WO2004102012A1 - Hydraulisch schaltbares wegeventil - Google Patents
Hydraulisch schaltbares wegeventil Download PDFInfo
- Publication number
- WO2004102012A1 WO2004102012A1 PCT/EP2004/004968 EP2004004968W WO2004102012A1 WO 2004102012 A1 WO2004102012 A1 WO 2004102012A1 EP 2004004968 W EP2004004968 W EP 2004004968W WO 2004102012 A1 WO2004102012 A1 WO 2004102012A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- piston
- connection
- control
- directional control
- Prior art date
Links
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
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86622—Motor-operated
- Y10T137/8663—Fluid motor
Definitions
- the invention relates to a hydraulically switchable directional control valve, in particular for expansion facilities in underground mining, with a high-pressure connection, a consumer connection, a return connection and a control pressure connection for hydraulic fluid, an axially displaceable, in particular hollow piston-shaped valve piston in a receiving bore of a valve seat support, which is connected to the consumer connection on its open end face is connected, which has a radial passage and which, in contact with a valve seat carrier-side sealing seat, blocks the consumer connection from the high-pressure connection, and with a control piston which is displaceable in a control piston guide by pressurization with a control pressure at the control pressure connection and with which the return connection depends on the position of the control piston can be connected to the consumer connection or can be shut off from the consumer connection and the high-pressure connection.
- the invention has for its object to provide a hydraulically switchable directional valve, which is characterized by a material-saving mode of operation and a quick response.
- the object is achieved by a hydraulically switchable directional valve with the features of claim 1.
- Advantageous developments of the invention are defined in the dependent claims.
- the above-mentioned object is achieved with the invention in that the valve piston has a second radial passage offset toward the front towards the first radial passage and in that the first radial passage can be closed with the control piston when an intermediate position between an initial and end position of the control piston is reached , Since the directional control valve according to the invention has radial passages arranged axially offset from one another, one of which can be closed with the control piston when pressurized with control pressure or is closed when the control pressure is applied, a significantly better response behavior of the directional control valve can be achieved.
- valve piston is guided between the two radial passages in a valve piston sliding guide to form a throttle gap, the second radial passage depending on the position of the valve piston opposite the valve piston sliding guide or on the high-pressure side of the valve piston sliding guide.
- a throttled liquid connection between the consumer connection and the return connection or a throttled liquid connection between the high pressure connection and guaranteed the return connection Only when the directional control valve is open, i.e.
- the arrangement according to the invention of the second radial passage of the valve piston ensures that in the intermediate position of the control piston, i.e. when the first radial passage is closed, a throttling effect between the consumer connection and the return connection is maintained, in that the hydraulic fluid flows through the second passage and a small gap between the surface of the valve piston sliding guide facing the valve piston and the outer wall of the valve piston. Furthermore, a reliable switching behavior of the directional control valve in its open position while avoiding undesirable leakage currents from the high-pressure connection back to the return connection is given by the fact that when the valve piston is fully open, ie when the hydraulic fluid at full pressure from the high-pressure connection passes through the second radial passage to the consumer connection, the return port is closed by the control piston in its end position.
- the control piston In the switching process of the directional control valve, the control piston is therefore first moved into the intermediate position, still in the closed position of the directional control valve, ie with the sealing seat closed, resulting in a throttled fluid connection between the Consumer connection and the return connection results.
- the hydraulic fluid is not included in the high-pressure connection, so that in the closed position of the directional control valve, a respective plunger can be retracted more gently and thus a material-saving operation of the directional control valve can be achieved.
- a smoother retraction of the stamp also has an advantageous effect on the overall lifespan of the corresponding step extension frame.
- This function of the directional control valve according to the invention also offers the advantage that, if necessary, an additional external throttle valve.
- control piston is freely displaceable relative to the valve piston from its initial position to its intermediate position.
- control piston can axially to the valve piston. ben be displaceable, whereby a displacement of the control piston can be realized in a known manner by means of a control pressure of a hydraulic fluid applied to the end face of the control piston.
