EP2047108B1 - Ensemble de soupape à ouverture en fondu (soft start) - Google Patents

Ensemble de soupape à ouverture en fondu (soft start) Download PDF

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Publication number
EP2047108B1
EP2047108B1 EP06829284A EP06829284A EP2047108B1 EP 2047108 B1 EP2047108 B1 EP 2047108B1 EP 06829284 A EP06829284 A EP 06829284A EP 06829284 A EP06829284 A EP 06829284A EP 2047108 B1 EP2047108 B1 EP 2047108B1
Authority
EP
European Patent Office
Prior art keywords
valve
soft
switching
passage
main valve
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.)
Not-in-force
Application number
EP06829284A
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German (de)
English (en)
Other versions
EP2047108A1 (fr
Inventor
Grzegorz Bogdanowicz
Jakob Brenner
Andreas Decker
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Festo SE and Co KG
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Festo SE and Co KG
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Publication date
Application filed by Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP2047108A1 publication Critical patent/EP2047108A1/fr
Application granted granted Critical
Publication of EP2047108B1 publication Critical patent/EP2047108B1/fr
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/068—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with valves for gradually putting pneumatic systems under pressure
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/048—Arrangements for compressed air preparation, e.g. comprising air driers, air condensers, filters, lubricators or pressure regulators
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/355—Pilot pressure control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements

Definitions

  • the invention relates to a soft-start valve device, with a between a primary pressure under a primary pressure-carrying primary channel and a secondary channel switched main valve, which is switchable from a connection separating the primary channel and secondary channel closed position into a compound for maximum flow releasing open position, wherein the responsibility for this switching opening force in a secondary pressure controlled operating mode of the valve device is derived from the secondary channel gradually building secondary pressure of the pressure medium, which flows through a first throttle device away from the primary channel into the secondary channel.
  • a valve device is in US 5337788 disclosed.
  • Such, designed for secondary pressure controlled operation soft-start valve device is from the textbook “ Pneumatic Controls ", Werner Deppert, Kurt Stoll, Vogel Verlag, 10th Edition 1994, pages 160 and 161 , forth.
  • the main valve is turned on there in the connection between a connected to a pressure source primary channel and connected to the consumers to be supplied secondary channel and can optionally shut off the connection (closed position) or release (open position).
  • the main valve is biased by a closing pressure based on the primary pressure in the closed position.
  • the pressure medium can flow past the closed main valve past a first throttle device into the secondary channel.
  • the prevailing in the secondary channel secondary pressure is returned to generate a force on the main valve and switches it to the open position when the secondary pressure has reached a predetermined opening force.
  • the present invention has for its object to propose measures that allow in a simple and cost-effective manner in the most cases a specific graded to the requirements gradual pressure build-up.
  • the soft-start valve device is constructed so that they simultaneously superimposed on the secondary pressure-controlled operating mode in a mode of operation, the main valve independent of the secondary pressure purely time-dependent in the open position switching time-controlled operating mode is operable, the responsible for this time-dependent switching opening force of a discharged through a second throttle device pressure medium is derived.
  • the soft-start valve device can thus be operated at the same time in two operating modes which functionally overlap one another are. Thereby, the main valve is switched in response to the conditions present on the secondary side individually either on the basis of reaching a predetermined secondary pressure or on the basis of an elapsed since the switch-on time in the maximum flow releasing open position.
  • the soft-start valve device can thus be designed, for example, such that the secondary pressure-controlled switching represents the normal case, but at the latest at a predetermined time switching takes place by the superimposed timing, even if the secondary pressure has not reached the pressure threshold at which he Able to switch the main valve.
  • the soft-start valve device can be used wherever a slow pressure build-up is desired during the start-up of one or more consumers, for example a pneumatically controlled system or machine.
  • the soft-start valve device may be part of a valve battery combined with a plurality of multi-way valves to form an assembly.
  • An insert is considered to be particularly advantageous as a component of a preferably modular compressed-air maintenance device. which is used for the treatment of compressed air in compressed air networks.
  • the soft-start valve device in particular if it is designed as a compact valve unit, take over the function of a so-called on-off valve.
  • the first throttle device is designed to be adjustable, it is easy to vary the time duration that is normally required until the secondary pressure causing the changeover to the open position has built up.
  • the absolute time duration can be set variably, after which the switchover to the open position takes place, if not previously a switchover was initiated by the secondary pressure.
  • the vast majority of applications of soft-start valve devices usually requires only a secondary pressure-controlled operation. If the channel containing the second throttle device and designated as the timing channel is equipped with shut-off means which, if required, permit shut-off of the fluid passage, then the soft-start valve device according to the invention can be switched to an exclusively secondary-pressure-controlled operating mode as required. The time-controlled operating mode is then shut down.
  • the blocking means can be designed, for example, in the form of a separate shut-off valve.
  • a design in which the adjustable second throttle device directly itself defines the shut-off means is simpler and less expensive. Disabling the timed Operation mode can be effected in this case, that the second throttle device is adjusted so far that it no longer lets fluid through.
  • the main valve of the soft-start valve device is thus formed at least as a three-position valve, in addition to the functioning as a basic position closed position and the maximum open position can also assume a responsible for the soft start soft start position.
  • the soft start fluid flow through the pilot valve and around the main valve around. Now it can pass through the main valve and does not require immediate control by the pilot valve.
  • the preferably electrically actuated pilot valve in cooperation with the additional changeover valve.
  • the fluidic pilot signal generated by the pilot valve first switches the main valve from the closed position to the soft start position.
  • the secondary pressure If the secondary pressure has reached the desired switching threshold after a certain period of time, it causes the switching valve to actuate the fluidic pilot signal of another actuating surface, so that the main valve is then switched from the soft start position into the open position ensuring the maximum flow.
  • the second actuating surface of the main valve is constantly acted upon by the flow restricting second throttle device of the fluidic pilot signal and can thereby cause a usually gradual switching to the maximum open position even if the secondary pressure is not the required switching threshold within reached a desired time frame.
  • the switching valve is expediently fluidly actuated, it being the secondary pressure directly aufschaltbar as a control pressure.
  • the switching valve for example, work in the manner of a pressure compensator.
  • Alternative would be but also an only indirect activation of the switching valve by the secondary pressure possible by, for example, an electrically activated switching valve is used, the switching signal is generated with the cooperation of a pressure sensor or pressure switch, which detects the secondary pressure. The latter allows a particularly simple variation of the switching threshold.
  • main valve so that it causes a pressure relief of the secondary channel in its closed position, thus causing a venting of the secondary channel in pneumatic application.
  • Relief through the main valve eliminates the use of a separate relief valve or relief through the pilot valve.
  • One or both throttles expediently include an adjustable throttle screw for specifying the respective desired throttling intensity.
