EP0869285B1 - Lastdruckgeführter Förderstromregler mit Spülkreislauf - Google Patents
Lastdruckgeführter Förderstromregler mit Spülkreislauf Download PDFInfo
- Publication number
- EP0869285B1 EP0869285B1 EP98103929A EP98103929A EP0869285B1 EP 0869285 B1 EP0869285 B1 EP 0869285B1 EP 98103929 A EP98103929 A EP 98103929A EP 98103929 A EP98103929 A EP 98103929A EP 0869285 B1 EP0869285 B1 EP 0869285B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- load
- line
- indicating
- flushing
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/18—Lubricating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/06—Pressure in a (hydraulic) circuit
- F04B2205/061—Pressure in a (hydraulic) circuit after a throttle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/06—Pressure in a (hydraulic) circuit
- F04B2205/062—Pressure in a (hydraulic) circuit before a throttle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/09—Flow through the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/15—By-passing over the pump
Definitions
- a load pressure-controlled flow controller is in generally referred to as a load-sensing controller and is used, for. B. from the DE 44 47 154 A 1 known.
- the known flow controller compares the load pressure a working line downstream of a measuring throttle or orifice plate with the Delivery pressure with which the hydraulic pump the pressure medium upstream of the measuring throttle feeds into the work management.
- the pressure difference between the the delivery pressure on the hydraulic pump side and the load pressure on the consumer side correspond to this Pressure drop at the preferably adjustable measuring throttle and possibly the additional one Pressure drop in the work line.
- the control valve regulates the delivery volume of the Hydraulic pump so that the pressure drop across the measuring throttle is as constant as possible.
- the one from the hydraulic pump into the working line delivered flow rate can be changed by changing the opening cross section of the measuring throttle can be varied because the pressure drop across the flow restrictor depends on its flow resistance and thus depends on the opening cross-section. Due to the load pressure
- the flow rate controller adjusts the displacement volume of the hydraulic pump to that of the Consumers needed quantity coordinated. If the pressure drop at the measuring throttle increases, the hydraulic pump is pivoted back to a lower delivery volume. However, if the pressure drop at the measuring throttle decreases, the hydraulic pump in In the direction of an increase in the funding volume further pivoted until the Balance is restored.
- the known load pressure-controlled flow controller has the disadvantage that at fully or almost completely swung back hydraulic pump in zero stroke operation or stand-by operation in the hydraulic pump almost no pressure medium is circulated. An operating condition can therefore occur in which one for lubrication and Cooling of the hydraulic pump is not ensured sufficient housing flushing. This can to overheat the hydraulic pump or to tear off the lubricating film cause corresponding damage.
- the hydraulic pump works against that completely or almost completely closed measuring throttle, so that in the upstream area of the measuring throttle a delivery pressure as dynamic pressure in the Working line builds up, but the delivery volume funded by the hydraulic pump relative is low and not safe for maintaining the cooling and lubricating function sufficient.
- the invention is therefore based on the object of a load pressure-guided Flow controller according to the preamble of claim 1 so that only in Operating range of a very low delivery volume of the hydraulic pump an adequate Lubrication and cooling function is maintained.
- the object is in connection with the characterizing features of claim 1 solved with the generic features.
- the invention is based on the knowledge to improve the cooling and Lubrication function one from the working line upstream of the measuring throttle branched flushing circuit for flushing the interior of the hydraulic pump provided.
- the flushing circuit according to the invention is only required if that of the Pumped delivery volume for maintaining the cooling and Lubrication function is too low.
- a flushing valve arranged in the flushing circuit is actuated with the load signaling pressure. If the load signal pressure in the load pressure signal line is a predetermined threshold exceeds the flushing circuit by actuating the flushing valve.
- the constructive effort for the additional rinsing circuit is relatively low. Generating of additional measured variables is not necessary, because according to the invention the Load signaling pressure, which is for controlling the load-sensing control valve anyway is required for controlling the flushing valve.
