EP0695878B1 - Hydraulische Steuervorrichtung - Google Patents
Hydraulische Steuervorrichtung Download PDFInfo
- Publication number
- EP0695878B1 EP0695878B1 EP95112101A EP95112101A EP0695878B1 EP 0695878 B1 EP0695878 B1 EP 0695878B1 EP 95112101 A EP95112101 A EP 95112101A EP 95112101 A EP95112101 A EP 95112101A EP 0695878 B1 EP0695878 B1 EP 0695878B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- opening
- piston
- load
- 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.)
- Expired - Lifetime
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Classifications
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- 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
- F15B11/003—Systems with load-holding valves
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- 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
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
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- 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
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
Definitions
- the invention relates to a hydraulic control device, especially for a hoist, according to the preamble of Claim 1.
- a hydraulic control device especially for a hoist, according to the preamble of Claim 1.
- Such a device is known from EP-A-503 266.
- the damper the both in opposite directions under certain operating conditions the damping throttle bypassing check valves as well as the bypass line with their throttle combination dampen these pressure vibrations on the control side of the load holding valve quickly.
- the load holding valve works depending on the load pressure Load pressure in the opening direction on the valve closing element. The bigger the load is, the smaller the pilot pressure for that Load holding valve.
- the pilot pressure can be over the load range vary with a power of ten. About that in the direction of heading Opening preloaded check valve to bypass the damping throttle and / or the damping throttle can especially at high Relief piston load pressure not relieved quickly enough become. There is a dangerous wake of the hydraulic motor on.
- the invention has for its object a hydraulic To create a control device in which pressure fluctuations quickly dampened in their effect on the load holding valve, however, if the load is to be stopped intentionally, the Hydromotor avoided even under unfavorable operating conditions become.
- the combination results in one regarding of the load pressure, pressure-relieved load holding valve, at which the pilot pressure is independent of the load, and the Damping device a proper functioning of the control device.
- Pressure vibrations sound on the control side of the Load holding valve and also in the overall system. Caster movements occur when the load is stopped intentionally, even under extreme conditions Operating conditions no longer.
- the response behavior can be the damping device exactly to the known Adjust the amplitudes of the pressure vibrations. Still leaves the locking valve the pressure medium in critical operating conditions bypassing the dampening movement Discharge damping throttle around the load holding valve if required reliable control, even in the event of an emergency shutdown the system or when the pressure medium is cold.
- the ones from Load pressure unaffected spring loading of the valve closing element of the load holding valve then either only opens for damping used locking valve directly or the locking valve is relieved by the piston to stop the load precisely.
- the damping device has a built-in, so to speak Intelligence that enables her to recognize whether subdued or must be controlled in order to correspondingly react.
- Relief valves are pressure-relieved with regard to the load pressure Although known from DE-A1-32 37 103 and DE-A1-35 09 952.
- the pilot piston has the same in these load holding valves Acting surface as the valve closing element, so that only one damping device with one in the opening direction bypassable damping throttle can be used, the damping effect is insufficient and that with pressure fluctuations, cold pressure medium or in the event of an emergency shutdown, the activation of the load holding valve delayed.
- the auxiliary damper is provided. She is expediently adjustable to a fine adjustment to the To allow operating conditions.
- the on the control piston acting pressure at one to control the load holding valve made pressure reduction in the pilot pressure line dismantled directly to the tank via the bypass, the Piston of the locking valve acts like a pressure sensor.
- the locking valve does not let any pressure medium flow out of the pilot pressure line to the control piston, but only controls the relief of the control piston in order to stop the load precisely.
- the guard locking valve forces the Damping device for working. In the through position it brings the damping device in terms of an exact Control of the load holding valve out of function.
- the embodiment according to claim 4 is structurally simple and reliable.
- the opposite of the exposure surface of the Closing member ensures greater contact area of the piston for the fact that the guard locking valve also in remains in the locked position and the damping device as intended forces to work.