  • the various components of the soft-start valve device are expediently combined to form an assembly. This simplifies handling during installation and removal.
  • the pilot valve is in particular a solenoid valve.
  • other electrically activatable valve types can also be used, for example piezo valves or electrostatic valves.
  • the main valve expediently contains a main valve element that can be positioned to predefine its switching positions in a corresponding number of switching positions, in particular in the form of a valve slide.
  • the first and then the second actuating surface act in each case drivingly together with the main valve member.
  • first actuating surface is conveniently located on a respect to the main valve member separate actuator.
  • This actuator is decoupled from the main valve member such that the latter can be switched without entrainment of the actuating element from the soft start position into the open position.
  • Reason for the aforementioned movement is expediently the presence of a arranged in the adjustment of the actuating element stop surface, which defines the soft start position.
  • the actuating element is preferably designed as an actuating piston.
  • actuating piston Alternatively, however, would be conceivable, for example, a realization as an actuating diaphragm.
  • the main valve member is subject to a spring force caused by permanent closing force in the direction of its closed position.
  • the spring means are compressed by a certain amount, whereby the degree of compression increases even further until the open position is maintained.
  • the spring means provide for a provision of the main valve member in the closed position.
  • the loading of the first actuating surface with the pilot pressure is expediently carried out directly via a control channel controlled by the pilot valve.
  • the application of the second actuating surface is expediently carried out via a switching channel diverted from the pilot control channel, in the course of which, in the manner of a parallel connection, the switching valve and the second throttle device are switched on.
  • the changeover valve expediently contains a movable changeover valve member. This is controlled and actuated on the basis of the secondary pressure.
  • a direct application by the secondary pressure can be done, for example, by means of a tapping channel which leads to the secondary channel or to the one between the secondary channel and the first throttle device extending channel branch of the pressure control channel is connected.
  • the channels running within the soft-start valve device are in some cases shown only as dotted, dashed and solid lines.
  • the dotted lines represent unpressurized channels, while the solid lines represent channels that are currently under pressure. Dotted lines indicate channels are under pressure build-up.
  • the designated in its entirety by reference numeral 21 soft start valve device is suitably designed as a valve unit in which all components are summarized in the manner of a module. This favors the installation on site and in particular the integration into a modular built, usable for the treatment of compressed air compressed air maintenance device.
  • the soft start valve device is designed as a module (maintenance module) of such a compressed air maintenance device and can be combined with other maintenance modules, for example with a pressure regulator module and / or a filter module.
  • the soft start valve device is used in particular as a so-called switch-on valve, which optionally allows a complete shut-off or a complete release of a fluid passage, wherein the release of the fluid passage gradually takes place, so that on the output side, ie on the secondary side, no sudden, but a gradual increase in pressure occurs, which allows easy commissioning of secondary consumers connected.
  • the soft-start valve device 21 which for the sake of simplicity is also referred to as "soft-start valve” below, contains a housing 28, on which a fluidic inlet connection 22 and a fluidic outlet connection 12 are formed.
  • the inlet port belongs to a primary channel 1 running in the housing 28 and allows the connection of a pressure source P which supplies a fluidic pressure medium under a primary pressure, which in particular is compressed air.
  • the soft start valve 21 may also be operated with another gas or with a liquid pressure medium.
  • the outlet connection 12 belongs to a secondary channel 2 running in the housing 28, via which the pressure medium fed in via the primary channel 1 leaves the soft-start valve 21, standing at a secondary pressure, in order to be supplied to one or more consumers (not shown).
  • the at least one consumer is, for example, a drive operated by fluid power, a valve device or other components operated with a fluid.
  • the soft start valve 21 is designed as a component of a valve battery.
  • the valve battery includes a one-piece or multi-part fluid distributor, which is equipped with a plurality of electrically actuated control valves and which is additionally equipped with the soft start valve 21.
  • About the fluid distributor is to be controlled by the control valves Supplied pressure medium.
  • the soft-start valve 21 is functionally connected upstream of the control valves in such a way that, when the valve battery is put into operation, a gentle fluid admission of the control valves takes place, so that damage or malfunctions are avoided.
  • the soft-start valve can be mounted on the outside of the fluid distributor, but integration is also possible.
  • the exemplary soft start valve 21 is functionally divided into a plurality of individual valves, which, however, are expediently combined to form a uniformly manageable assembly.
  • the soft start valve 21 includes a main valve 24, a pilot valve 25 and a switching valve 26th
  • the soft-start valve 21 includes a first throttle device 38, which is responsible for a secondary-pressure-controlled operating mode, and a second throttle device 39, which is primarily responsible for a purely timed operating mode.
  • These throttle devices 38, 39 are also conveniently housed in the housing 28.
  • the soft-start valve 21 is activated by the pilot control valve 25, which can act directly on the one hand and on the other, with the interposition of the switching valve 26 and the second throttle device connected in parallel, indirectly to the main valve 24 to one of a total of three possible switching positions of the main valve 24th pretend.
  • the pilot valve 25 is in particular of the electrically actuated type and has an electrical interface 27, via which it can be supplied with the required electrical actuation signals.
  • valve member receptacle 32 In the housing 28 of the soft start valve 21 is an elongated, exemplary vertically aligned cavity defining a valve member receptacle 32.
  • the valve member receptacle 32 includes an elongated, in the direction of its longitudinal axis 31 linearly displaceable main valve member 33.
  • main valve member 33 In the context of one of the longitudinal axis 31 following, indicated by a double arrow switching movement 34, the main valve member 33 and thus the main valve 24 can be switched between a total of three switching positions to be explained in more detail ,