- control piston could also be rotatable relative to the valve piston, so that it rotates from its initial position into its intermediate position when the control pressure is correspondingly present, thereby covering or closing off the first radial passage of the valve piston. In the intermediate and end positions, the control piston can cover the first radial passage, cover it in a sealed manner or cover it up to a throttle gap.
- control piston will be moved coupled to the valve piston into its end position when the directional control valve is opened further.
- control piston can have a projection on its end facing the control pressure connection, which comes into contact with a shoulder portion of the valve piston when the intermediate position is reached and thus forces a common displacement of the control piston and valve piston due to a positive fit when the directional control valve is subsequently opened.
- the control piston is coupled to the valve piston by means of a positive fit between the projection of the control piston and the shoulder section of the valve piston. Due to the free displacement of the control piston into its intermediate position, in which the first radial passage is closed by the control piston, throttling between the consumer connection and the return connection can thus advantageously be achieved without the high-pressure connection being opened by lifting the valve cone becomes.
- the sealant for closing the sealing seat with a reliable sealing effect between the valve piston and the valve Seat carriers can advantageously consist of a valve cone on the valve piston and a sealing ring which is arranged on the valve seat carrier and has a conical surface as a sealing seat.
- the sealing ring is fixed in the valve seat carrier by a retaining ring. Furthermore, the valve piston can be guided in the valve seat carrier along the retaining ring between the high-pressure connection and the return connection without a seal.
- the tolerances between the valve piston and the retaining ring are preferably selected so that there is a slight play between these components or there is a small gap.
- the valve piston has a conical surface ring on its outer jacket side, on the underside of which the valve cone is provided, since this allows the valve piston to be manufactured inexpensively as a turned or cast part.
- the conical surface ring is arranged on the high-pressure side of the two radial passages, which ensures that when the valve cone is lifted off the sealing ring, the hydraulic fluid passes through the high pressure connection thus released directly into the second radial passage of the valve piston and through it to the consumer connection.
- the hydraulic fluid can flow through the above-described throttle point between the retaining ring and the outer wall of the valve piston in order to avoid pressure surges.
- the control piston can have a control piston shaft which holds the valve piston in its lower end arranged on the tank side. partially covered and in the intermediate and end positions of the control piston covers the first radial passage and closes it. Secure closing of the return connection can advantageously be ensured if, in the end position of the control piston, a front, preferably outer, end of the control piston shaft comes to the sealing system with a sealing seat element arranged in the valve seat carrier.
- a preferably inner contact surface of the sealing seat element which is adapted to the front end of the control piston shaft, can be conical, which results in a very reliable sealing effect at this point.
- the valve seat carrier can have a step-shaped receptacle in which the sealing ring and the retaining ring can be clamped in a form-fitting manner.
- the two ring elements can be positioned in a simple manner during the manufacture of the directional valve, and they are also well shielded from external loads.
- the retaining ring preferably encompasses the sealing ring on the side facing away from the piston sealing surface in a form-fitting manner with an inwardly tapered ring mount, as a result of which the sealing ring is positioned very securely in its position.
- the sealing ring can be made from a preferably high-strength plastic.
- the retaining ring can also preferably be made of steel.
- the aforementioned individual components of the directional valve are positively clamped by a screw closure in the valve housing.
- the screw closure closes the receiving bore of the valve seat support from the outside.
- the clamping force of the screw cap prevents the built-in parts from loosening when pressure changes occur.
- the step-shaped receptacle of the valve seat carrier is designed in such a way that the tensioning force of the tensioning screw does not affect the plastic sealing ring which is sensitive to pressure forces. Excessive stress or even damage to the sealing ring can thus be avoided, which increases the operational safety and the service life of the directional valve.
- a reliable closed position of the directional valve, in which the valve cone is located in the sealing system on the sealing ring, can preferably be achieved by a closing spring arranged in the valve seat carrier, which is connected to the valve piston, e.g. cooperates with an upper side of the conical surface ring and thus prestresses the valve cone against the sealing ring in a dead man's function.
- the control piston could also be pretensioned in its initial position by a pretensioning device; a return movement of the control piston from its intermediate position into its starting position is, however, preferably carried out under pressure control.