- the area ratio is considered to the known size of the amplitudes of the pressure vibrations chosen to ensure that the tumbler valve essentially the bypass line to the tank only opens when the pressure drop in the pilot pressure line (via the directional valve or in the event of a safety shutdown) the required one Load stopping condition represented. If, for example the load holding valve opened to lower the load is, and on the piston on the one hand and on the closing member on the other the lock valve remains the same pressure in the shut-off position, and also with pressure fluctuations the predetermined amplitudes.
- a small one is sufficient Opening overpressure off, the load holding valve in critical situations to intentionally steer.
- the hydraulic Control device very sensitive to the respective operating conditions of the hoist.
- the manufacturer does not need one Provide adjustability of the spring load, but is from from the outset the spring load for optimal working of the Adjust the control device.
- With the chosen hydraulic Tax ratio is the rapid and speedy control of the Load control valve reached without using the directional control valve extremely high pilot pressure. It also follows with the large contact area of the control piston great for the quick damping of the pressure vibrations moving tax volume.
- a structurally simple and compact embodiment is the starting point 7 out.
- a seat valve takes in the closed position even large load pressures are leak-free. Because the spring load is selected without taking into account the respective load pressure, result in a clean opening and closing behavior with more effective Damping for the load holding valve.
- the quantity regulation of the outflowing pressure medium takes place sensitively via the metering holes, since the slide piston with the fitting bore and the valve seat works together.
- the control piston is outside the flow path of the working pressure medium and cooperates with the spool, the movement and force when opening of the control piston transmits.
- the valve closing element of the load holding valve with respect to that of the directional control valve adjusted pressure pressure balanced.
- a control pressure for the control piston which is only more varies in a very narrow range, e.g. depending on how the valve closing element is lifted far from the valve seat or which spring characteristic the valve closing element acting in the closing direction and the spring load generating spring.
- a small variation in the opening pressure is cheap because under all operating conditions easily manageable pressure conditions result, and the influence the damping device can be precisely predetermined.
- the discharge to the tank avoids disturbing influences of a dynamic pressure on the control function of the load holding valve.
- a structurally simple and compact embodiment is the starting point Claim 10 out.
- the check valve is the in the Housing chamber uses available space. In action there is enough space for generously dimensioned through openings, a low-loss flow through the open check valve guarantee.
- the spool has an additional function, because it is used to guide the circular ring in the housing chamber is used. It can be structurally simple Account must be taken of that with regard to the load pressure pressure balanced load holding valve no shock valve function can perform. An additional shock valve then bypasses Requires the controlled load holding valve to the tank. The bypass line and if necessary the bypass line is connected to that of the shock valve line leading to the tank connected.
- the load balancing valve is balanced with the damping device, the hydraulic control ratio and the geometric area ratio between the Control piston and the valve closing element as well as the response behavior of the locking valve precisely to the known Pressure values of the pressure vibrations in the pilot pressure line interpretable. From the interaction of the individual components there is a rapid damping of the pressure vibrations. On the other hand If the control is intentional, the hydraulic motor continues to run reliably prevented.
- a hydraulic control device S for one as double acting cylinder designed hydraulic motor Z is from a Pressure source P supplied with pressure medium from a tank T in order to Hydromotor V to adjust a piston 1.
- the control device S contains a directional control valve W, e.g. a 4/3-way control valve with depressurized middle position, on Load holding valve L and a damping device D.
- the directional control valve W is via work lines 4, 5 to work rooms 3, 4 of the hydraulic motor V.
- the working line 5 is divided into sections 5a, 5b, between which the load holding valve L is classified.
- the load holding valve L has one Housing 7 a control side 6 to which a control pressure line 8 is connected by the working line 4th branches.
- the damping device D is in the pilot pressure line 8 arranged between sections 8a and 8b. It includes one preferably adjustable, damping throttle 9, one in the direction of flow check valve 10 opening to control side 6, one in the direction of flow from the control side 6 to the working line 4 opening guard locking valve Z, e.g. a check valve 11, which is biased by a spring 12, and one between sections 8a and 8b of the pilot pressure line 8 bypass line branching off to tank T 13.