  • the main valve member 33 is designed in particular in the manner of a valve spool.
  • valve member receptacle 32 By means arranged in the valve member receptacle 32 fixed to the housing sealing means 35, which consist for example of a plurality of axially spaced apart annular sealing elements which coaxially surround the main valve member 33, the valve member receptacle 32 is divided into a plurality of axially successive sections 36a, 36b, 36c, of which each one the valve housing 28 passing through the valve channel.
  • These valve channels are the primary channel 1, the secondary channel 2 and a further channel, which is connected within the housing 28 with the secondary channel 2 and which is designated as a pressure control channel 3.
  • the communicating with the primary channel 1 first portion 36a of the valve member receptacle 32 is located axially between the communicating with the secondary channel 2 second portion 36b and communicating with the pressure control channel 3 third portion 36c.
  • the first throttle means 38 are turned on. They limit the fluid flow through the pressure control channel 3 according to the predetermined throttling intensity.
  • the first throttle device 38 With regard to the throttling intensity which can be predetermined by it, the flow rate for the pressure control channel 3 can be set variably as required.
  • the first throttle device 38 includes a throttle screw 38a accessible from an outer surface of the housing 28.
  • the longitudinal portion of the main valve member 33 located within the portions 36a, 36b, 36c forms a control portion 42 cooperating with the sealing means 35. It is stepped in its longitudinal direction and contains alternately arranged regions of larger and smaller diameter. Depending on whether a region of larger diameter or a region of smaller diameter is arranged at the same axial height with one of the sealing elements of the sealing means 35, each axially on both sides of the corresponding sealing element arranged portions of the valve member receptacle 32 are separated or fluidly interconnected.
  • a drive section 43 of the main valve element 33 connects to the side of the third section 36c of the valve member receptacle 32.
  • the main valve member 33 in the direction of a FIGS. 1 and 4 anticipate closed position. This closed position is the basic position of the soft-start valve 21.
  • the spring means 44 are preferably designed as a compression spring device, which expediently surrounds the drive section 43 coaxially. It is supported at one end - in the drawing with its lower end - from the housing 28 and at the other end - with its top in the drawing - the main valve member 33. Thus, the main valve member 33 by the spring force of the spring means 44 constantly - in the drawing directed above - acted upon in the direction of its closed position.
  • the main valve member 33 optionally in the off FIGS. 1 and 4 apparent closing position, in the off Figures 2 and 5 apparent soft start position or in the off Figures 3 and 6 apparent maximum open position be positioned. These positions differ in a different interconnection of the valve channels 1, 2, 3 by the control section 42. If the timed operating mode is effective, intermediate positions of the main valve member 33 between the soft start position and the maximum open position are possible (in FIG. 2 dash-dotted lines indicated).
  • the secondary channel 2 is completely separated from the primary channel 1. Also, the fluid passage through the pressure control channel 3 is shut off here. Conveniently, the secondary channel 2 is connected in the closed position, however, with a discharge channel 4 of the main valve 24, so that a pressure relief of the secondary channel 2 takes place. If compressed air is used as the pressure medium, the relief channel 4 forms a venting channel, to which a silencer not shown in the drawing can be connected if required.
  • discharge channel 4 in coaxial extension of the valve member receptacle 32 opens at an end face of the housing 28.
  • the secondary channel 2 is in the off FIG. 5 apparent soft start position exclusively via the pressure control channel 3, and thus across the first throttle device 38, with the primary channel 1 in conjunction.
  • the connection is here released between the first and third sections 36a, 36c of the valve member receptacle 32.
  • a direct connection between primary channel 1 and secondary channel 2, bypassing the pressure control channel 3, is not available.
  • both operating modes can in the off FIG. 2 apparent soft start position in addition to the connection via the pressure control channel 3 also a direct connection between the secondary channel 2 and the primary channel 1 via the first and second portions 36a, 36b of the valve member receptacle 32 are present.
  • this last-mentioned direct connection however, the maximum flow cross-section is not yet released, so that only throttled overflow of the pressure medium takes place, which is illustrated by the dashed arrow flow arrow 30.
  • the secondary channel 2 is separated from the discharge channel 4.
  • connection between primary channel 1 and secondary channel 2 via the pressure control channel 3 is expediently additionally maintained as a parallel connection. Due to the throttling taking place, however, the associated flow rate is considerably lower than that of the direct main flow bypassing the pressure control channel 3.
  • the main valve 24 includes a first (46) and a second (47) actuating surface, each drivingly cooperating with the main valve member 33.
  • the first actuating surface 46 is located on a relative to the main valve member 33 independent actuator 48, which is exemplified in the manner of an actuating piston and which is received axially in the valve member receptacle 32 following the drive portion 43 of the main valve member 33.
  • the first actuating surface 46 has axially away from the main valve member 33, in the drawing upwards.
  • the actuating element 48 is slidably mounted in the direction of the longitudinal axis 31 of the main valve member 33 in a receiving chamber 52 formed by the end portion of the valve member receptacle 32. With its peripheral wall, it is in sealing contact.
  • the end faces of the receiving chamber 52 form a main stopper 33 facing the first stop surface 53 and an oppositely oriented second stop surface 54 for the actuator 48, which limit the adjustment.
  • actuating element 48 could for example be designed as an actuating diaphragm.
  • the second actuating surface 47 is axially fixed to the main valve member 33. It therefore makes every linear movement of the main valve member 33 with. It points in the same direction as the first actuating surface 46, in the present case away from the control section 42.
  • the second actuating surface 47 is located on the end face of the main valve member 33 facing the actuating element 48.
  • the main valve member 33 moves in the direction of the closed position, it dips into the receiving chamber 52 with its end section having the second actuating surface 47 ( FIGS. 1 and 4 ).