- the first radial passage and / or the second radial passage can lead as a radial bore into the axial bore in the hollow piston-shaped valve piston and / or the radial passages can comprise several, preferably four, radial bores arranged circumferentially offset from one another.
- Radial bores can be produced in a simple and inexpensive manner, with large flow cross sections being achieved with several radial bores for each passage.
- Embodiments of the valve piston possible, which ensure a radial passage from its outer wall to its interior.
- the valve piston is preferably axially secured in the valve seat carrier with a snap ring and provided with a connecting thread or the like for a dismantling tool.
- the directional control valve can then be removed as a valve cartridge from its valve housing by screwing the dismantling tool onto the valve piston or fastening it in another suitable manner and then pulling it with the dismantling tool on the valve piston.
- the snap ring arranged on the valve piston rests on the valve seat carrier and also the shoulder section of the valve piston on the projection of the control piston, whereby it is possible to pull out the essential components of the directional control valve as a valve cartridge from the valve housing.
- Fig. 2 is a circuit diagram of the directional control valve according to the invention in the position of Fig. 1;
- 3 is a longitudinal section of the directional control valve according to the invention in an intermediate position
- Fig. 4 is a hydraulic circuit diagram of the directional control valve according to the invention in the position of Fig. 3; 5 shows in a longitudinal section the open position of the directional valve according to the invention; and
- FIG. 6 is a circuit diagram of the directional control valve according to the invention in the position of FIG. 5.
- Fig. 1 shows a directional valve 10 in the closed position.
- a hydraulically switchable directional valve serves e.g. for controlling the hydraulic cylinders, not shown, of hydraulic walking frames in underground mining, e.g. during longwall construction.
- the valve is designed as a valve cartridge, which is inserted into a receiving bore of a valve housing, not shown, and is secured therein by means of a screw cap.
- the valve housing with its receiving bore, the corresponding passage openings which adjoin the respective connections of the directional control valve, and the screw closure can be designed in a manner known to the person skilled in the art, as is e.g. is disclosed in DE 197 08 741 AI, to which reference is made for further explanation in this regard.
- valve housing (not shown), a high-pressure connection P for the high-pressure liquid inlet and a consumer connection A are provided, which is connected to the hydraulic cylinder to be actuated. Furthermore, the valve housing has a return connection R for back-flowing hydraulic fluid and a control pressure connection ST, via which control pressure fluid is supplied to the valve for its actuation.
- the directional control valve 10 essentially consists of a valve seat support 11 with a valve piston 12 axially displaceably therein and a control piston 13 which is mounted in a longitudinally displaceable manner in a control piston guide 14. Both the valve piston 12 and the control piston 13 are preferably hollow-cylindrical.
- the control piston 13 is so formed such that it comprises part of a portion of the valve piston 12 arranged on the tank side in a cup shape.
- the valve piston 12 is provided with a valve cone 15, which is provided on an underside of a conical surface ring 16 arranged on the outer jacket side of the valve piston 12.
- a closing spring 17, which surrounds the valve piston 12, is accommodated in the valve seat carrier 11.
- the closing spring 17 presses in the closed position of the directional control valve 10 shown here against an upper side of the conical surface ring 16 and thus brings the sealing cone 15 to the sealing system on a conical surface of a sealing ring 18.
- the valve seat support 11 has a step-shaped receiving section 19 in which the sealing ring 18 together are positively chambered with a retaining ring 20.
- the sealing ring 18 preferably consists of a high-strength plastic, the retaining ring 20 preferably being made of a steel.
- the retaining ring 20 positively engages the sealing ring 18 on the side facing away from the piston sealing surface of the sealing ring 18 with an inwardly bevelled ring mount 22, as a result of which the sealing ring 18 is positioned very reliably in the valve seat carrier 11 ,
- the receiving portion 19 of the valve seat support 11 is designed in cooperation with the steel retaining ring 20 so that a clamping force exerted by the screw closure (not shown) via the control piston guide 14 does not act on the plastic sealing ring 18.