- a throttle passage 15 is provided, which has an interference throttle passage 14 cooperates in the bypass line 13. Of the Interference throttle passage 14 is slightly larger than the throttle passage 15 (area ratio e.g. 0.6: 0.5mm).
- pressure-controlled Pressure relief valve 17 is included.
- the bypass line 13 is downstream of the pressure relief valve 17 to the line 16 connected.
- valve closing element C In the load holding valve L is a spring chamber 18 through a valve seat 20 connected to a housing chamber 19. To the pen chamber 18, the line section 5b is connected to the Housing chamber 19, however, the line section 5a.
- An Indian Spring chamber 18 arranged valve closing element C with a conical or spherical seat surface 21 works with the valve seat 20 together. This is in an insert 27, the is removably fixed by means of a spring housing 45.
- the valve closing element C is in the closing direction by a spring 44 acted on the valve seat 20.
- Part of the valve closing element C is a hollow slide piston 22 which is in a Fitting bore 26 of the insert 27 and guided with its free, a housing chamber wall 31 penetrating sealed End 23 protrudes into a control chamber 32.
- metering holes 24 different Size arranged so that several smaller metering holes 24 are positioned closer to the seat surface 21 than several larger metering holes 24.
- passages 25 are in the jacket of the spool molded.
- a control piston 35 is sealed in the control chamber 32 slidably guided with the free end 23 of the Slide piston 22 cooperates.
- Part of the control chamber 32 is either via a channel 33 with the spring chamber 18th or connected to the tank via a channel 33 '.
- the lower, part of the control chamber closed by a plug 36 32, is via a channel 34 with the control side 6 and Section 8b of the control pressure line 8 connected.
- valve closing element C is both in terms of in the housing chamber 19 prevailing load pressure of the work space 2 pressure balanced because the load pressure radially on the outer circumference of the Slide piston 22 acts, as well as via the channel 33 with respect of the pressure prevailing in the spring chamber 18, or via the Channel 33 'to tank T.
- Fig. 1 is the hydraulic motor V.
- the load pressure in the work area 3 is from the check valve R, by the spring 44 to the Valve seat 20 pressed valve closing element C and from the pressure relief valve 17 added.
- the directional control valve W in the right Switched position.
- the working line 5 is with the Pressure source P connected while the working line 4 with the Tank T is connected.
- the pressure lifts the annulus 29 from the Passages 28 from, the pressure medium flows essentially unthrottled to the work area 3.
- the piston 1 is raised. Pressure medium is from the work room 2 on the work line 4 and the directional control valve W pressed into the tank T. To stop the Piston 1, the directional control valve W in the middle position adjusted.
- the piston 1 If the piston 1 is to be lowered under a load V, then it will Directional control valve W switched to the left position, in which the Working line 4 with the pressure source and the working line 5 is connected to the tank.
- the check valve R blocks.
- Out the pressure fed into the working line 4 is in the pilot pressure line 8 a pilot pressure derived, which the Control piston 35 lifts and the piston slide 22 Seat 21 of the valve seat 20 against the spring load of the Spring 44 takes off. Some run over from the metering openings 24 the valve seat 20.
- the pressure medium flows through the passages 25 and the uncovered metering openings 24 in the spring chamber 18th and via section 5b of the working line 5 to the tank.
- the directional control valve W returned to the middle position shown.
- At control pressure on the control piston 35 is via the damping throttle 9 reduced, provided the pressure difference of the damping throttle 9 below the biasing force of the spring 12 remains.
- the spring 44 presses the seat 21 on the valve seat 20 so that the piston 1st stopped and the load pressure is maintained.
- the check valve 11 opens in the direction of flow to the bypass line 13 and the working line 4, so that the load holding valve L controls properly.
- the bias of the check valve applied by the spring 12 11 is smaller than that due to the spring loading of the spring 44 on the control piston 35 generated pressure, by one Value of about 2 to 15 bar, preferably at about 3 bar.
