EP0384157A2 - Soupape à deux voies à commande pilotée hydrauliquement en manière à siège - Google Patents

Soupape à deux voies à commande pilotée hydrauliquement en manière à siège Download PDF

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Publication number
EP0384157A2
EP0384157A2 EP19900101628 EP90101628A EP0384157A2 EP 0384157 A2 EP0384157 A2 EP 0384157A2 EP 19900101628 EP19900101628 EP 19900101628 EP 90101628 A EP90101628 A EP 90101628A EP 0384157 A2 EP0384157 A2 EP 0384157A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
closing body
piston
closing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19900101628
Other languages
German (de)
English (en)
Other versions
EP0384157B1 (fr
EP0384157A3 (fr
Inventor
Heinz Ing. Walter (Grad.)
Dirk-Walter Dipl.Ing. Herold (Fh)
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 EP0384157A2 publication Critical patent/EP0384157A2/fr
Publication of EP0384157A3 publication Critical patent/EP0384157A3/fr
Application granted granted Critical
Publication of EP0384157B1 publication Critical patent/EP0384157B1/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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves

Definitions

  • the invention is based on a hydraulically controllable 2-way cartridge valve in seat valve design according to the preamble of the main claim.
  • the built-in valve has an actuating device in which an actuating piston is arranged in a separate housing part, which in turn can be mounted on a commercially available standard cartridge like a cover.
  • the pressure surfaces for opening and closing are formed on opposite surfaces of the same actuating piston in the actuating device.
  • the hydraulically pilot-operated 2-way cartridge valve according to the invention with the characterizing features of the main claim has the advantage that it allows a simpler and more cost-effective design with high functional reliability while maintaining the previous range of functions. Due to the fact that in the actuating device the space relieved of the tank is always between the pressure surfaces for opening and closing, there can be no mutual interference between the two pressure spaces by leakage oil. The effort for sealing on the actuating piston is thus less and can be sufficient with a seal as in the area of the usual slide / housing tolerances and thus also reduce the friction in the valve. From each other Separate components such as the closing body and locking piston run in two separate housing parts, which enables simple, inexpensive production. The locking piston itself is only acted upon on one side by the control pressure medium.
  • the built-in valve can be further designed by connecting its pressure chambers in such a way that it can be used as an unblockable check valve in both flow directions.
  • the cartridge valve can therefore be used advantageously in safety circuits to meet a wide variety of requirements.
  • the actual cartridge can still be used separately for other functions.
  • a design according to claim 2 is particularly expedient, as a result of which almost all of the measures required for the actuating device can be accommodated in the cover, so that largely a standardized, commercially available standard cartridge with an associated housing can be used. This enables an inexpensive construction.
  • Formations according to claims 3 to 5 are also expedient, whereby a simple and cheap construction is favored in each case.
  • a non-positive connection between the closing body and the actuating piston is sufficient, with all moving parts being guided in separate components, so that the built-in valve can be produced easily and inexpensively.
  • the actuating piston is arranged directly on the closing body, so that when the opening pressure surface on the actuating piston is acted upon, the closing body is carried along during an opening stroke.
  • This not only leads to greater functional reliability of the built-in valve, but also enables a lower flow resistance, since the built-in valve does not act when this open-pressure surface is pressurized in the main flow must be flowed through against spring force.
  • the built-in valve now comes with 5 pressure chambers, with only one pressure chamber in the cover.
  • An embodiment according to claim 7 or 8 favors simple manufacture of the cartridge valve, especially since the pressure-relieved space is limited by the separating surface between the two housing parts.
  • the locking piston is additionally loaded by a spring.
  • the closing pressure surface on the locking piston can be of the same size as the sum of the ring surface and circular surface on the closing body. This favors a compact design.
  • the spring ensures a non-positive coupling of the locking piston and closing body and also promotes a faster closing function of the cartridge valve. Also, in certain operating states, the forward resistance when the cartridge flows through is not adversely affected by the spring. The spring also enables an exact assignment between the signal of the position monitoring and the position of the locking piston.
  • the built-in valve is used in a safety circuit, as is used in particular in plastic machines or presses for controlling the locking cylinder or in comparable systems. Further advantageous embodiments result from the remaining claims, the description and the drawing.
  • FIG. 1 shows a longitudinal section through a first 2-way cartridge valve in a simplified representation
  • FIG. 2 shows a longitudinal section through a second exemplary embodiment of the cartridge valve
  • FIG. 1 shows a hydraulically pilot-controllable, two-way cartridge valve 10 constructed in the manner of a seat valve, which essentially consists of a housing 12 receiving a valve cartridge 11 and a cover 14 receiving an actuating device 13.
  • the housing 12 has a recess 15, to which a first connection 16 denoted by A in the axial direction and a second connection 17 denoted by B lead in the radial direction.
  • the actual valve cartridge 11 is inserted into the recess 15, so that its closing body 19, which is mounted in a cartridge sleeve 18, controls the connection between the two connections 16, 17.
  • the cartridge case 18 is further secured by a cartridge guide 21 inserted into the recess 15, which also acts as a partition between different pressurized chambers.