- valve piston 12 At the upper end of the valve piston 12 facing away from the valve cone 15, in FIG. 1 it is sealed by means of a rod seal consisting of an O-ring 23 and a support ring 24 against a guide ring 25 which is connected to the Consumer connection A facing end of the valve seat carrier 11 is attached and comprises an open end 26 of the valve piston 12. Corresponding to the consumer connection A, an opening 27 is formed in the guide ring 25.
- the closing spring 17 is supported on an underside of the guide ring 25 upwards in order to apply pressure to the conical surface ring 16 and to bias the valve cone 15 against the sealing ring 18.
- the hollow cylindrical valve piston 12 has a first radial, 29 and a second radial passage 28, which are preferably each formed as a radial bore or as radial openings in the valve piston jacket.
- the second radial bore 28 is formed in the valve piston 12 in such a way that, in the closed position of the directional control valve, it lies opposite a valve piston guide 20A formed on the inner circumferential surface of the retaining ring, and consequently lies with its entire bore cross section at the same height as the retaining ring 20 and largely through it is blocked.
- the second radial bore 28 When the directional control valve is opened and the valve piston 12 is displaced accordingly (upwards in FIG. 1), the second radial bore 28 always remains arranged on the high-pressure side. As can be clearly seen in FIG.
- valve piston 12 is thus guided in the valve seat carrier 11 along a surface of the retaining ring 20 facing the valve piston 12 between the high-pressure connection P and the return connection R without seals, ie without sealing rings or the like.
- the distance or the tolerance between the outer wall of the valve piston 12 and the valve piston guide surface 20A of the retaining ring 20 facing the valve piston 12 is selected such that a narrow gap forms at this point as a gap seal through which hydraulic fluid flows in a throttled manner can.
- the first radial bore 29 of the valve piston 12 is formed on the tank side of the second radial bore 28, it being arranged in alignment with the return port R.
- the control piston guide 14 has passage openings 30 which correspond to the return port R.
- the valve seat support 11 has passage openings 31 which correspond to the high-pressure connection P.
- the consumer connection A is connected to the return connection R essentially via the open first radial bore 29 of the hollow piston-shaped valve piston 12, so that hydraulic fluid from the plunger can flow back into the tank via this connection without loss.
- the high-pressure connection P is connected via the passage opening 31 to an interior 32 of the valve seat support 11, so that the interior 32 is filled with hydraulic fluid flowing in from the high-pressure connection P and the valve piston 12 is acted upon by the pressure in the high-pressure connection.
- FIG. 2 The hydraulic closed position of the directional valve 10 is shown in Fig. 2 in a corresponding circuit diagram.
- the above-described embodiment of the directional control valve is a 3/2-way valve, with a fluid connection between the consumer connection A and the return connection R in the explained closed position.
- the above-mentioned closing spring 17 is accordingly identified as a symbol which prestresses the valve piston 12 or the valve cone 15 against the sealing ring 18.
- FIG. 3 shows the directional control valve 10 in an intermediate state, in which the control piston 13 has moved from its starting position into an intermediate position.
- a hydraulic fluid is supplied from the control pressure connection ST, which exerts the control pressure and an opening force on the annular end face 33 of the control piston. Since the control piston 13 is guided axially displaceably from its starting position within the control piston guide 14, the control piston 13 is pressed in the direction of the valve piston 12 (upward in FIG. 3) when the control pressure is applied until an indentation 34, which together with of the ring end face 33 is formed, with a shoulder section 35 of the valve piston 12 comes to rest, which shoulder section is formed in a lower region of the section of the valve piston 12 arranged on the tank side.
- the intermediate position of the control piston is thereby defined.
- the hydraulic fluid also acts on a bottom end face 38 of the valve piston 12, but the level of the control pressure at the start of the switching movement of the directional valve 10 in conjunction with the corresponding area ratios leads to an upward force which is less than the closing force which is caused by the Closing spring 17 and the high pressure act on the pressure side of the valve piston 12. Consequently, no displacement of the valve piston 12 begins (yet) at the control pressure selected here for the displacement of the control piston.
- the control piston 13 has in its front, the valve piston
- control piston shaft 36 which covers the first radial bore 29 and thus closes when the control piston 13 is moved into its intermediate position.