- the check valve 11 can open, for example, when cold and viscous pressure medium if there is a pressure drop in the section 8a the pressure difference across the damping throttle 9 the preload the spring exceeds 12, also in a so-called Emergency shutdown, despite the fully open directional control valve W the pressure in section 8a drops suddenly and if necessary even with pressure fluctuations as they typically occur when moving the piston 1 in the lowering direction under a Result load in the pilot pressure line 8 and in the entire system.
- the control device is shown as a block diagram, wherein the hydraulic motor V is loaded with a load V 1 .
- the pressures when controlling a movement of the piston in FIG. 2 to the left are tapped, which are shown in the pressure / time diagram in FIGS. 3 and 4.
- the rod-side pressure p sta in the working line 4 is tapped off at the interface 37.
- the control pressure p d prevailing between the throttle passage 15 and the damping throttle 9 is tapped at the interface 38.
- the control pressure p stk effective on the control piston 35 is tapped at the interface 39.
- the curve of the rod-side pressure p sta over time is shown as a solid curve.
- the dash-dot-dot-dash curve above illustrates fluctuations in the load pressure and the load V 1 .
- the dashed curve represents the course of the control pressure p d .
- the dash-dotted curve finally illustrates the course of the pilot pressure p stk when the spring 12 is set to a preload of 15 bar.
- the pressure p sta initially rises steeply to approx. 80 bar and then drops again to approx. 22 bar within approx. 2 seconds.
- This first amplitude is followed by further weaker pressure waves within approx. 4 seconds, initially up to approx. 52 bar with a drop down to 45 bar, then again up to approx. 62 bar with a drop down to 30 bar.
- the throttle passage 15 in the pilot pressure line 18, which cooperates with the interference throttle passage 14 in the bypass line 13 these pressure waves are already significantly damped and reduced in effect at the interface 38.
- the control pressure p d rises steeply up to 32 bar within about half a second and then drops to 10 bar within about 2 seconds.
- This first amplitude is followed by further, smaller amplitudes, first up to 20 bar and then up to 25 bar, which end significantly dampened compared to curve p sta .
- the pilot pressure p stk initially follows the control pressure pd up to approx. 32 bar.
- the load holding valve is opened.
- the piston 1 begins its movement. When the movement starts, the rod-side pressure p sta collapses, and the control pressure p d also drops as a result.
- the damping throttle 9 is effective while the check valve 11 remains closed by the spring 12. Up to a region 40, the pilot pressure p stk drops gently due to the influence of the damping throttle 9.
- the pressure difference across the damping throttle 9 exceeds the pretension of the spring 12.
- the check valve 11 opens, the pilot pressure p stk drops to approximately 23 bar.
- the check valve 11 closes in the area 41, so that only the damping throttle 9 acts and the pilot pressure p stk can drop slightly up to the area 42. From region 42, there is a further increase in the pilot pressure p stk from approximately 20 bar to 25 bar in region 43, because the control pressure p d also increases to approximately 25 bar. From region 43, the opening pressure p stk only drops slightly.
- the diagram in FIG. 4 shows an optimized working behavior of the control device with a check valve 11 pretensioned to approximately 25 bar. Since the preload of the check valve 11 is greater than the pressure difference of the first amplitude of the control pressure p d , the check valve 11 does not respond.
- the damping throttle 9 dampens the course of the opening pressure p stk from opening the load holding valve.
- the rod-side pressure p sta and the control pressure p d fluctuate approximately as in FIG. 3.
- the course of the opening pressure p stk ( dash-dotted ) is ideal, so that the pressure fluctuations do not influence the opening of the load holding valve.
- the load pressure fluctuations V 1 also decay more rapidly in FIG. 4 than in FIG. 3.
- the spring loading of the spring 44 on the preload of the check valve 11 or vice versa can be adjusted very precisely in knowledge of the course of the pressure fluctuations in the control pressure p d in order to achieve optimal damping on the one hand and nevertheless to ensure the reliable control of the load holding valve on the other hand.