  • the closing body 19 is guided in the cartridge case 18 with a guide part 22, the outer diameter of which is larger than the associated seat diameter 23. In this way, a circular surface 24 is formed on the closing body 19, which in the illustrated blocking position of the closing body 19 is dependent on the pressure in the first connection 16 is acted upon while an associated annular surface 25 is acted upon by the pressure in the second connection 17.
  • the cover 14 has a stepped bore 29, which runs coaxially to the recess 15 and to whose first section 31 with a large diameter adjoins a second section 32 with a smaller diameter.
  • an actuating piston 33 is guided tightly and slidably, while in the inner section 32 a locking piston 34 is guided tightly and slidably.
  • Actuating piston 33 and locking piston 34 are formed in one piece with one another and form parts of the actuating device 13.
  • the actuating piston 33 is non-positively coupled to the closing body 19 via a plunger 35, the plunger 35 being guided tightly and slidingly in the partition wall 21.
  • the cross-sectional area of the plunger 35 is considerably smaller than the annular surface 25 or the circular surface 24.
  • the diameter of the actuating piston 33 is larger than the diameter of the locking piston 34, which in turn is larger than the diameter of the guide part 22 on the closing body 19 and locking pistons 34 together delimit in the first section 31 an annular space 36 which is continuously relieved to the tank 28 via a channel 37.
  • the actuating piston 33 borders with an open pressure surface 38 on a first pressure chamber 39, into which the plunger 35 protrudes with one end and which, via a control channel 41 and a 4/2 switching valve 42, optionally with the pressure from a Pump or pressure medium source 43 can be acted upon or relieved to the tank 28.
  • the locking piston 34 includes in the second section 32 a second pressure chamber 44, the pressure of which acts on a circular closing pressure surface 45 of the locking piston 34. Furthermore, a closing spring 46 loading the locking piston 34 is arranged in the second pressure chamber 44. The position of the locking piston 34 can be queried via an electromechanical displacement sensor 47.
  • the second pressure chamber 44 is directly connected to the second connection 17 via a second control channel 48. The pressure in the second Pressure chamber 44 can be queried via an electro-hydraulic pressure sensor 49.
  • the moving parts such as the actuating piston 33, plunger 35 and closing body 19 are each mounted in separate, fixed components such as cover 14, cartridge guide 21 and cartridge sleeve 18 or housing 12, so that simple manufacture is possible.
  • the surface gradation in the built-in valve 10 is selected such that the sum of the annular surface 25 and the opening pressure surface 38 is greater than the closing pressure surface 45, the closing force of the closing spring 46 possibly also having to be taken into account.
  • the closing pressure surface 45 is larger than the sum of the annular surface 25 and the circular surface 24, wherein the closing pressure surface 45 can also be selected to be the same size in the limit case when the closing spring 46 is used.
  • the circular area 24 is chosen larger than the ring area 25.
  • the mode of operation of the built-in valve 10 is explained as follows, it being assumed that the built-in valve 10 is used in a safety circuit in which a flow through the valve cartridge 11 generally takes place in both directions.
  • the function of the built-in valve 10 is influenced by a switching valve 42, which is controlled as a function of the position of a safety device 51, which can be the protective door in an injection molding machine, for example. There are thus four switching states in which the built-in valve 10 has to meet predetermined safety requirements.
  • the built-in valve 10 works like a check valve in these states, the closing body 19 assuming the drawn blocking position and preventing flow from B to A .
  • This check valve function is also supported by the closing spring 46, so that this function is retained in the borderline case if the closing pressure area 45 is chosen to be the same size as the sum of the circular area 24 and the ring area 25. From the second pressure space 44 past the outer surface of the locking piston 34 leaking oil at most gets into the relieved space 36, so that no malfunction can occur due to a pressure build-up in the space 39 due to leakage oil.
  • FIG. 2 shows a longitudinal section through a second cartridge valve 60, which differs from the first cartridge valve 10 according to FIG. 1 as follows, the same reference numerals being used for the same components.
  • the built-in valve 60 has a closing body 61, at the upper end of which the actuating piston 62 is attached directly.
  • the closing body 61 with integrated actuating piston 62 is tightly and slidably guided in a cartridge case 63, so that the first pressure chamber 39 with the associated, now annular opening pressure surface 38 is arranged inside the cartridge case 63 and thus also within the housing 12.
  • the relieved space 36 now lies within the housing 12 and is delimited by the cover 14 in the separating surface 64.
  • the cover 14 instead of a stepped bore, the cover 14 now has a simple cylindrical bore 65, in which the locking piston 34 is guided in a tight and sliding manner.
  • the locking piston 34 itself is a simple cylindrical rotating part and rests with its lower end in the unloaded space 36 on the actuating piston 62.
  • the conditions for grading the area are met as with the first built-in valve 10.
  • the arrangement of the actuating piston 62 directly on the closing body 61 has the advantage that the number of pressure chambers is reduced from 6 to 5 now. Furthermore, there is a simpler design for the actuating device, which manages with a simple cylindrical bore 65 and a suitable cylindrical locking piston 34.
  • the frictional coupling between the locking piston 34 and the closing body 61 takes place advantageously in the relieved space 36, which also borders on the parting plane 64 between the housing 12 and the cover 14.
