 is only so far moved in the inventive principle, as it requires the pilot control fluidically.
  • the actual opening stroke is essentially due to the force of the electromagnet, wherein this opening stroke can in turn be adapted to the pressure and pressure medium volume flow conditions, so that closing of the high-pressure valve due to flow forces is virtually eliminated.
  • the valve body 12 may also be partially integrated into the magnetic flux even in the basic valve position.
  • the tension spring 44 can be made weaker. However, this is at the expense of the magnetic force on the armature 46 and thus at the expense of the achievable opening force of the pilot control.
  • the magnetic force between pilot control and main stage can be distributed over the geometric design of the main stage anchor 32.
  • valve body 12 is constructed in two parts with the valve plate 14 and the main stage armature 34, the latter being made of a magnetically favorable material. In principle, however, the valve body can also be formed in one piece.
  • the peripheral edge 34 of the main stage armature 34 dips into the corresponding annular recess 57 of the pilot 46 of the pilot control, before the two facing end faces of the two armatures 46, 34 come into abutment.
  • the characteristic of the magnetic force acting on the main stage armature 34 can be adapted to the respective conditions.
  • a projection on the armature 46 can be provided in kinematic reversal, which dips into a corresponding recess on the main stage armature 34.
  • the projections may have different geometries.
  • this projection can be cylindrical or trapezoidal and the corresponding wall regions of the other armature can then be bevelled.
  • other geometries for example a peripheral edge with a triangular or trapezoidal cross-section, can be selected instead of the ring-cylindrical peripheral edge 34.
  • the overlapping region can be chosen such that the characteristic curve is suitably adapted to the respective desired conditions.
  • an anti-sticking plate can still be provided in the respective contact areas.
  • a pilot-operated valve with an electromagnetically actuated pilot control and a valve-controlled hydraulic machine with such a valve in addition to an armature of the electromagnetically actuated pilot control, a further main stage armature is provided, via which a valve body of the main stage for opening a pressure fluid flow path can be moved into an open position.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne une soupape pilote avec une commande pilote actionnée électromagnétiquement et une machine hydraulique à commande par soupape équipée d'une telle soupape. Selon l'invention, il est prévu à côté d'une armature de la commande pilote actionnée électromagnétiquement une autre armature principale à circuits étagés par l'intermédiaire de laquelle un corps de soupape du circuit principal peut être déplacé dans une position d'ouverture pour ouvrir une voie d'écoulement de fluide sous pression.
PCT/DE2009/001775 2008-12-22 2009-12-16 Soupape pilote et machine hydraulique à commande par soupape WO2010072201A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008064408.0 2008-12-22
DE200810064408 DE102008064408A1 (de) 2008-12-22 2008-12-22 Vorgesteuertes Ventil und ventilgesteuerte Hydromaschine

Publications (1)

Publication Number Publication Date
WO2010072201A1 true WO2010072201A1 (fr) 2010-07-01

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ID=42115869

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2009/001775 WO2010072201A1 (fr) 2008-12-22 2009-12-16 Soupape pilote et machine hydraulique à commande par soupape

Country Status (2)

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DE (1) DE102008064408A1 (fr)
WO (1) WO2010072201A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105508627A (zh) * 2015-12-24 2016-04-20 华中科技大学 一种高压管路手动平衡式阀
CN106574727A (zh) * 2014-07-10 2017-04-19 弗路德自动控制系统有限公司 双孔口可变流动速率阀

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012109074A1 (de) 2012-09-26 2014-03-27 Sauer-Danfoss Gmbh & Co. Ohg Verfahren und Vorrichtung zur Ansteuerung einer elektrisch kommutierten Fluidarbeitsmaschine
EP2743555A1 (fr) * 2012-12-12 2014-06-18 Magna Steyr Fahrzeugtechnik AG & Co KG Soupape à plusieurs étages
DE102021104830A1 (de) 2021-03-01 2022-09-01 ECO Holding 1 GmbH Pneumatikventil zum Steuern eines gasförmigen Mediums
DE102022107951A1 (de) 2022-04-04 2023-10-05 ECO Holding 1 GmbH Pneumatikventil zum Steuern eines gasförmigen Mediums

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1168725B (de) * 1960-07-21 1964-04-23 Erich Herion Durchgangsmagnetventil mit elektromagnetischer Hilfsventilausloesung
US5735582A (en) * 1994-11-24 1998-04-07 Robert Bosch Gmbh Electromagnetically controllable valve arrangement
EP1537333B1 (fr) 2002-09-12 2006-06-14 Artemis Intelligent Power Ltd. Machine de travail fluidique et methode d'utilisation
WO2008029073A1 (fr) 2006-09-08 2008-03-13 Artemis Intelligent Power Limited Machine fonctionnant avec un fluide

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1168725B (de) * 1960-07-21 1964-04-23 Erich Herion Durchgangsmagnetventil mit elektromagnetischer Hilfsventilausloesung
US5735582A (en) * 1994-11-24 1998-04-07 Robert Bosch Gmbh Electromagnetically controllable valve arrangement
EP1537333B1 (fr) 2002-09-12 2006-06-14 Artemis Intelligent Power Ltd. Machine de travail fluidique et methode d'utilisation
WO2008029073A1 (fr) 2006-09-08 2008-03-13 Artemis Intelligent Power Limited Machine fonctionnant avec un fluide

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106574727A (zh) * 2014-07-10 2017-04-19 弗路德自动控制系统有限公司 双孔口可变流动速率阀
CN106574727B (zh) * 2014-07-10 2019-05-28 弗路德自动控制系统有限公司 双孔口可变流动速率阀
CN105508627A (zh) * 2015-12-24 2016-04-20 华中科技大学 一种高压管路手动平衡式阀
CN105508627B (zh) * 2015-12-24 2017-11-14 华中科技大学 一种高压管路手动平衡式阀

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