- the flush valve not between switching on and switching off the rinsing circuit abruptly switches, but in the area above the Switch-off point characterizing the threshold value the pressure medium flow in the flushing circuit throttles with increasing load signal pressure. Pressure peaks when switching the purge valve are prevented in this way.
- the flush valve does not feed the pressure of the working line directly into the Housing flush line.
- the housing flush line is rather at a branch point between the purge valve and the pressure medium tank downstream of the purge valve connected.
- an effective pressure reduction is achieved and prevents pressure fluctuations and pressure peaks occurring in the working line have an undamped effect in the housing flushing line.
- a branch throttle and between the branch point and the pressure medium tank a tank throttle be provided so that the Pressure reduction in the housing flushing line from the ratio of the opening cross-sections of these chokes results.
- Branch valve can be arranged, which interrupts the housing flushing line when on the Branch pressure prevailing pressure, e.g. B. when pressure peaks occur, a predetermined threshold value exceeds.
- Claim 6 structurally combines the branch valve and the branch throttle.
- Fig. 1 shows a schematic, hydraulic circuit diagram of a first Embodiment of the load pressure-controlled flow controller 1 according to the invention.
- the load pressure-controlled flow controller 1 further developed according to the invention is also under the term "load-sensing controller" known and is in its generic Basic function briefly described below.
- the hydraulic pump 2 sucks pressure medium 3 from a pressure medium tank via a suction line 4 and feeds it into a working line 5 under a delivery pressure.
- the Working line 5 is via an adjustable measuring throttle 6 with at least one on the downstream section 5b of the working line 5 connected consumers connected, via which the pressure medium flows back into the pressure medium tank 4.
- the Section between the hydraulic pump 2 and the measuring throttle 6 is hereinafter referred to as upstream section 5a of the working line 5.
- the working line 5 is connected to the delivery flow controller 1 according to the invention via a load pressure signaling line 7.
- the upstream section 5a of the working line 5 for detecting the delivery pressure generated by the hydraulic pump 2 in the upstream section 5a of the working line 5 is connected to the delivery flow controller 1 according to the invention via a delivery pressure signaling line 8.
- the load pressure signaling line 7 transmits a load signaling pressure to a control valve 9 as a control signal
- the delivery pressure signaling line 8 transmits a delivery signaling pressure to the control valve 9 as a control signal.
- the control valve 9 is designed as a 3/2-way valve and has a first pressure chamber 10 connected to the load pressure signaling line 7 and a second pressure chamber 11 connected to the delivery pressure signaling line 8. If the delivery signal pressure transmitted through the delivery pressure reporting line 8 increases compared to the load reporting pressure transmitted through the load pressure reporting line 7 or the load reporting pressure decreases compared to the delivery reporting pressure, the control valve 9 is shifted in the direction of its first control position 12.
- the control valve 9 connects the working line 5 to the control pressure line 13, so that a control pressure 15 which is movable in a first control cylinder 14 is acted upon by control pressure in such a way that the delivery volume V g is pivoted back towards the minimum delivery volume V gmin ,
- the control valve 9 is shifted towards its second control position 18. In the second control position 18, the control valve 9 connects the control pressure line 13 to the pressure medium tank 4. Therefore, the first control cylinder 14 is relieved and the hydraulic pump 2 is further pivoted in the direction of the maximum delivery volume V gmax , so that the delivery volume V g of the hydraulic pump 2 increases ,
- the control valve 9 can assume any intermediate position, so that continuous control of the delivery volume of the hydraulic pump 2 is made possible.
- the delivery volume of the hydraulic pump 2 is reduced when the pressure drop at the measuring throttle 6 increases, and conversely, the delivery volume of the hydraulic pump 2 is increased when the pressure drop at the measuring throttle 6 decreases.