- the tolerances between the front end of the control piston shaft 36 and the part of the valve piston adjoining the second radial bore 28 have been selected accordingly with a view to a sufficient sealing effect.
- the fluid connection between the consumer port A and the return port R through the first radial bore 29 is interrupted, so that hydraulic fluid flowing back from the plunger is no longer easy, or at most via a throttle point between the first radial passage 29 and the control piston 13. can return to the tank through the first radial bore 29.
- FIG. 4 shows a hydraulic circuit diagram for the intermediate position of the directional valve 10 according to FIG. 3. The explained throttling effect between the consumer connection A and the return connection R is indicated symbolically.
- the switching of the valve and the movement of the valve piston 12 from the closed state into the open state takes place at maximum control pressure after the control piston 13 has been moved into its intermediate position and is already in contact with the valve piston.
- the hydraulic fluid supplied from the control pressure connection ST simultaneously acts on the annular end face 33 of the control piston 13 and the bottom end face 38 of the valve piston 12, the resulting total area being larger than the annular end face 33 of the control piston which is subjected to the control pressure at the start of the switching movement.
- the force applied via the control pressure applied to the entire surface 33, 38 is now high enough to overcome the biasing force acting counter to the valve piston 12.
- the control piston 13 moves further upward together with the valve piston 12 in the drawing.
- valve cone 15 lifts off from the sealing ring 18, so that hydraulic fluid can flow from the high-pressure connection P via the passage opening 31 through the second radial bore 28 and the hollow cylindrical valve piston 12 to the consumer connection A.
- the control piston shaft 36 still closes the first radial bore 29 and thus prevents the hydraulic fluid from flowing out through the first radial bore 29 back to the tank.
- control piston 13 has a diameter which corresponds to the diameter of the valve seat carrier 11.
- diameter of the control piston shaft 36 and the effective opening diameter of the valve cone 15 are at least approximately the same. This adjustment of the respective diameters achieves pressure equalization, so that only a comparatively low control pressure is required to open the directional valve 10, which essentially only has to overcome the closing force of the closing spring 17. This results in a very safe switching behavior of the directional valve 10.
- FIG. 5 shows the directional control valve 10 in its open position.
- the arrangement of the second passage 28 and its distance from the first passage 29 is selected so that the connection between the passage opening 31 and the second radial bore 28 is now completely released and therefore no flow losses occur between the high pressure connection P and the consumer connection A.
- the control piston 13 in the open position of the directional valve 10, the control piston 13 reaches its end position.
- a front end of the control piston shaft 36 comes with a conical region of the retaining ring 20 which is adapted to it, so that the annular gap 37 is closed towards the throttle point and thus the return connection R is closed.
- the retaining ring 20 thus serves as a sealing seat element for the front end of the control piston sheep.
- the aforementioned conical area of the retaining ring 20 allows an excellent sealing effect between the retaining ring and the control piston achieve shaft.
- the return port R is also closed by the control piston 13 in such a way that an outer wall of the control piston shaft 36 covers the passage opening 30 corresponding to the return port R.
- the tolerances between the material pairs are chosen accordingly to achieve a desired sealing effect. Because of the closed return connection R, disadvantageous leakage flows of the hydraulic fluid flowing from the high-pressure connection P through the throttle point cannot occur when the directional control valve is fully open, the gap length of the adjoining surfaces 12A, 20A minimizing the leakage anyway. As a result, the hydraulic fluid can flow from the high-pressure port P to the consumer port A without loss.
- the opening position of the directional control valve 10 is shown in FIG. 6 by a corresponding circuit diagram.
- various rod seals each consisting of an O-ring 23 and a support ring 24 are provided.
- these rod seals are also provided between an inner wall of the control piston shaft 36 and the valve piston 12, between an outer wall of the control piston shaft 36 and an inner wall of the control piston guide 14, and otherwise between respective outer walls of the guide ring 25 , the valve seat support 11 or the control piston guide 14 and the receiving bore of the (not shown) valve housing.