  • the main valve member can take the other apparent from the drawing positions in which it is completely moved out of the receiving chamber 52 and the second actuating surface 47 having end portion in a subsequent to the receiving chamber 52 longitudinal portion 55 of the valve member receptacle 32 is whose cross section is smaller than that of the receiving chamber 52. Accordingly, the second actuating surface 47 is advantageously smaller than the first actuating surface 46th
  • the above-mentioned spring means 44 are arranged locally between on the one hand the two actuating surfaces and on the other hand the control section 42 on the drive section 43 of the main valve member 33.
  • the spring means 44 are based on the main valve member 33 on a preferably sleeve-shaped head piece 57, on which the second actuating surface 47 is expediently formed.
  • the actuator 48 divides the receiving chamber 52 into a first actuating chamber 62 located on the side opposite the main valve member 33 and a second actuating chamber 63 located on the side facing the main valve member 33.
  • the first actuating chamber 62 is delimited by the first stop surface 53 opposite the actuating element 48.
  • the second actuating chamber 63 has, axially opposite the actuating element 48, via a rigid boundary wall formed by the second stop surface 54 and also via an axially movable boundary wall, which is formed by the main valve member 33 and the second actuating surface 47.
  • the second actuating chamber 63 may extend a little way into the adjoining the receiving chamber 52 longitudinal portion 55 of the valve member receptacle 32 in, as is apparent from Figures 3 and 6 is apparent.
  • a fluidic pilot channel 64 branches off from the primary channel 1 and ends in the first actuating chamber 62.
  • the pilot valve 25 is turned on, so that the pilot channel 64 in a communicating with the primary channel 1 pilot-feed channel 64a and communicating with the first actuating chamber 62 pilot control working channel 64b is divided.
  • pilot control working channel 64b can be turned on, if necessary, a manual activation of the soft start valve enabling auxiliary valve 69, the fluid passage through the pilot control working channel 64b permits unrestricted in the basic position shown in the drawing.
  • the pilot valve 25 is a 3/2-way valve capable of connecting the pilot working passage 64b to either the pilot feed passage 64a or to a pilot relief vent passage serving for relieving the pressure internally the pilot valve 25 extends and is not shown in the drawing.
  • the pilot exhaust passage opens expediently directly to the atmosphere.
  • the switching valve 26 includes a preferably linear, according to double arrow 66 movable switching valve member 67.
  • a preferred mechanical spring device 68 generates a spring force, by which the switching valve member 67 in the direction of a FIGS. 1 to 5 is biased apparent starting position. The initial position is predetermined by the system of the Umschaltventilgliedes 67 on a fixed housing stop portion 72.
  • a gas spring device in particular an air spring device, could also be used.
  • the switching valve member 67 axially delimits a control chamber 73 which is constantly connected to the secondary channel 2 via a tap channel 74. This connection can take place directly as shown, but also by connecting the tap channel 74 to the channel branch of the pressure control channel 3 extending between the first throttle device 38 and the secondary channel 2.
  • a switching channel 75 is connected at one end to the pilot control working channel 64 and at the other end to the second actuating chamber 63.
  • the switching valve 26 and the second throttle device 39 are integrated in parallel in the course of the switching channel 75. More specifically, the switching passage 75 branches between its input portion 75a connected to the pilot working passage 64b and its output portion 75b connected to the second actuating chamber 63 into two first and second branch portions 75c, 75d connected in parallel with each other, into the first branch portion 75c, the switching valve 26 and in the second branch portion 75d, the second throttle device 39 is turned on.
  • the second branch section 75d includes the second throttling device 39 responsible for the timed operating mode, it is also referred to below as the "timing channel”.
  • the switching valve 26 is capable of controlling the fluid passage through the first branch portion 75c.
  • the Umschaltventilgliedes 67 In the initial position of the Umschaltventilgliedes 67 is the connection interrupted. Is the change-over valve member 67 by a sufficiently high switching force in the off FIG. 6 displaced apparent switching position, the fluid passage through the switching channel 75 is released.
  • the switching force also has to overcome the pressure force resulting from the fluidic precontrol signal, which acts on the changeover valve member 67 in the same direction as the spring device 68.
  • the second throttle device 39 is expediently designed to be adjustable with regard to the throttling intensity which can be predetermined by it.
  • it contains as an adjustable throttle element an externally accessible throttle screw 39a.
  • the pressure medium diverted from the pilot-control working channel 64b into the switching channel 75 can flow over into the second actuating chamber 63, irrespective of the switching position of the switching valve 26, via the second throttle device 39.
  • the flow rate depends on the set throttling intensity. Accordingly, the set duration of the pressure build-up in the second actuation chamber 63 is predetermined by the set throttling intensity.
  • the second throttle device 39 also takes over the additional function of shut-off means 70, through which the fluid passage through the timing channel 75d can be completely shut off.
  • shut-off means 70 By way of example, this happens simply in that the throttle screw 39a is screwed into a closed position.
  • the shut-off means are formed by an existing in addition to the second throttle device 39 shut-off valve, which in a Series connection with the second throttle device 39 is incorporated into the timing channel 75d.
  • the soft start valve device 21 is in this way exclusively in a secondary pressure controlled operating mode.
  • the time-controlled operating mode is shut down.
  • pilot valve 25 is deactivated and the main valve member 33 in the off FIG. 4 apparent closed position is located.
  • the secondary channel 2 is depressurized, as well as the consumers possibly connected thereto.
  • a pressure medium which is under a primary pressure is fed in, which thus also rests in the pilot-control feed channel 64a.
  • the two actuating chambers 62, 63 are vented via the pilot valve 25.
  • the pilot valve 25 is actuated via a supplied electrical control signal.
  • the pilot valve 25 opens the passage through the pilot channel 64, so that a primary pressure corresponding fluid pilot signal is fed via the pilot working channel 64b away in the first actuating chamber 62 and there applied to the first actuating surface 46.
  • the actuating force resulting therefrom displaces the actuating element 48 until it abuts against the second stop surface 54, whereby it acts on the main valve element 33 on its second actuating surface 47 and carries the spring means 44 while overcoming the spring force.
  • Has the actuator 48 reaches the second stop surface 54 the main valve member 33 is in the off FIG. 5 apparent soft start position.