- the control valve 9 therefore regulates the delivery volume V g so that there is a constant pressure drop across the measuring throttle 6. Since the pressure drop at the measuring throttle 6, on the other hand, is proportional to the volume flow in the working line 5 flowing through the measuring throttle 6, the hydraulic pump 2 is regulated to a constant delivery volume V g by the load pressure-controlled flow rate controller 1.
- a pressure relief valve 19 is used to limit the pressure in the load pressure signaling line 7 provided that the load pressure signaling line 7 connects to a pressure medium tank 4.
- the invention relates to a further development of the load-pressure-controlled flow rate controller 1 in the operating range of a low or almost vanishing delivery volume V g of the hydraulic pump 2.
- V g a low or almost vanishing delivery volume of the hydraulic pump 2.
- the hydraulic pump 2 delivers against the completely or almost closed measuring throttle 6 and maintains a relatively high delivery pressure in the upstream section 5a, while the load pressure prevailing in the downstream section 5b of the working line 5 is relatively low.
- the purge valve 30 If the load pressure signaling line 7 only a low load signaling pressure leads, the purge valve 30 by the spring 32 in a first switching state 33rd pressed, in which the purge valve 30 a throttled, preferably adjustable Passage has. If the load pressure in the load pressure signaling line exceeds the predetermined first threshold value, the purge valve 30 interrupts the Flushing circuit by pushing the flushing valve 30 into a second switching state 34, in which it has no passage. It has been shown that the load reporting pressure represents a reliable criterion for switching the flushing circuit on or off, because the load pressure in the downstream section 5b of the working line 5 is low when the measuring throttle 6 is completely or almost completely closed.
- the flushing valve 30 has a Connection line 35 connected to the working line 5, so that the rinsing circuit the working line 5 is branched off.
- the purge valve 30 is via a tank throttle 36 and a cooler 37 connected to the pressure medium tank 4.
- a branch point 38 Between the purge valve 30 and the tank throttle 36 is a branch point 38, one of which Branch purge line 39 branches.
- a branch valve 40 In the housing flushing line 39, preferably in the vicinity the branch point 38, a branch valve 40 is arranged, which a Branch choke 41 has.
- the branch valve 40 is designed so that it Housing flush line 39 interrupts when the prevailing at the branch point 38 Pressure exceeds a predetermined threshold. That way you can Pressure peaks are kept away from the housing flushing line 39.
- the housing flushing line 39 from the main branch 42 of the flushing circuit becomes one Reduction of the case purge pressure is achieved, without doing anything special Pressure reducing valve would be necessary.
- the pressure in the housing flushing line 39 is due to the Ratio of the opening cross sections of the tank throttle 36 and the branch throttle 41 adjustable.
- the structural union of the branch throttle 41 and the branch valve 40 allows a particularly compact design.
- FIG. 2 shows an exemplary embodiment for a concrete realization of the one in FIG. 1 shown hydraulic circuit used flush valve 30th
- a connection 51 for the connecting line 35 is in each case in a valve body 50 the working line 5, a connection 52 for the connecting line 31 with the load pressure signaling line 7 and a further connection 53 for a line leading to the branch point 38 leads, provided.
- the one connected to the load pressure signaling line 7 Port 52 opens into a pressure chamber 54, which has a pressure surface 55 of an actuating piston 56 acted against a return spring 57.
- the actuating piston 56 is in one step-cylindrical bore 58 of the valve body 50 against the return spring 57 movable.
- the Bore 58 has an annular extension 59.
- the adjusting piston 56 has a first one Section 60 and a second section 61 each with an enlarged diameter. The first section 60 with an enlarged diameter separates the one with the load pressure signaling line 7 connected terminal 52 of the connected to the working line 5 Connection 51. Both sections 60 and 61 simultaneously serve to guide the actuating piston 56 in the cylindrical bore 58.
- the Adjusting piston 56 has a section 62 with a reduced diameter, on which Transition between the reduced diameter section 62 and the first Section 60 with an enlarged diameter a control edge 63 is formed.