- the hydraulic control ratio by means of the throttle passages 15 and 14 and the geometric area ratio between the control piston 35 and the valve closing element C can also be selected with a view to optimal damping of pressure fluctuations and to the control and activation of the load holding valve.
- the separation between the valve closing element C and the control piston 35 results in structural simplifications.
- the control piston 35 can be so large that a large amount of control pressure medium moves in the control line 8 with regard to the damping, and that the load holding valve can nevertheless be controlled with moderate pressure in the working line 4.
- FIG. 4 also applies to the embodiment of FIG Control device according to FIGS. 5 and 6, in the case of the guard locking valve Z a drain valve 11 'is provided, which in the Fig. 4 shown lowering does not respond, but is held in a locked position, by means of the Pressure pd.
- the tumbler valve Z, 11 'of FIG. 5 sits in a bypass line 44 'from the control side 6 or the line section 8b to tank T.
- the detailed structure of this tumbler valve Z is in Fig. 6 shown.
- the further structure of the control device corresponds 1 and 2.
- the tumbler valve 11 has a chamber 47 in a housing 45 on, in which a piston 50 is displaceable in a bushing 48 and is guided sealed.
- the piston 50 has an action surface Y on which the pressure of the pilot pressure line 8 (Line section 8a) or the bypass line 13 loads.
- the other side of piston 50 and chamber 47 is over one Valve seat 51 with the control side 6 or the line section 8b and simultaneously with the bypass line 44 'to Tank connected.
- the valve seat 51 is a ball Assigned closing member 52, the pressure on the control piston 35 exposed exposure area indicated with X. is.
- the closing member 52 is by means of the piston 50 in the in Fig.
- the application area Y is a Multiple times the area X, so that the shut-off position of the guard locking valve is maintained even if the pressures on the two application surfaces X, Y are the same are.
- the area ratio Y: X is approximately 3 : 1, which means that the pressure in the pilot pressure line 8a drop to a third of the pressure in the line section 8b can without giving up the shut-off position.
- the shut-off position is given up and the through position set in which the pressure medium from the control side 6 practically no resistance via the bypass line 44 ' flows to the tank.
- the tumbler valve Z is expedient an auxiliary damping throttle 46 upstream to a sudden Avoid stopping the load when the tumbler valve Z at abrupt pressure reduction in line section 8a (e.g. at a Safety shutdown) suddenly from the shut-off to the Straight through position.
- the piston 50 is acted upon by the pressure prevailing in the bypass line 13 between the throttle points 15 and 14, that is to say the pressure prevailing in the line section 8a downstream of the throttle passage.
- the locking valve Z of FIGS. 5 and 6 would only be switched to the open position (with an area ratio Y: X of 3: 1) if the pressure p d was reduced to below 10 bar after two seconds, ie to a value to which the pressure p d does not drop under the pressure fluctuations in the system. 5 and 6 therefore remains in the shut-off position during the pressure fluctuations in order to allow the damping device D to come into effect as desired.
Description
- Fig. 1
- eine Blockschaltbild einer hydraulischen Steuervorrichtung mit einem im Längsschnitt dargestellten Lasthalteventil,
- Fig. 2
- einen Teil des Blockschaltbildes von Fig. 1 mit symbolhaft dargestelltem Lastehalteventil, und mehreren Druckabgriffsstellen,
- Fig. 3
- eine Druck/Zeit-Diagramm zur Verdeutlichung des Arbeitsverhaltens der Steuervorrichtung gemäß den Fig. 1 und 2, bei einer bestimmten Einstellung,
- Fig. 4
- ein Druck/Zeit-Diagramm für die Steuervorrichtung bei optimierter Einstellung,
- Fig. 5
- ein Blockschaltbild einer weiteren Ausführungsform, und
- Fig. 6
- einen Schnitt einer Detailvariante von Fig. 5.
