EP3475598A1 - Einrichtung zur strömungskraft-kompensation - Google Patents
Einrichtung zur strömungskraft-kompensationInfo
- Publication number
- EP3475598A1 EP3475598A1 EP17734236.7A EP17734236A EP3475598A1 EP 3475598 A1 EP3475598 A1 EP 3475598A1 EP 17734236 A EP17734236 A EP 17734236A EP 3475598 A1 EP3475598 A1 EP 3475598A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control piston
- control
- fluid
- pressure
- connection
- 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.)
- Pending
Links
Classifications
-
- 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
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
-
- 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
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
- F16K31/0613—Sliding valves with cylindrical slides
-
- 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
- F16K31/0686—Braking, pressure equilibration, shock absorbing
Definitions
- the invention relates to a device consisting of at least one control piston, which is guided longitudinally movable in a housing having at least two connection points for fluid, and which cooperates with a control edge of the housing at a connection point, the other connection parts in control positions of the control piston supplied with fluid via a fluid connection and seeks to pull due to occurring flow forces in the direction of a fluid connection blocking this closed position.
- a proportional pressure control valve is known with a generic device with a longitudinally movable in a valve housing controlled piston, which serves by means of a solenoid actuation system for selectively connecting existing in the valve housing connection points, such as a
- the inlet pressure is used to compensate for the flow force, the pressure level occurring being generally higher than on the return side of the device. tion, so that you can control larger volume flows in a regulatory manner better.
- the fluid flowing through the device in the region of the control or regulating edge and the shape change in the control piston is deflected by 90 °, so that the occurring fluid impulse can be supported over the full area on the shape change or the compensating surface thus created.
- the flow force compensation produced in this way makes it possible to manage with smaller magnetic actuation systems which are regularly distinguished by an improved, timely control behavior.
- FIG. 2 and 3 show a device known from the prior art or the compensating device according to the invention in an enlarged view of a circular image detail designated X in FIG. 1;
- FIG. 1 shows in longitudinal section a known 3-way proportional pressure regulating valve with a control piston 12 which can be moved longitudinally in a valve housing 10 and which is provided with an actuating system designated as a whole by 14 for selectively connecting valve housing 10 Connection points are used, such as a pressure supply or pump connection P, a consumer connection A and a tank or return connection T.
- the actuation system 14 shown in FIG. 1 is designed in the manner of a magnet system; but it would also be possible operations by means of a pneumatic or other fluidic actuator (not shown). Also, a mechanical actuation system for the control piston 12 is not excluded in principle.
- the magnet system 14 has a coil winding 16 in a bobbin 18 in the usual and therefore not described in detail manner, wherein the coil winding 16 of the pertinent actuating coil via a plug part 20 with a control current can be supplied.
- the bobbin 18 adjoins a pole plate 22, which is summarized at its free end face of a flange plate 24, which serves to set the pressure control valve to a valve block, not shown.
- 1 can be defined in the manner of a cartridge insert or in the manner of an insert cartridge in the valve block not shown, which has corresponding connection geometries, with the aforementioned ports P, A and T in the valve housing 10th are clearly brought together in fluid-conducting cover.
- the valve shown does not have a 100% pole tube.
- the control edge is integrally formed on the anchor plate 22. Furthermore, there is an independent sleeve which seals the fluid space.
- a magnetic armature 26 is guided longitudinally in the bobbin 18 and has a pressure compensation channel 28 in order to allow a pressure-compensated, pressure-balanced reciprocating movement of the magnet armature 26 in the magnet system. Seen in the direction of FIG. 1, the cylindrical magnet armature 26 has on its right free end side an actuating rod 30 which bears permanently against the control piston 12. For this purpose, the control piston 12 is held at its viewed in the direction of FIG.
- the compression spring 32 moves the arrangement consisting of control piston 12, actuating rod 30 and magnet armature 26, as seen in the direction of FIG. 1 to the left, and not more so long until the control piston 12 in abutment with the stop 33 of the Valve housing 10 is coming.