  • the changeover valve member 67 which still occupies the initial position, in this case holds the second actuation chamber 63 separated from the pilot control conduit 64.
  • a soft start phase lasting a certain time begins. This is characterized in that flows over the enabled pressure control channel 3 away with throttled flow pressure medium in the secondary channel 2, so that the prevailing secondary pressure gradually increases.
  • the gradient of the pressure increase can be varied via the setting of the first throttle device 38.
  • the secondary channel 2 is supplied with pressure medium from the primary channel 1 via the large flow cross-section, which is now maximally unlocked by the main valve member 33, thus bypassing the first throttle device 38.
  • the secondary pressure increases in the shortest possible time up to the level of the primary pressure.
  • the spring means 68 of the switching valve 26 may be formed adjustable in terms of their spring force. This allows a variation of the switching threshold.
  • the switching valve 26 will be designed so that the switching threshold is at a secondary pressure which corresponds to half of the primary pressure.
  • the particular advantage of the soft start valve 21 is that it according to FIGS. 1 to 3 is operable in a way in which just that FIGS. 4 to 6 described secondary pressure-controlled operating mode is superimposed on a time-controlled operating mode.
  • the timed mode of operation is active in addition to the secondary pressure controlled mode of operation when fluid flow through the timing channel 75d through is possible.
  • only the second throttle device 39 is to be adjusted in the embodiment so that it no longer completely shuts off the timing channel 75d, but allows a flow rate with a flow rate corresponding to the selected setting.
  • the main valve member 33 If the secondary pressure does not reach the switching threshold required for actuating the switching valve 26 even after a relatively long time, the main valve member 33, after a certain time, arrives at the maximum flow between the two sections solely because of the pressure medium flowing in via the second throttle device 39 36a, 36b releasing open position.
  • the actual switching time depends on the throttling intensity of the second throttle device 39.
  • the switching of the main valve 24 into the maximum flow-releasing open position is ultimately determined by which pressure first causes the switchover Threshold has reached, so either the tapped via the tap channel 74 secondary pressure or in the second actuating chamber 63 building actuating pressure.
  • the switching valve 26 is switched directly as the switching force supplying control pressure.
  • the changeover valve 26 it would also be possible to form the changeover valve 26 in an electrically actuable manner, the electrical changeover signal being generated with the assistance of a pressure sensor or pressure switch which detects the secondary pressure.
  • auxiliary valve 69 This has an auxiliary valve member 77 which is turned on in the course of the pilot control working channel 64b and in the normally occupied, shown in the drawing unconfirmed basic position allows a free passage through the pilot working channel 64b and at the same time also a continuous connection between this pilot control Working channel 64b and the input portion 75a of the switching channel 75th
  • auxiliary valve 69 is connected via one of the better distinguishability because only dash-dotted lines indicated auxiliary control channel 78 to the primary channel 1 or the portion 36a of the valve member receptacle 32, said auxiliary control channel 78 is shut off in the normal position by the auxiliary valve 69.
  • the auxiliary valve 69 allows activation of the soft-start valve 21 when the pilot valve 25 is not actuated, that is to say when the pilot-control working channel 64b is depressurized.
  • manual switching of the auxiliary valve 69 in an actuated working position is a fluid connection between the auxiliary control channel 78 and the input portion 75a of the switching channel 75, which allows operation as well as if the fluidic pilot signal would be present.
  • the auxiliary valve 69 is expediently formed self-resetting. It returns automatically to the normal position when the fluidic pilot control signal is present by actuation of the pilot control valve 25 in the channel branch of the pilot control working duct 64b extending between the auxiliary valve 69 and the pilot control valve 25. This acts on the auxiliary valve member 77 against the arrow 79 and moves it back to the normal position. Thus, a manual reset of the auxiliary valve 69 in the unactuated basic position is unnecessary.
  • An advantage of the described valve assembly is also in the insensitivity of the soft-start valve 21 to pressure fluctuations in the primary channel 1 or secondary channel 2. Should due to a pressure drop acting on the switching valve 26 switching force so far drop that the switching valve 26 switches back to the starting position, this affects the Open position of the main valve member 33 is not because the pilot located in the second actuating chamber 63 control fluid remains trapped and can not escape. If at the same time the time-controlled operating mode is active, is also constantly on the second throttle device 39 pressure medium in the second actuating chamber 63, which maintains the open position of the main valve member 33.
  • This variant provides a Fluidabgriffskanal 80, the one end in an upstream the first throttle device 38 opens existing fluid space, which is exemplified by the upstream of the first throttle device 38 lying input side channel portion 3a of the pressure control channel 3.
  • this fluid space could also be the section 36c of the valve member receptacle 32. In any case, it is a fluid space which is separated in the closed position of the main valve from the primary channel 1, but immediately with the beginning of the soft start phase directly, via the portion 36 a, is connected to the primary channel 1.
  • Fluidabgriffskanal 80 With its opposite end of the Fluidabgriffskanal 80 opens to the outer surface of the housing 28, where it is associated with connection means not shown in detail, which allow the connection of a leading to a consumer fluid line.
  • the consumer is, for example, the pilot valve of a pilot operated multiway valve.
  • the soft-start valve device 21 then outputs a throttled and an unthrottled pressure medium simultaneously and independently of one another.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Driven Valves (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne un ensemble soupape (21) pour démarrage progressif, qui présente une soupape principale (24) commandant la liaison fluidique entre un canal primaire (1) et un canal secondaire (2). Pour être commutée en position ouverte, la soupape principale (24) est sollicitée par une force d'ouverture qui, dans un mode de fonctionnement régulé par la pression secondaire, est dérivée de la pression secondaire régnant dans le canal secondaire (2) et qui, dans un mode de fonctionnement temporisé, est dérivée d'un fluide sous pression s'écoulant à travers un dispositif d'étranglement (39). Un avantage particulier résulte du fait que les deux modes de fonctionnement sont exécutés en superposition simultanée.