Claims (10)
- Hydraulische Steuervorrichtung (S) für einen aus einer Druckquelle (P) über ein Wegesteuerventil (W) doppelseitig beaufschlagbaren Hydromotor (V), insbesondere in einem Hebezeug, mit einem in zumindest einer Arbeitsleitung (5) zum Hydromotor (V) angeordneten, in Zuströmrichtung zum Hydromotor (V) durch ein Rückschlagventil (R) umgehbaren, in Rückströmrichtung gegen Federbelastung aus einer Aufsteuerdruckleitung (8) hydraulisch aufsteuerbaren Lasthalteventil (L), und mit einer in der Aufsteuerdruckleitung (8) angeordneten Dämpfungsvorrichtung (D), die eine in Aufsteuer-Strömungsrichtung durch ein Rückschlagventil (10) und in Zusteuerströmungsrichtung mittels eines druckabhängig zu öffnenden Zuhalteventils (Z, 11, 11') umgehbare Dämpfdrossel (9) und eine permanent druckmittelablassende, von der Aufsteuerdruckleitung (8) abzweigende Beipaßleitung (13) aufweist, in der ein mit einem in der Aufsteuerdruckleitung (8) vorgesehenen Drosseldurchgang (15) zusammenwirkender, gegenüber dem Drosseldurchgang (15) größerer Stördrosseldurchgang (14) enthalten ist, wobei das Zuhalteventil (Z, 11, 11') ein in Öffnungsrichtung vom Aufsteuerdruck des Lasthalteventils (L) beaufschlagtes Schließglied aufweist, das in Schließrichtung zumindest mit dem Druck in der Aufsteuerdruckleitung (8, 8a) belastbar ist, dadurch gekennzeichnet, daß das Lasthalteventil (L) einen zum Abheben eines mit einem Ventilsitz (20) zusammenarbeitenden Ventilschließelements (C) vorgesehenen Aufsteuerkolben (35) aufweist, der in Abheberichtung des Ventilschließelementes auf seiner gegenüber der Fläche (A) des Ventilsitzes (20) größeren Beaufschlagungsfläche (B) aus der Aufsteuerdruckleitung (8) druckbeaufschlagbar und zum Zusteuern des Lasthalteventils unter der Federbelastung des Ventilschließelements (C) druckentlastbar ist, daß das Ventilschließelement (C) im Lasthalteventil (L) bezüglich des Rückströmdrucks vom Hydromotor (V) druckausgeglichen ist, und daß das Schließglied des Zuhalteventils (Z, 11, 11') in Schließrichtung zusätzlich entweder mit einem den Druck in der Aufsteuerdruckleitung (8, 8a) übersetzenden Kolben (50) oder durch eine Vorspannfeder (12) belastbar ist, deren Vorspannung kleiner ist als der durch die Federbelastung über das hinsichtlich des Rückströmdrucks druckausgeglichene Ventilschließelement (C) am Aufsteuerkolben (35) erzeugbare Druck.
- Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß zwischen dem Aufsteuerkolben (35) und dem Schließglied des Zuhalteventils (Z, 11, 11') parallel zur Dämpfdrossel (9) eine Hilfsdämpfdrossel (46) vorgesehen ist.
- Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Zuhalteventil (Z, 11') in einer vom Aufsteuerkolben (35) zum Tank (T) verlaufenden Umgehungsleitung (44') angeordnet und mittels des auf die Differenz zwischen dem Druck am Aufsteuerkolben (35) und dem am Schließglied (52) wirkenden Druck in der Aufsteuerdruckleitung (8, 8a) bzw. der Beipaßleitung (13) ansprechenden Kolbens (50) zwischen einer Absperrstellung und einer Durchgangsstellung umschaltbar ist.
- Steuervorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß das Zuhalteventil (Z, 11') eine Kammer (47) für den Kolben (50), das auf dem Aufsteuerkolben (35) zugewandten Seite des Kolbens (50) liegende Schließglied (52) und einen Ventilsitz (51) für das Schließglied (52) aufweist, die zwischen dem Ventilsitz (51) und dem Kolben (50) an den Tank (T) angeschlossen ist, daß die dem Schließglied (52) abgewandte Beaufschlagungsfläche (Y) des Kolbens (50) aus der Aufsteuerdruckleitung (8, 8a) bzw. der Beipaßleitung (13) beaufschlagbar ist, und daß die Beaufschlagungsfläche (Y) des Kolbens (50) größer ist als die Beaufschlagungsfläche (X) des auf dem Ventilsitz (51) aufliegenden Schließgliedes (52), vorzugsweise um ein Mehrfaches.
- Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Federbelastung (44) des Ventilschließelementes (C) so viel stärker ist als die Vorspannfeder (12), daß mit der Federbelastung über das Ventilschließelement (C) und den vom Ventilschließelement (C) getrennten Aufsteuerkolben (35) im Zuhalteventil (Z, 11) ein Öffnungsüberdruck zwischen 1,0 und 10,0 bar, vorzugsweise zwischen 2,0 bis 5,0 bar, erzeugbar ist.
- Steuervorrichtung nach den Ansprüchen 1 und 5, dadurch gekennzeichnet, daß der Stördrosseldurchgang(14) mit dem Drosseldurchgang (15) ein hydraulisches Aufsteuerverhältnis von ca. 2:1 bis ca. 4:1, vorzugsweise von ca. 3:1 (in der Arbeitsleitung herrschender Druck zum am Aufsteuerkolben (35) wirksamen Druck) herstellt, und daß das geometrische Flächenverhältnis (A:B) zwischen dem Ventilsitz (20) des Ventilschließelements (C) und der Beaufschlagungsfläche des Aufsteuerkolbens (35) bei ca. 1:6,5 bis 1:10,0, vorzugsweise bei ca. 1:8 bis 1:9, liegt.
- Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Ventilsitz (20) im Lasthalteventil (L) an der einer an das Wegeventil (W) angeschlossenen Federkammer (18) zugewandten Mündung einer zylindrischen Passbohrung (26) angeordnet ist, daß das Ventilschließelement (C) eine kegelige oder kugelige Sitzfläche (21) und im Anschluß an die Sitzfläche (21) einen hohlen Schieberkolben (22) aufweist, der mit kontinuierlichem Außendurchmesser in einem Gleitsitz in der Passbohrung (26) geführt ist und eine mit einem Arbeitsraum (3) des Hydromotors (Z) verbundene Gehäusekammer (19) sowie eine der Passbohrung (26) abgewandte Gehäusekammerwand (31) durchsetzt, die eine den Aufsteuerkolben (35) enthaltende Aufsteuerkammer (32) von der Gehäusekammer (19) trennt, und daß im Mantel des Schieberkolbens (22) angrenzend an die Sitzfläche (21) mehrere Zumeßbohrungen (24) und wenigstens eine in der Gehäusekammer (19) liegende Auslaßöffnung (25) vorgesehen sind.
- Steuervorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß die an die Aufsteuerdruckleitung (8) angeschlossene Aufsteuerkammer (32) an der Eintrittsseite des Schieberkolbenendes (23) durch einen Kanal (33, 33') zur Federkammer (18) oder zum Tank (T) druckentlastet ist.
- Steuervorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß die Zumeßbohrungen (24) im Mantel des Schieberkolbens (22) unterschiedliche Größen aufweisen, und daß kleinere Zumeßbohrungen näher an der Sitzfläche (21) liegen als größere Zumeßbohrungen.