- the Control edge 63 reaches the return spring edge 64 of the annular groove 59 is the Connection between the connection 51 connected to the working line 5 and the the branch 38 connected connection 53 interrupted.
- the Edge 64 of the annular groove 59 reached, a throttling effect already occurs, so that the Connection between the terminals 51 and 53 is not abruptly interrupted, but the cross section gradually increases with increasing displacement of the adjusting piston 56 reduced.
- the flush volume required for flushing the housing of the hydraulic pump 2 is through a z. B. by means of a thread adjustable stop 65 on which the actuating piston 56 strikes in its rest position, adjustable.
- FIG. 3 shows an alternative embodiment of the inventive load pressure-controlled flow rate controller 1. Elements already described are included matching reference numerals, so that a repetitive description unnecessary.
- FIG. 3 differs from that already based on 1 described embodiment in that the flush valve 30 and Pressure relief valve 19 are structurally combined to a particularly compact design to achieve the flow rate controller 1 according to the invention and the manufacturing costs further to reduce.
- the combined pressure limiting and flushing valve 30, 19 is a 4/2-way valve formed and via the connecting line 31 with the load pressure signaling line 7, and the Connection line 35 connected to the working line 5. At the same time it stands combined pressure limiting and flushing valve 30, 19 with the branch point 38 of the Rinsing circuit in connection.
- the combined pressure relief and purge valve 30, 19 can be any Take intermediate position.
- d. H. for pressure cutoff or pressure limitation, d. H. for the threshold value at which the pressure limiting valve 19 is triggered, on the one hand and for the pressure setting for the flush volume pressure, d. H. the threshold, at which the rinsing cycle is interrupted, on the other hand, are different Values adjustable.
- Fig. 4 is a concrete one Realization of the combined used in the embodiment of FIG. 3 Pressure relief and purge valve 30, 19 shows. Already used in Fig. 2 Reference numerals are used in the same way to facilitate the assignment.
- valve body 50 there is a connection to the working line 5 via the connecting line 35 connected working line connection 51, one via the connecting line 31 with the Load pressure reporting line 7 connected load reporting connection 52, one with the Flushing circuit, in particular with branch point 38, connected flushing connection 53 and a plurality of tank connections 80-83 connected to the pressure medium tank 4 are formed.
- the actuating piston 56 is against a first return spring 84, which actuates the actuating piston 56 permanently acted upon, and against a second return spring 85 which actuates the actuating piston 56 only applied from a predetermined minimum shift from the rest position, in one step-cylindrical bore 86 movable.
- the control edge 63 interrupts the connection between the Working line connection 51 and the flushing connection 53 when the actuating piston 56th is displaced accordingly far against the first return spring 84, so that the control edge 63 reaches the edge 64 of the annular groove 59.
- the threshold at which the Flushing cycle is interrupted therefore, by adjusting the bias of the first Return spring 84 variable. This first threshold is typically below 30 bar.
- a pressure chamber 54 is located in valve body 50 for displacing actuating piston 56 formed, which is connected to the load signaling connection 52 and a pressure surface 55th of the actuating piston 56.
- the actuating piston 56 has a third section 90 expanded diameter, which in the rest position of the actuating piston 56, the load signaling connection 52 separates from the tank connection 82. If the adjusting piston 56 so far is shifted that the control edge 91 of the actuating piston 56, the edge 92 of the Valve body 50 formed annular groove 93, there is a throttled connection between the load signaling connection 52 and the tank connection 82. In this way the load reporting pressure in the load pressure reporting line 7 to a predetermined threshold limited.
- the second return spring 85 only acts on the actuating piston 56, when the control edge 91 reaches the area of the edge 92 of the valve body 50, however not yet when the control edge 63 is in the area of the edge 64 of the annular groove 59, are the first threshold for interrupting the rinsing cycle by setting the first return spring 64 and the second threshold value for the pressure limitation of the Load reporting pressure by adjusting the second return spring 85 independently of each other adjustable. While the first threshold is typically below 30 bar the second threshold is typically above 30 bar.