- the directional control valve according to the invention can be removed as a valve cartridge from the valve housing as a unit of all of its essential components.
- the valve piston 12 on its bottom face 38 there is a connection thread 39 into which a dismantling tool (not shown) can be screwed in order to remove the valve cartridge.
- a snap ring 40 is arranged at the upper end of the valve piston 12, which engages on a shoulder 41 of the guide ring 25 when the valve piston 12 is pulled down (downward in FIG. 5).
- valve piston and the retaining ring
- a "seal-free guidance" between the valve piston and the retaining ring can also be understood in a general sense in such a way that throttled overflow of hydraulic fluid from the interior 32 is possible in the annular gap 37 when the conical surface ring 16 is lifted off.
- suitable overflow channels or bores can also be provided, the throttle effect being set as desired when the return port R is not closed.
- a further or an alternative throttle point can also be provided between the front end of the control piston shaft and the first radial passage, so that it is only approximately completely covered or sealed in the intermediate position of the control piston.
- the directional control valve according to the invention can also be used for other hydraulic switching tasks.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Driven Valves (AREA)
- Check Valves (AREA)
- Lift Valve (AREA)
- Sliding Valves (AREA)
- Quick-Acting Or Multi-Walled Pipe Joints (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/553,615 US20060219306A1 (en) | 2003-05-13 | 2004-05-10 | Hydraulically switchable directional control valve |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2003207512 DE20307512U1 (de) | 2003-05-13 | 2003-05-13 | Hydraulisch schaltbares Wegeventil |
DE20307512.9 | 2003-05-13 |
Publications (1)
Publication Number | Publication Date |
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WO2004102012A1 true WO2004102012A1 (de) | 2004-11-25 |
Family
ID=27588938
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/004968 WO2004102012A1 (de) | 2003-05-13 | 2004-05-10 | Hydraulisch schaltbares wegeventil |
Country Status (7)
Country | Link |
---|---|
US (1) | US20060219306A1 (de) |
CN (1) | CN100340777C (de) |
CZ (1) | CZ298266B6 (de) |
DE (1) | DE20307512U1 (de) |
PL (1) | PL208923B1 (de) |
RU (1) | RU2305802C2 (de) |
WO (1) | WO2004102012A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104791518A (zh) * | 2015-04-17 | 2015-07-22 | 金湖县江朝汽车有限公司 | 汽车气冷却除尘装置的排污控制阀 |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004015012B3 (de) * | 2004-03-26 | 2005-09-15 | Sauer-Danfoss (Neumünster) GmbH & Co OHG | Ventilanordnung in einem Hyraulikkreis, Verwendung derselben und Anordnung zum Steuern eines hydraulischen Fahrzeugantriebs |
DE102005025916A1 (de) * | 2005-06-06 | 2006-12-07 | Marco Systemanalyse Und Entwicklung Gmbh | Ventilpatrone |
DE102005029055B4 (de) * | 2005-06-21 | 2015-09-03 | Dams Gmbh | Ventilpatrone |
DE102009025092B4 (de) * | 2009-06-16 | 2019-04-25 | Marco Systemanalyse Und Entwicklung Gmbh | Ventilpatrone |
KR101035101B1 (ko) * | 2011-03-31 | 2011-05-19 | 한국뉴매틱(주) | 이단 에어콘트롤 밸브 |
CN103244155B (zh) * | 2013-05-23 | 2015-07-29 | 北京天地玛珂电液控制系统有限公司 | 一种无卸载冲击谐振的液压缸控制阀 |