Claims (15)

  1. Ensemble de soupape à démarrage progressif, avec une soupape principale (24) insérée entre un canal primaire (1) conduisant un agent de pression mis sous une pression primaire et un canal secondaire (2), laquelle soupape est commutable d'une position fermée coupant la liaison entre le canal primaire (1) et le canal secondaire (2) à une position ouverte libérant cette liaison pour un débit maximal, la force d'ouverture responsable de cette commutation étant issue, lorsque l'ensemble de soupape est dans un mode de fonctionnement commandé par la pression secondaire, de la pression secondaire de l'agent de pression s'établissant progressivement dans le canal secondaire (2), qui s'écoule du canal primaire (1) au canal secondaire (2) en passant par un premier dispositif d'étranglement (38), caractérisé en ce que l'ensemble soupape peut être exploité en même temps dans le mode de fonctionnement commandé par la pression secondaire et dans un mode de fonctionnement commandé par le temps superposé à ce mode de fonctionnement et commutant la soupape principale (24) dans la position ouverte indépendamment de la pression secondaire, uniquement en fonction du temps, la force d'ouverture responsable de cette commutation fonction du temps étant issue d'un agent de pression traversant le deuxième dispositif d'étranglement (39).
  2. Ensemble de soupape à démarrage progressif selon la revendication 1, caractérisé en ce que le deuxième dispositif d'étranglement (39) est placé dans un canal de commande de temps (75d), des moyens de fermeture (70) étant prévu qui permettent de bloquer le passage de fluide par ce canal de commande de temps (75d) pour désactiver le mode de fonctionnement commandé par le temps, les moyens de fermeture (70) étant formés de manière avantageuse par le deuxième dispositif d'étranglement (39) réglable dans une position de fermeture.
  3. Ensemble de soupape à démarrage progressif selon la revendication 1 ou 2, caractérisé en ce que le premier dispositif d'étranglement (38) est réalisé de manière réglable en ce qui concerne l'intensité d'étranglement qu'il peut prédéfinir et/ou en ce que le deuxième dispositif d'étranglement (39) est réalisé de manière réglable en ce qui concerne l'intensité d'étranglement qu'il peut prédéfinir.
  4. Ensemble de soupape à démarrage progressif selon l'une des revendications 1 à 3, caractérisé en ce que le canal secondaire (2) est relié à un canal de décharge (4) lorsque la soupape principale (24) est en position fermée.
  5. Ensemble de soupape à démarrage progressif selon l'une des revendications 1 à 4, caractérisé par les caractéristiques suivantes :
    - la soupape principale (24) est commutable entre la position fermée, la position ouverte et une position de démarrage progressif, cette soupape reliant dans la position de démarrage progressif le canal secondaire (2) au canal primaire (1) par le biais d'un canal de commande de pression (3) contenant le premier dispositif d'étranglement (38) et libérant dans la position ouverte une liaison directe, contournant le premier dispositif d'étranglement (38), entre le canal primaire (1) et le canal secondaire (2),
    - il est prévu une soupape pilote (25) servant à influencer la position de commutation de la soupape principale (24), lors de l'actionnement de laquelle un signal pilote fluidique est généré, qui sollicite une première surface d'actionnement (46) de la soupape principale (24) pour commuter la soupape principale (24) de la position fermée à la position de démarrage progressif,
    - il est prévu en plus une soupape de commutation (26) actionnable par la pression secondaire régnant dans le canal secondaire (2), qui, lorsque la pression secondaire est à une valeur prédéfinie, relie le signal pilote fluidique généré par la soupape pilote (25) à une deuxième surface d'actionnement (47) de la soupape principale (24) pour commuter la soupape principale (24) de la position de démarrage progressif à la position de travail,
    - le deuxième dispositif d'étranglement (39) est raccordé de telle sorte que le signal pilote fluidique s'applique à son entrée et que sa sortie est reliée à la deuxième surface d'actionnement (47).
  6. Ensemble de soupape à démarrage progressif selon la revendication 5, caractérisé en ce que les deux surfaces d'actionnement (46, 47) sont dirigées dans le même sens.
  7. Ensemble de soupape à démarrage progressif selon la revendication 5 ou 6, caractérisé en ce que les trois positions de commutation de la soupape principale (24) sont prédéterminées par des positions de commutation correspondantes d'un organe de soupape principale mobile (33), la première et la deuxième surfaces d'actionnement (46, 47) étant réalisées respectivement pour coopérer par entraînement avec l'organe de soupape principale (33).
  8. Ensemble de soupape à démarrage progressif selon la revendication 7, caractérisé en ce que la première surface d'actionnement (46) est réalisée au niveau d'un élément d'actionnement (48) séparé par rapport à l'organe de soupape principale (33), qui peut être déplacé en cas de sollicitation par le signal pilote fluidique en entraînant l'organe de soupape principale (33) jusqu'à ce qu'il s'applique contre une surface de butée (54) prédéfinissant la position de démarrage progressif, l'organe de soupape principale (33) s'éloignant de l'élément d'actionnement (48), lorsqu'il continue ensuite à être déplacé par la sollicitation fluidique de la deuxième surface d'actionnement (47) en direction de la position ouverte.
  9. Ensemble de soupape à démarrage progressif selon la revendication 8, caractérisé en ce que l'élément d'actionnement (48) est disposé axialement à la suite de l'organe de soupape principale (33) déplaçable de manière linéaire et s'appuie de manière lâche contre l'organe de soupape principale (33) d'une manière permettant simplement la transmission d'efforts de commande de poussée.
  10. Ensemble de soupape à démarrage progressif selon l'une des revendications 7 à 9, caractérisé en ce que la deuxième surface d'actionnement (47) est disposée rigidement au niveau de l'organe de soupape principale (33), en particulier de telle manière que la deuxième surface d'actionnement (47) s'éloigne de la première surface d'actionnement (46) lorsque la soupape principale (24) est commutée de la position de démarrage progressif à la position ouverte.
  11. Ensemble de soupape à démarrage progressif selon l'une des revendications 5 à 10, caractérisé en ce qu'il est prévu un canal de commutation (75) conduisant à la deuxième surface d'actionnement (47), qui communique avec un canal pilote (64) fournissant le signal pilote fluidique et dans le cheminement duquel, dans un montage en parallèle, sont insérés la soupape de commutation (26) et le deuxième dispositif d'étranglement (39), la deuxième surface d'actionnement (47) délimitant de manière avantageuse une deuxième chambre d'actionnement (63), qui communique avec le canal de commutation (75).
  12. Ensemble de soupape à démarrage progressif selon l'une des revendications 5 à 11, caractérisé en ce que la soupape de commutation (26) présente un organe de soupape de commutation (67) précontraint dans une position de départ par un effort de retenue, fourni en particulier par un dispositif à ressort (68), qui est sollicité de manière opposée à l'effort de retenue par une force de commutation dépendant de la pression secondaire régnant dans le canal secondaire (2).
  13. Ensemble de soupape à démarrage progressif selon la revendication 12, caractérisé en ce que l'organe de soupape de commutation (67) commande le passage de fluide par un canal de commutation (75), qui est sollicité d'un côté avec le signal pilote fluidique de la soupape pilote (25) et conduit de l'autre côté à la deuxième surface d'actionnement (47) de telle sorte que le passage de fluide est bloqué dans la position de départ de l'organe de soupape de commutation (67) et est libéré lorsque l'organe de soupape de commutation (67) est déplacé dans une position de commutation du fait qu'une pression secondaire de valeur prédéterminée est atteinte.
  14. Ensemble de soupape à démarrage progressif selon l'une des revendications 5 à 13, caractérisé en ce que la pression secondaire régnant dans le canal secondaire (2) est reliée directement à la soupape de commutation (26) sous forme de pression de commande servant à générer la force de commutation.
  15. Ensemble de soupape à démarrage progressif selon l'une quelconque des revendications 5 à 14, caractérisé en ce qui est prévue une chambre de fluide (3a) située en amont du premier dispositif d'étranglement (38), qui est séparée du canal primaire (1) dans la position fermée et est reliée au canal primaire (1) au moins dans la position de démarrage progressif et qui est en relation avec un canal de prélèvement de fluide (80), qui permet un prélèvement de fluide non étranglé pendant la phase de démarrage progressif.
EP06829284A 2006-12-05 2006-12-05 Ensemble de soupape à ouverture en fondu (soft start) Not-in-force EP2047108B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2006/011637 WO2008067828A1 (fr) 2006-12-05 2006-12-05 Ensemble soupape pour démarrage progressif