- the consumer connection A is fluid-conductively connected to the tank or return connection T, via a groove 38 in the control piston 12, which is permanently connected to the fluid space 36 in fluid-carrying fashion and whose axial length is smaller than the length the inner wall portion of the valve housing 10 between port P and port T.
- a displacement position as is apparent from Fig. 2 in the prior art.
- bore rows 40 and 42 are introduced into the valve housing in a conventional manner, wherein one recognizes in Figs. 2 and 3 still a part of a bore of the row of holes 40.
- a throttle channel 44 is introduced at its left end side, which is located between the interior of the valve housing 10 with the stop 33 and the fluid space 36 inside the hollow-bored control piston 12 through the end wall extends.
- the pressure supply or pump connection P is closed and the consumer connection A is connected to the tank or return connection T.
- the magnet system 14 presses on the control piston 12 with a force corresponding to the magnitude of the control current in the direction of the load connection A.
- the control piston 12 will oppose the return spring 32 pushed to the right and the fluid (oil) flows from the pressure supply or pump port P to the load port A.
- the cylindrical control piston 12 moves back further and closes the inlet bores 40 of the pressure supply or pump connection as shown in the prior art FIG. 2 P and interrupts the fluid supply at the consumer connection A. If the outlet pressure drops below the pressure setting due to the relieved load of the connected consumer, the magnet armature 26 pushes the control piston 12 back to the right via the actuating rod 30 and the control process begins again.
- the maximum achievable control pressure is determined by the magnetic force of the magnet system 14. If the pressure at the consumer connection A rises above the preset value, the control piston 12 with the magnet armature 26 is pushed to the left as seen in the direction of FIG.
- the control piston 12 for a flow force compensation in the region of the control or control edge 34 of the housing 10 has a shape change 48 from its cylindrical outer basic shape 50. Because of this change in shape 48, a flow engagement surface 52 is created for fluid, which causes a force acting counter to the flow force compensating force on the control piston 12, which seeks to pull the control piston 12 in an open position opposite to the blocking position; seen in the direction of looking at Fig. 1 so from left to right to pull looking.
- the flow engagement surface 52 is perpendicular to the longitudinal or travel axis 54 of the control piston 12 and is movable together with this.
- the shape change 48 consists in particular of a diameter jump, preferably from a step 56 in the control piston 12, the opposite a free end face 58 of the control piston 12 in the region of its groove 38 is set back from this in the direction of the connection point A.
- the flow-engaging surface 52 forms an annular surface and is arranged in a regulating position in contact with the control or control edge 34 of the housing 19, respectively in the extension, wherein the fluid connection between the two connection points P, A is controlled.
- the change in shape 48 in the control piston 12 forms an annular fluid control chamber 60, which is subjected to a lower fluid pressure on the return side 62 of the device than the pressure prevailing at the connection point P in the valve housing 10 in the regulating operation, wherein the respectively to be controlled pressures greater than Tank or ambient pressure are.
- a fluid diversion of approximately 90 ° is brought about in operation such that the resulting impulse arises on the Entire flow engagement surface 52 can be supported in the direction of the terminal A, wherein the shape change 48 is then exposed to a total of constant fluid pressure during the control.
- the diameter jump in the form of the step 56 is formed by two different diameters in the control piston 12, the smaller diameter opening into the already mentioned recess or channel 38 in the control piston 12.
- a surface 52 was added to the control piston 12, below the control or control edge 34.
- the input pressure at the pump or pressure supply port P can be added be used to compensate for the flow force.
- the counterforce generated acts counter to an opening position which moves or pulls in the control piston 12.
- the associated horizontal pressure characteristic curve is shown in FIG. which is bordered for clarity by an ellipse 64. This results in a largely harmonious filling behavior for a consumer connected to the consumer connection A, such as a motor vehicle clutch.
- the device according to the invention need not be limited to applications with direct-controlled compact pressure regulators, such as the valve presented. Such a flow force control in the sense of compensation can also be realized without difficulty with slide valves. Furthermore, two connection points, which are to be connected to one another in a fluid-conducting manner in a regulating manner, are sufficient to be able to carry out the flow-force compensation in the frame outlined.