DE102013222732A1 (de) * | 2013-11-08 | 2015-05-13 | Continental Teves Ag & Co. Ohg | Hydraulisch betätigbares Sperrventil |
WO2016113519A1 (en) * | 2015-01-15 | 2016-07-21 | Axon Energy Products Uk Ltd | Sub-plate mounted valve |
CN105605290B (zh) * | 2016-03-01 | 2017-10-13 | 安徽梯易优叉车有限公司 | 一种液压阀柔性操纵装置 |
RU171264U1 (ru) * | 2017-02-16 | 2017-05-26 | Закрытое акционерное общество "ЭЛКАМ-нефтемаш" | Клапан скважинного насоса |
CN109296816B (zh) * | 2018-11-28 | 2023-12-01 | 陕西航天泵阀科技集团有限公司 | 机械切换分注装置 |
DE102019209440B3 (de) * | 2019-06-28 | 2020-07-30 | HAWE Altenstadt Holding GmbH | Hydromechanischer Linearwandler |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19708741A1 (de) * | 1997-03-04 | 1998-09-10 | Dbt Gmbh | Druckgesteuertes 3/2-Wegeventil |
DE10047073C1 (de) * | 2000-09-22 | 2002-01-24 | Dbt Gmbh | Hydraulisch schaltbares Wegeventil |
US20020129856A1 (en) * | 2001-03-15 | 2002-09-19 | Werner Reinelt | Electrohydraulic control device |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2705020A (en) * | 1950-10-26 | 1955-03-29 | Virgil L Frantz | Fluid pressure actuated control valve |
DE2910029C2 (de) * | 1979-03-14 | 1982-12-23 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München | Steuerventil |
DE3530657C2 (de) * | 1985-08-28 | 1995-03-16 | Westfalia Becorit Ind Tech | Vorrichtung zum Ansteuern hydraulischer, im untertägigen Bergbau eingesetzter Verbraucher |
DE3804846C2 (de) * | 1988-02-17 | 1995-04-27 | Westfalia Becorit Ind Tech | Hydraulisch entsperrbares Rückschlagventil, insbesondere für hydraulische Ausbausysteme |
DE9211629U1 (de) * | 1992-08-29 | 1992-11-05 | Westfalia Becorit Industrietechnik Gmbh, 4670 Luenen, De | |
DE19544592A1 (de) * | 1995-03-23 | 1996-09-26 | Rexroth Mannesmann Gmbh | Zwei-Wege-Einbauventil |
US5901749A (en) * | 1997-03-19 | 1999-05-11 | Gilmore Valve Company, Inc. | Three-way poppet valve |
JPH1113929A (ja) * | 1997-06-23 | 1999-01-22 | Sanwa Seiki Co Ltd | 油圧切換弁 |
-
2003
- 2003-05-13 DE DE2003207512 patent/DE20307512U1/de not_active Expired - Lifetime
-
2004
- 2004-05-10 US US10/553,615 patent/US20060219306A1/en not_active Abandoned
- 2004-05-10 CZ CZ20050705A patent/CZ298266B6/cs not_active IP Right Cessation
- 2004-05-10 PL PL378000A patent/PL208923B1/pl unknown
- 2004-05-10 WO PCT/EP2004/004968 patent/WO2004102012A1/de active IP Right Grant
- 2004-05-10 RU RU2005138489A patent/RU2305802C2/ru not_active IP Right Cessation
- 2004-05-10 CN CNB2004800069459A patent/CN100340777C/zh not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19708741A1 (de) * | 1997-03-04 | 1998-09-10 | Dbt Gmbh | Druckgesteuertes 3/2-Wegeventil |
DE10047073C1 (de) * | 2000-09-22 | 2002-01-24 | Dbt Gmbh | Hydraulisch schaltbares Wegeventil |
US20020129856A1 (en) * | 2001-03-15 | 2002-09-19 | Werner Reinelt | Electrohydraulic control device |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104791518A (zh) * | 2015-04-17 | 2015-07-22 | 金湖县江朝汽车有限公司 | 汽车气冷却除尘装置的排污控制阀 |
Also Published As
Publication number | Publication date |
---|---|
CZ2005705A3 (cs) | 2006-02-15 |
RU2305802C2 (ru) | 2007-09-10 |
CN100340777C (zh) | 2007-10-03 |
US20060219306A1 (en) | 2006-10-05 |
RU2005138489A (ru) | 2006-04-27 |
PL208923B1 (pl) | 2011-06-30 |
DE20307512U1 (de) | 2003-07-10 |
CN1761818A (zh) | 2006-04-19 |
PL378000A1 (pl) | 2006-02-20 |
CZ298266B6 (cs) | 2007-08-08 |
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