- Steuervorrichtung nach wenigstens einem der Ansprüche 1 und 7 bis 9, dadurch gekennzeichnet, daß die Passbohrung (26) mittig und axial in einem im Gehäuse (7) des Lasthalteventils (2) herausnehmbar angeordneten Einsatz (27) angeordnet ist, daß der Einsatz (27) außermittige Durchgänge (28) aufweist, und daß an der dem Ventilsitz (20) abgewandten Seite des Einsatzes (27) ein federbelasteter Kreisring (29) auf dem Schieberkolben (22) verschiebbar geführt ist, der mit den Durchgängen (28) das Rückschlagventil (R) bildet.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE9412531U | 1994-08-03 | ||
DE9412531U DE9412531U1 (de) | 1994-08-03 | 1994-08-03 | Hydraulische Steuervorrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0695878A1 EP0695878A1 (de) | 1996-02-07 |
EP0695878B1 true EP0695878B1 (de) | 1999-12-01 |
Family
ID=6911961
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95112101A Expired - Lifetime EP0695878B1 (de) | 1994-08-03 | 1995-08-01 | Hydraulische Steuervorrichtung |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0695878B1 (de) |
AT (1) | ATE187228T1 (de) |
DE (3) | DE9412531U1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19940966B4 (de) * | 1999-08-28 | 2005-04-07 | Wessel-Hydraulik Gmbh | Hydraulische Schaltungsanorndung zum Betrieb von zwei doppelt wirkenden Arbeitszylindern, insbesondere für die Schenkel einer Abbruchschere |
EP2372167B1 (de) * | 2010-03-30 | 2012-11-14 | Bosch Rexroth Oil Control S.p.A. | Vorrichtung zur Steuerung eines Vorsteuerdrucks, insbesondere eines Ausgleichsventils |
EP3015717B1 (de) * | 2014-10-31 | 2020-02-26 | HAWE Hydraulik SE | Gewindescheibe für ein Ventil |
DE102020212201B4 (de) * | 2020-09-28 | 2022-12-01 | Hawe Hydraulik Se | Separates hydraulisches Dämpfungsmodul und Lasthalteventil mit separatem hydraulischen Dämpfungsmodul |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2559029C2 (de) | 1975-12-29 | 1985-10-31 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 8000 München | Bremsventil |
DE3216580A1 (de) | 1981-05-07 | 1983-02-24 | Hiab-Foco AB, 82401 Hudiksvall | Lasthalte- und senkbremsventil |
DE3234496A1 (de) | 1982-09-17 | 1984-03-22 | Wessel-Hydraulik Günther Wessel, 2940 Wilhelmshaven | Hydraulisches sicherheitsventil |
DE3237103C3 (de) | 1982-10-07 | 1997-01-23 | Wessel Hydraulik | Sicherheitsventil als Lasthalteventil in der Hebezeughydraulik |
DE3509952C3 (de) | 1985-03-19 | 1994-09-01 | Rexroth Mannesmann Gmbh | Bremsventil |
DE8510560U1 (de) | 1985-04-11 | 1986-08-28 | Beringer-Hydraulik GmbH, Neuheim, Zug | Leckfreies Brems-Sperrventil |
US4624445A (en) | 1985-09-03 | 1986-11-25 | The Cessna Aircraft Company | Lockout valve |
DE4105459A1 (de) | 1991-02-21 | 1992-08-27 | Heilmeier & Weinlein | Hydraulische steuervorrichtung |
DE4107776A1 (de) | 1991-03-11 | 1992-09-17 | Heilmeier & Weinlein | Hydraulische steuervorrichtung |
-
1994
- 1994-08-03 DE DE9412531U patent/DE9412531U1/de not_active Expired - Lifetime
-
1995
- 1995-08-01 DE DE59507312T patent/DE59507312D1/de not_active Expired - Lifetime
- 1995-08-01 AT AT95112101T patent/ATE187228T1/de not_active IP Right Cessation
- 1995-08-01 EP EP95112101A patent/EP0695878B1/de not_active Expired - Lifetime
- 1995-08-01 DE DE59506205T patent/DE59506205D1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE59506205D1 (de) | 1999-07-22 |
DE59507312D1 (de) | 2000-01-05 |
DE9412531U1 (de) | 1994-09-29 |
EP0695878A1 (de) | 1996-02-07 |
ATE187228T1 (de) | 1999-12-15 |
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