- the flushing quantity with which the flushing circuit is supplied can be adjusted by setting the Stop 65, on which the adjusting piston 56 strikes in its rest position, adjustable.
- Fig. 4 also shows a specific embodiment for the branch valve 40.
- Das Branch valve 40 has a pressure chamber 100, which has a pressure surface 101 of the Actuating piston 102 urged against a return spring 103. If the actuating piston 102 so is shifted far that the control edge 104 the edge 105 of the extension 106th reached, the connection between the branch 38 and the housing flushing line 39 interrupted.
- the branch throttle 41 is integrated in the actuating piston 102.
- the invention is not limited to the exemplary embodiments shown. As part of The invention can use a variety of other specific valve designs come. There are also a large number of other specific configurations of one load pressure-controlled flow rate controller.
- the embodiment shown in Fig. 4 Branch valve 40 can of course also be used in the exemplary embodiment according to FIG. 1 are used.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Description
- Fig. 1
- einen hydraulischen Schaltplan eines ersten Ausführungsbeispiels des erfindungsgemäßen Förderstromreglers;
- Fig. 2
- eine konkrete Realisierung des bei dem in Fig. 1 dargestellten Ausführungsbeispiels des erfindungsgemäßen Förderstromreglers verwendeten Spülventils in einer schematischen Darstellung;
- Fig. 3
- einen hydraulischen Schaltplan eines zweiten Ausführungsbeispiels des erfindungsgemäßen Förderstromreglers; und
- Fig. 4
- eine konkrete Realisierung des bei dem in Fig. 3 dargestellten Ausführungsbeispiels des erfindungsgemäßen Förderstromreglers verwendeten kombinierten Druckbegrenzungs- und Spülventils in einer schematischen Darstellung.
Claims (11)
- Lastdruckgeführter Förderstromregler (1) für eine unter einem Förderdruck in eine Arbeitsleitung (5) fördernde Hydropumpe (2) mit
einer in der Arbeitsleitung (5) angeordneten Meß-Drossel (6),
einer stromabwärts der Meß-Drossel (6) mit der Arbeitsleitung (5) verbundenen Lastdruck-Meldeleitung (7) zum Erfassen eines Lastdrucks eines an der Arbeitsleitung (5) angeschlossenen Verbrauchers und zum Übertragen eines vom Lastdruck abhängigen Lastmeldedrucks,
einer stromaufwärts der Meß-Drossel (6) mit der Arbeitsleitung (5) verbundenen Förderdruck-Meldeleitung (8) zum Erfassen des Förderdrucks der Hydropumpe (2) und zum Übertragen eines vom Förderdruck abhängigen Fördermeldedrucks, und
einem mit der Lastdruck-Meldeleitung (7) und mit der Förderdruck-Meldeleitung (8) verbundenen, das Fördervolumen der Hydropumpe (2) regelnden Regelventil (9), welches das Fördervolumen der Hydropumpe (2) mit zunehmender Differenz zwischen Fördermeldedruck und Lastmeldedruck verringert und mit abnehmender Differenz erhöht,
gekennzeichnet durch
einen von der Arbeitsleitung (5) stromaufwärts der Meßdrossel (6) abgezweigten Spülkreislauf (30, 38, 40, 39) zum Spülen des Gehäuseinnenraums der Hydropumpe (2) mit einem mit der Lastdruck-Meldeleitung (7) verbundenen Spülventil (30), das den Spülkreislauf (30, 38, 40, 39) unterbricht, wenn der in der Lastdruck-Meldeleitung (7) herrschende Lastmeldedruck einen vorgegebenen ersten Schwellwert überschreitet. - Lastdruckgeführter Förderstromregler nach Anspruch 1,