- the device according to the invention can basically be used there, where just connection points are to be connected to one another in a regulating manner in a fluid-conducting manner via a control piston or to be separated again from one another.
- the flow force compensation according to the invention it is possible to design smaller magnet systems, which improves the control behavior and helps to save costs and installation space. This has no equivalent in the prior art.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016007881.2A DE102016007881A1 (de) | 2016-06-28 | 2016-06-28 | Einrichtung zur Strömungskraft-Kompensation |
PCT/EP2017/000707 WO2018001549A1 (de) | 2016-06-28 | 2017-06-19 | Einrichtung zur strömungskraft-kompensation |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3475598A1 true EP3475598A1 (de) | 2019-05-01 |
Family
ID=59258169
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17734236.7A Pending EP3475598A1 (de) | 2016-06-28 | 2017-06-19 | Einrichtung zur strömungskraft-kompensation |
Country Status (4)
Country | Link |
---|---|
US (1) | US10865891B2 (de) |
EP (1) | EP3475598A1 (de) |
DE (1) | DE102016007881A1 (de) |
WO (1) | WO2018001549A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021003430A1 (de) | 2021-07-02 | 2023-01-05 | Hydac Fluidtechnik Gmbh | Ventil |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3269416A (en) * | 1964-05-25 | 1966-08-30 | American Brake Shoe Co | Control valve mechanism with means for reducing hydraulic shock |
US3945301A (en) | 1974-04-01 | 1976-03-23 | The Bendix Corporation | Spool valve for hydraulic brake booster |
DE2711861A1 (de) * | 1977-03-18 | 1978-09-21 | Elmeg | Anordnung zur reduzierung der stroemungskraefte in ventilen |
US4941508A (en) | 1989-12-28 | 1990-07-17 | Dana Corporation | Force balanced hydraulic spool valve |
DE19748841A1 (de) * | 1996-11-06 | 1998-05-07 | Anton Haumann | Strömungskraftkompensation an Ventilen |
DE19938884B4 (de) * | 1999-08-17 | 2009-10-01 | Schaeffler Kg | Wegeventil und Verfahren zur Optimierung von dessen Regelbarkeit und Bauaufwand |
US7343934B2 (en) | 2005-04-15 | 2008-03-18 | Fema Corporation Of Michigan | Proportional pressure control valve with control port pressure stabilization |
US8104511B2 (en) * | 2007-08-27 | 2012-01-31 | Parker Hannifin Corporation | Sequential stepped directional control valve |
DE112013000689T5 (de) * | 2012-01-25 | 2014-10-09 | Advics Co., Ltd. | Schieberventil |
DE102012015356A1 (de) | 2012-08-03 | 2014-05-15 | Hydac Fluidtechnik Gmbh | Ventil, insbesondere vorgesteuertes Proportional-Wegesitzventil |
TWI535960B (zh) | 2013-07-01 | 2016-06-01 | Winner Hydraulics Corp | Regulator valve |
DE102014004796A1 (de) | 2014-04-02 | 2015-10-08 | Hydac Fluidtechnik Gmbh | Proportional-Druckregelventil |
DE102016105203A1 (de) * | 2015-07-14 | 2017-01-19 | Hilite Germany Gmbh | Hydraulisches Wegeventil |
EP3118497B1 (de) * | 2015-07-14 | 2018-06-27 | Hilite Germany GmbH | Hydraulisches wegeventil |
-
2016
- 2016-06-28 DE DE102016007881.2A patent/DE102016007881A1/de active Pending
-
2017
- 2017-06-19 US US16/313,537 patent/US10865891B2/en active Active
- 2017-06-19 EP EP17734236.7A patent/EP3475598A1/de active Pending
- 2017-06-19 WO PCT/EP2017/000707 patent/WO2018001549A1/de unknown
Also Published As
Publication number | Publication date |
---|---|
US10865891B2 (en) | 2020-12-15 |
DE102016007881A1 (de) | 2017-12-28 |
US20190162319A1 (en) | 2019-05-30 |
WO2018001549A1 (de) | 2018-01-04 |
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