  • the arrangement of the actuating piston 62 on the closing body 61 has the advantage that when the opening pressure surface 38 is pressurized, the closing body 61 is carried along in the opening direction and thus when the valve cartridge flows through it no additional spring force has to be overcome.
  • the built-in valve 60 has the same principle of operation as the first built-in valve 10, in that it enables free flow from port A to port B in the cross position of the switching valve 42, while acting in the reverse direction of flow from B to A as a check valve and blocking the flow . By actuating the switching valve 42 in a parallel position with pressurization of the open pressure surface 38, this locking is released, so that a free flow in both directions is possible.
  • FIG. 3 shows the second built-in valve 60 in a simplified representation in connection with a safety circuit 70, such as is used for a locking cylinder 71 in a plastic machine.
  • the first port A of the built-in valve 60 is connected to a first port 72 on the closing side 73 on the locking cylinder.
  • the second port B of the built-in valve 60 is connected to a 4/3-way valve 75 via a working line 74.
  • a second working line 76 leads from the directional control valve 75 to a second connection 77 on the opening side 78 of the locking cylinder 71.
  • the directional control valve 75 is also connected to the pump 43 and the tank 28.
  • the pressure of the pump 43 is fed via a control line 79 to the 4/2 switching valve 42 which, via the first control channel 41, either applies pump pressure to the first pressure chamber 39 or unloads it to the tank.
  • the protective door 51 in the plastic machine is used here as a safety device for actuating the switching valve 42. It is also for pressure relief a line 81 is provided which leads from the closing side 73 to the switching valve 42 and in which a check valve and a throttle point are arranged.
  • the built-in valve 60 serves as a closing safety device in the safety circuit 70 and, in addition to the directional control valve 75, is the second element responsible for safety. It is therefore arranged between the closing side 73 of the cylinder 71 and the directional control valve 75.
  • the hydraulic actuation of the locking device 60 takes place via the switching valve 42 actuated by the movable protective door 51.
  • the built-in valve 60 serving as a locking device must be installed in such a way that the switching valve 42 assumes its spring-centered parallel position when the protective door 51 is closed and due to the pressurization of the open pressure surface 38 on the actuating piston 33 the lock in the installation valve 60 is released so that in the parallel position of the directional control valve 75 the pressure medium flows from the pump 43 via the working line 74 and the open installation valve 60 to the closing side 73 and the extending piston rod in the locking cylinder 71 can close a shape.
  • the switching valve 42 is forcibly brought into its cross position by this and the locking in the built-in valve 60 is effective, so that closing of the mold is prevented at all times by extending the locking cylinder 71.
  • the installation valve 60 works in the safety circuit 70 in the same manner as was explained in connection with the first installation valve 10 on the basis of the 4 switching states.
  • the first switching state results when the directional valve 75 is switched to its parallel position to close the mold while the protective door 51 is still open and the switching valve 42 thus relieves the first control channel 41 to the tank.
  • the safety function of the built-in valve 60 is effective and the closing body 61 remains in the blocking position by pressure via line 48 into the second pressure chamber 44.
  • the second switching state occurs when the directional valve 75 again assumes its parallel position, but the protective door 51 is closed. In this case, the built-in valve 60 is not locked, ie the valve cartridge is opened by pressure via line 41 into the first pressure chamber 39.
  • the third switching state results when the directional valve 75 assumes its cross position to open the mold while the protective door 51 is still open. Even then the valve cartridge is open.
  • the fourth switching state results in a corresponding manner when the protective door 51 is closed in the cross position of the directional control valve 75 and thus the closing body 61 assumes its open position when the lock in the built-in valve 60 is released.
  • the pressure build-up for the closing movement in the built-in valve 60 is brought about by control oil which reaches the closing pressure surface 45 from the second connection B via the short, second control channel 48. Since this short control channel 48 is formed directly in the block 12, 14, the reliable function of the closing movement when the control line 41 is relieved and the oil pressure in the second port B is simultaneously present and therefore does not require any additional control.
  • the displacement sensor 47 enables the control of the two switching states open and closed of the closing body 61.
  • the closing body 61 has an overlap stroke 52 in which the electrical signaling for the switching positions valve open or closed takes place.
  • the cartridge valve can also be used without position monitoring and can then be used as a hydraulically unlockable check valve.
  • the built-in valve can also be used in such a way that the second control channel 48 is connected to the free port B of a 4/2-way valve 42, so that the open pressure area and the close pressure area alternately via a 4/2 pilot valve with the Pressure applied or relieved to the tank. There is then a fixed association between the position of the protective door 51 and the position of the safety cartridge.
  • the built-in valve by connecting the pressure chambers appropriately, it can also be achieved that the valve can also function as a check valve in the other flow direction.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
EP90101628A 1989-02-18 1990-01-27 Soupape à deux voies à commande pilotée hydrauliquement en manière à siège Expired - Lifetime EP0384157B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3905015 1989-02-18
DE3905015A DE3905015A1 (de) 1989-02-18 1989-02-18 Hydraulisch vorsteuerbares 2-wege-einbauventil in sitzventilbauweise