dadurch gekennzeichnet, daß das Spülventil (30) bei einem Lastmeldedruck unterhalb des vorgegebenen ersten Schwellwerts den Durchfluß durch den Spülkreislauf (30, 38, 40, 39) mit zunehmendem Lastmeldedruck drosselt. - Lastdruckgeführter Förderstromregler nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß das Spülventil (30) zwischen der Arbeitsleitung (5) und einem Druckmitteltank (4) angeordnet ist und eine Gehäusespülleitung (39) an einem Abzweigepunkt (38) stromabwärts des Spülventils (30) abzweigt. - Lastdruckgeführter Förderstromregler nach Anspruch 3,
dadurch gekennzeichnet, daß in der Gehäusespülleitung (39) eine Abzweige-Drossel (41) und zwischen dem Abzweigepunkt (38) und dem Druckmitteltank (4) eine Tank-Drossel (36) vorgesehen sind. - Lastdruckgeführter Förderstromregler nach Anspruch 3 oder 4,
dadurch gekennzeichnet, daß in der Gehäusespülleitung (39) ein Abzweigeventil (40) abgeordnet ist, das die Gehäusespülleitung (39) unterbricht, wenn der an dem Abzweigepunkt (38) herrschende Druck einen vorgegebenen Schwellwert überschreitet. - Lastdruckgeführter Förderstromregler nach Anspruch 4 und 5,
dadurch gekennzeichnet, daß das Abzweigeventil (40) und die Abzweige-Drossel (41) baulich vereinigt sind. - Lastdruckgeführter Förderstromregler nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet, daß zwischen der Lastdruck-Meldeleitung (7) und dem Druckmitteltank (4) ein Druckbegrenzungsventil (19) angeordnet ist, das den in der Lastdruck-Meldeleitung (7) herrschenden Lastmeldedruck bei Überschreiten eines zweiten Schwellwerts begrenzt. - Lastdruckgeführter Förderstromregler nach Anspruch 7,
dadurch gekennzeichnet, daß das Druckbegrenzungsventil (19) und das Spülventil (30) zu einem kombinierten Druckbegrenzungs- und Spülventil (30, 19) baulich vereinigt sind. - Lastdruckgeführter Förderstromregler nach Anspruch 8,
dadurch gekennzeichnet, daß das kombinierte Druckbegrenzungs- und Spülventil (30, 19)
einen in einem Ventilkörper (50) ausgebildeten, mit der Arbeitsleitung (5) verbundenen Arbeitsleitungs-Anschluß (51),
einen in dem Ventilkörper (50) ausgebildeten, mit der Lastdruck-Meldeleitung (7) verbundenen Lastmelde-Anschluß (52),
einen in dem Ventilkörper (50) ausgebildeten, mit dem Spülkreislauf (38, 40, 39) verbundenen Spül-Anschluß (53),
zumindest einen in dem Ventilkörper (50) ausgebildeten mit dem Druckmitteltank (4) verbundenen Tank-Anschluß (82) und
einen in dem Ventilkörper (50) bewegbaren Stellkolben (56)
aufweist,
wobei an dem Stellkolben (56)
eine mit dem Lastmelde-Anschluß (52) verbundene und mit dem Lastmeldedruck beaufschlagte Druckfläche (55), um den Stellkolben (56) gegen zumindest eine Rückstellfeder (84, 85) zu verschieben,
eine erste Steuerkante (63), die die Verbindung zwischen dem Arbeitsleitungs-Anschluß (51) und dem Spül-Anschluß (53) infolge der Verschiebung des
Stellkolbens (56) unterbricht, wenn der Lastmeldedruck den ersten Schwellwert überschreitet, und
eine zweite Steuerkante (91), die die Verbindung zwischen dem Lastmelde-Anschluß (52) und dem Tank-Anschluß (82) infolge der Verschiebung des Stellkolbens (56) öffnet, wenn der Lastmeldedruck den zweiten Schwellwert überschreitet,