Publications (2)

Publication Number Publication Date
EP2047108A1 EP2047108A1 (fr) 2009-04-15
EP2047108B1 true EP2047108B1 (fr) 2010-01-06

Family

ID=38269055

Family Applications (1)

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EP06829284A Not-in-force EP2047108B1 (fr) 2006-12-05 2006-12-05 Ensemble de soupape à ouverture en fondu (soft start)

Country Status (4)

Country Link
EP (1) EP2047108B1 (fr)
DE (1) DE502006005894D1 (fr)
TW (1) TWI403656B (fr)
WO (1) WO2008067828A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112012004574B4 (de) 2011-11-02 2018-03-08 Smc Kabushiki Kaisha Strömungsratensteuervorrichtung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014151241A1 (fr) * 2013-03-15 2014-09-25 Ross Operating Valve Company Vanne de commande fiable d'isolation d'énergie pneumatique comportant une fonction de démarrage progressif
CN106761660B (zh) * 2016-12-27 2023-02-03 中铁工程装备集团有限公司 凿岩机自动回退控制系统及其控制方法

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5337788A (en) * 1993-10-22 1994-08-16 Robertshaw Controls Company Pneumatic valve with slow start and quick exhaust
US5669422A (en) * 1995-04-07 1997-09-23 Ckd Corporation Slow start valve
AT404065B (de) * 1995-08-04 1998-08-25 Hygrama Ag Startventil für pneumatische anlagen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112012004574B4 (de) 2011-11-02 2018-03-08 Smc Kabushiki Kaisha Strömungsratensteuervorrichtung

Also Published As

Publication number Publication date
WO2008067828A1 (fr) 2008-06-12
EP2047108A1 (fr) 2009-04-15
TWI403656B (zh) 2013-08-01
DE502006005894D1 (de) 2010-02-25
TW200900613A (en) 2009-01-01

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