Publications (3)

Publication Number Publication Date
EP0384157A2 true EP0384157A2 (fr) 1990-08-29
EP0384157A3 EP0384157A3 (fr) 1991-04-17
EP0384157B1 EP0384157B1 (fr) 1994-01-12

Family

ID=6374419

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90101628A Expired - Lifetime EP0384157B1 (fr) 1989-02-18 1990-01-27 Soupape à deux voies à commande pilotée hydrauliquement en manière à siège

Country Status (2)

Country Link
EP (1) EP0384157B1 (fr)
DE (2) DE3905015A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007128420A1 (fr) * 2006-05-05 2007-11-15 Robert Bosch Gmbh Vanne et arrangement de commande hydraulique
IT202200020595A1 (it) * 2022-10-06 2024-04-06 Pnr Italia S R L Gruppo valvolare per il controllo e/o la regolazione della portata di un fluido in pressione

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009025827A1 (de) * 2009-05-18 2010-11-25 Bucyrus Dbt Europe Gmbh Hydraulikschaltvorrichtung für die Mobilhydraulik, mobile Hydraulikmaschine und Ventileinheit

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2835771A1 (de) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics Anordnung zur aussteuerung eines cartridgeelementes
DE3135273A1 (de) * 1981-09-05 1983-03-24 Klöckner-Humboldt-Deutz AG, 5000 Köln Hydraulisches steuergeraet
DE3741521C1 (en) * 1987-12-08 1989-02-16 Hemscheidt Maschf Hermann 2/2-way seat valve

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007128420A1 (fr) * 2006-05-05 2007-11-15 Robert Bosch Gmbh Vanne et arrangement de commande hydraulique
EP2243991A1 (fr) * 2006-05-05 2010-10-27 Robert Bosch GmbH Soupape et dispositif de commande hydraulique
CN101438087B (zh) * 2006-05-05 2012-11-14 罗伯特.博世有限公司 阀和液压控制装置
IT202200020595A1 (it) * 2022-10-06 2024-04-06 Pnr Italia S R L Gruppo valvolare per il controllo e/o la regolazione della portata di un fluido in pressione

Also Published As

Publication number Publication date
DE3905015A1 (de) 1990-08-23
EP0384157B1 (fr) 1994-01-12
EP0384157A3 (fr) 1991-04-17
DE59004167D1 (de) 1994-02-24

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