ausgebildet sind. - Lastdruckgeführter Förderstromregler nach Anspruch 9,
dadurch gekennzeichnet, daß eine erste, den Stellkolben (56) permanent beaufschlagende Rückstellfeder (84) und eine zweite, den Stellkolben (56) erst ab einer vorgegebenen Mindestverschiebung beaufschlagende Rückstellfeder (85) vorgesehen sind, und
daß die Vorspannung der ersten Rückstellfeder (84) zur Variation des ersten Schwellwertes und/oder die Vorspannung der zweiten Rückstellfeder (85) zur Variation des zweiten Schwellwerts einstellbar sind. - Lastdruckgeführter Förderstromregler nach Anspruch 9 oder 10,
dadurch gekennzeichnet, daß der Anschlag (65) des Stellkolbens (56), an welchem der Stellkolben (56) in seiner Ruhestellung anschlägt, zur Variation des im Spülkreis (38, 40, 39) fließenden Spülmittelstroms einstellbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19713934 | 1997-04-04 | ||
DE19713934A DE19713934B4 (de) | 1997-04-04 | 1997-04-04 | Lastdruckgeführter Förderstromregler mit Spülkreislauf |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0869285A2 EP0869285A2 (de) | 1998-10-07 |
EP0869285A3 EP0869285A3 (de) | 1999-09-22 |
EP0869285B1 true EP0869285B1 (de) | 2002-09-11 |
Family
ID=7825449
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98103929A Expired - Lifetime EP0869285B1 (de) | 1997-04-04 | 1998-03-05 | Lastdruckgeführter Förderstromregler mit Spülkreislauf |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0869285B1 (de) |
DE (2) | DE19713934B4 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19930618A1 (de) * | 1999-07-02 | 2001-01-04 | Mannesmann Rexroth Ag | Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern |
DE10351930A1 (de) * | 2003-11-07 | 2005-06-09 | Linde Ag | Hydrostatische Maschine |
DE102005051482A1 (de) * | 2005-10-27 | 2007-05-03 | Brueninghaus Hydromatik Gmbh | Lastdruckgeführter Förderstromregler mit Schwingungsdämpfung |
DE102009012560B4 (de) | 2009-03-11 | 2019-09-12 | Robert Bosch Gmbh | Ventilvorrichtung für eine Regelungsvorrichtung |
CN102878153B (zh) * | 2012-11-06 | 2015-03-18 | 南京贝奇尔机械有限公司 | 一种多路阀试验台的泵控切换装置及其切换控制方法 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1284310A (en) * | 1969-06-25 | 1972-08-09 | Task Corp | Improvements relating to fluid pumping systems |
US3753627A (en) * | 1971-04-09 | 1973-08-21 | E Ward | Pump bypass liquid control |
US3856436A (en) * | 1972-12-18 | 1974-12-24 | Sperry Rand Corp | Power transmission |
GB1555118A (en) * | 1975-10-04 | 1979-11-07 | Lucas Industries Ltd | Servo pressure control arrangements for variable stroke pumps |
DE2925236A1 (de) * | 1979-06-22 | 1981-01-15 | Danfoss As | Steuergeraet fuer eine pumpe mit verstellbarer foerdermenge |
DE4447154C2 (de) * | 1994-12-29 | 2002-05-29 | Brueninghaus Hydromatik Gmbh | Load-Sensing-Schaltung |
-
1997
- 1997-04-04 DE DE19713934A patent/DE19713934B4/de not_active Expired - Fee Related
-
1998
- 1998-03-05 DE DE59805468T patent/DE59805468D1/de not_active Expired - Fee Related
- 1998-03-05 EP EP98103929A patent/EP0869285B1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE19713934A1 (de) | 1998-10-08 |
EP0869285A2 (de) | 1998-10-07 |
DE19713934B4 (de) | 2004-06-03 |
DE59805468D1 (de) | 2002-10-17 |
EP0869285A3 (de) | 1999-09-22 |
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